heat exchange plate and heat exchanger

专利摘要:
HEAT EXCHANGER INCLUDING A MANIFOLDE. The present invention relates to a heat exchanger including heat exchanger plates in a stacked arrangement, so that each heat exchanger plate is spaced from the adjacent heat exchanger plate. The space between heat exchanger plates defines an external fluid passage and each external fluid passage being configured to receive a first fluid. Each heat exchanger plate includes a peripheral edge, and an internal fluid passage to receive a second fluid. The internal fluid passage includes an inlet and an outlet that open at the peripheral edge. The heat exchanger additionally includes a manifold, having a manifold feed chamber that makes fluid communication with the inlet on each heat exchanger plate, and a discharge chamber that makes fluid communication with the outlet of each heat exchanger plate. .
公开号:BR112015008522B1
申请号:R112015008522-9
申请日:2013-10-15
公开日:2021-01-19
发明作者:Barry R. Cole；Laurence Jay Shapiro；Barry Noel；Hoseong Lee；Yunho Hwang；Daniel Latimer Wilkins
申请人:The Abell Foundation, Inc.；
IPC主号:

专利说明:

Related Applications
[0001] The present invention claims priority for Provisional Patent Application No. 61 / 720,591 filed on October 31, 20212 and Provisional Patent Application No. 61 / 714,538 filed on October 16, 2012, both incorporated herein, by reference, in its integrality. Technical Field
[0002] The present invention relates to the transfer of heat between fluids, and, more specifically, to the transfer of heat between fluids using heat exchanger plates. Background
[0003] The planet's tropical seas and oceans are a unique renewable energy resource. The so-called "Ocean Thermal Energy Conversion" (OTEC of Ocean Thermal Energy Conversion) is a way to produce renewable energy using solar energy stored as heat in the oceans in tropical regions. The OTEC process uses the temperature difference between the surface and the depths of the ocean to move an engine, to produce electricity. The hot water needed for OTEC heat engines is found on the surface to a depth of 30.48 (100 feet) or less. The constant source of cold water can be found between a depth of 762 m and 1280.16 m (2700 feet and 4200 feet) or more. Since such depths are not typically found near large population centers or even large land masses, an offshore shore plant is required.
[0004] OTEC floating plants for small waves having high efficiency heat exchanger systems have been proposed, where hot water and cold water ducts and heat exchangers are structurally integrated into a floating platform, and used to move a thermal engine. The thermal engine, in turn, moves a generator through which electrical energy is produced. summary
[0005] In some respects, an electricity generating plant uses ocean thermal energy conversion processes as an energy source.
[0006] Additional aspects relate to small wave OTEC electric power plants having high efficiency multi-stage heat exchanger systems, where hot and cold water supply ducts, and heat exchanger modules are structurally integrated into one platform or floating structure of the power plant.
[0007] In some aspects of the implementations of the invention, a heat exchanger includes two or more heat exchanger plates in a stacked arrangement, so that each heat exchanger plate is spaced from the adjacent heat exchanger plate, with the space between adjacent plates defines an external fluid passage, each external fluid passage configured to receive a first fluid. Each heat exchanger plate includes a peripheral edge, an internal fluid passageway configured to receive a second fluid, and an entrance to the internal fluid passageway that opens at the peripheral edge, and a collector communicates fluidly with the inlet of each heat exchanger plate.
[0008] In other exemplary implementations of the invention, the heat exchanger includes one or more of the following components: the collector includes a collector chamber that extends in a direction normal to the plane defined by a heat exchanger plate. The collector includes a flap that extends from a portion of the peripheral edge of each heat exchanger plate, where each flap includes a flap passage that makes fluid communication with the inner passage, each flap including an opening that intercepts its flap passage , the openings of each flap are aligned in a direction normal to the plane defined by the heat exchanger plate and defines a collector chamber, and the inner surface of the collector chamber includes joints that correspond to a connection between a first surface of a passage flap of a flap and a second surface of a flap passage of an adjacent flap. The flaps on each plate are encapsulated in a fluid impermeable material. The tabs on each plate are encapsulated in a rigid material. The collector is configured to be connected to a collector of a second heat exchanger, so that the respective collectors are in fluid communication.
[0009] Still other exemplary implementations of the invention may include one or more of the following components: each plate comprises a first external heat exchange surface and a second external heat exchange surface opposite the first external heat surface, the first and second external heat exchange surfaces make fluid contact with the first fluid, when the heat exchanger is in use. The heat exchanger comprises an outlet from the internal fluid passage, the outlet opening at the peripheral edge and the collector make fluid communication with the outlet of each heat exchange plate, and the collector comprises a first collector chamber, which it is configured to supply a second fluid at the entrance of the internal fluid passage, and a second collector chamber configured to receive a second fluid from the exit of the internal fluid passage, the first collector chamber being isolated from the second collector. The first collector chamber has a different volume than the second collector chamber. The internal passage is defined between a flat inner surface of the heat exchanger plate and a non-flat inner surface of the heat exchanger plate. Each heat exchanger plate comprises a first non-flat heat exchange surface and a second heat exchange surface, opposite the first heat exchange surface, which is flat, and the stacked arrangement of the heat exchanger plates comprises arranging the heat exchanger plates, so that the first heat exchange surface of a stack plate faces the second heat exchange surface of an adjacent stack plate. The internal fluid passage expands outward from one side of the plate, whereby the first side of the plate includes outwardly extending regions, which correspond to the location of an internal fluid passage, and the second side of the plate is not deformed. The internal fluid passage includes several mini-channels.
[00010] In some implementations, the two or more heat exchanger plates are stacked vertically. In other respects, the two or more heat exchanger plates are stacked horizontally. The heat exchanger plates can be arranged so that a space is provided between each heat exchanger plate to allow fluid to envelop and pass through each heat exchanger plate.
[00011] In additional exemplary implementations, the heat exchanger includes heat exchanger plates in a stacked arrangement, where each heat exchanger plate is spaced from the adjacent heat exchanger plate, the space between adjacent heat exchanger plates defines an external fluid passage, each external fluid passage being configured to receive a first fluid. Each heat exchanger plate includes a peripheral edge, an internal fluid passageway configured to receive a second fluid, an inlet to the first end of the internal fluid passageway, the inlet opening on the peripheral edge, and an outlet from the second end of the internal fluid passage, the outlet opening at the peripheral edge, and a collector having a feed chamber in fluid communication with the inlet of each heat exchanger plate, and a discharge chamber, in fluid communication with the outlet of each heat exchanger plate.
[00012] Other implementations of the invention include one or more of the following components: the collector feed chamber and the collector discharge chamber, each extending in a direction normal to the plane defined by a heat exchanger plate. The collector includes a flap that extends from a portion of the peripheral edge of each heat exchanger plate, each flap including a flap entry passage in fluid communication with the internal fluid inlet and a flap exit passage in fluid communication with the internal fluid passage outlet, each flap including a flap inlet opening, the flap inlet openings of each flap define a collector feed chamber and the inner surface of the collector chamber includes joints that correspond to the connection between a first surface of a flap entry passage of a flap and a second surface of a flap entrance passage of an adjacent flap, and the flap exit openings of each flap define a collector discharge chamber, and the inner surface of the collector discharge chamber includes joints that correspond to a connection between the first surface of a flap outlet passage and a second surface of an outlet passage flap flow of an adjacent flap. The tabs on each plate are encapsulated in a rigid material. The flaps on each plate are encapsulated in a fluid impermeable material. The collector is at least encapsulated in rigid material. The collector is configured to be connected to a collector of a second heat exchanger so that the respective collectors are in fluid communication. Each plate comprises a first outer heat exchange surface and a second outer heat exchange surface opposite the first outer heat exchange surface the first and second outer heat exchange surfaces fluidly contact the first fluid when the heat exchanger is in use. The collector feed chamber has a different volume than the collector discharge chamber.
[00013] Still other exemplary implementations of the invention may include one or more of the following components: a defined inner passage between a flat inner surface of the heat exchanger plate and a non-flat inner surface of the heat exchanger plate. Each heat exchanger plate comprises a first non-flat heat exchange surface and a second flat heat exchange surface opposite the first heat exchange surface, and the stacked arrangement of the heat exchanger plates comprises arranging the heat exchanger plates of heat so that the first heat exchange surface of a stack plate faces the second heat exchange surface of an adjacent stack plate. The internal fluid passage expands outward from only one side of the plate, whereby the first side of the plate includes outwardly extending regions that correspond to the location of the internal fluid passage, and a second side of the plate is undeformed. The internal fluid passage includes several mini-channels.
[00014] In some implementations of the invention, a heat exchanger includes heat exchanger plates, each heat exchanger plate comprises an internal fluid passageway configured to receive a first fluid, a first external surface, and a second opposite external surface to the first outer surface. The first outer surface is flat, the second outer surface includes protruding regions that correspond to the location of the inner passage on each heat exchanger plate, and the heat exchanger plates are stacked along a geometric axis perpendicular to the first external surface, so that the first outer surface of a heat exchanger plate faces the second outer surface of an adjacent heat exchanger plate.
[00015] Additional exemplary implementations include one or more of the following components: the heat exchanger plates are arranged so that the first outer surface of a heat exchanger plate is spaced from the second outer surface of an adjacent heat exchanger plate . Each of the first and second outer surfaces contacts a second fluid, when the heat exchanger is in use.
[00016] In some aspects of the invention, a method for making a heat exchanger includes providing a heat exchanger plate having a first external heat exchange surface and a second side opposite the first side, and providing a second external heat surface. heat exchange and an internal fluid passage; cut an opening in the plate, so that the cut opening intersects the internal passage; repeat the steps above to form a plurality of cut plates, stack the cut plates along a geometric alignment axis, to provide a stack of plate having aligned cut openings, and join the cut edges together, so that the first side of a plate is connected to a second side of an adjacent plate, so that a collector chamber is formed in a volume defined at least in part by the respective connected openings, the collector chamber makes fluid communication with each internal passage.
[00017] Exemplary aspects of the invention may include one or more of the following components: affixing a flange to the cut openings of the plate stack and encapsulating a portion of the joined plates and a ferrule portion of the plastic flange. The heat exchanger additionally comprises a flap which extends from a portion of the peripheral edge of each plate and the cut opening of each plate is located on the flap. The heat exchanger flaps are encapsulated in a different encapsulation material than the material used to form the flaps. The heat exchanger flaps are encapsulated in plastic. Stacking includes arranging the plates so that the side of a plate faces the second side of an adjacent plate. Providing a heat exchanger plate having an internal fluid passage includes providing a first and a second panel in a predetermined arrangement; applying a bond inhibiting agent to a surface of the first panel in a predetermined arrangement; stack the first and second panels so that the bonding agent is between the first and second sheets; roll first and second stacked panels together to form a plate; and expanding the plate to form an internal passageway that corresponds to the predetermined arrangement. During the step of expanding the plate, the second panel is deformed by the pressure of the injected air, and the first panel remains undeformed by the pressure of the injected air. Expanding the plate comprises injecting air between the first panel and the second panel. Joining the cut edges of the cut openings comprises joining the first panel of a plate with a second panel of an adjacent plate. Stacking the plates includes having an alignment template, and placing the plates in the alignment template to provide a stack of plates having peripheral edges and aligned cut openings. After stacking, the alignment template remains with the plate stack.
[00018] Exemplary methods may also include one or more of the additional components: joining a connector with the cut openings on the sides facing outward from the end plates of the plate stack. The inner passage includes an inlet and an outlet, the step of cutting an opening in the plate includes cutting an inlet opening that intersects the inlet end of the inner passage and cutting an outlet opening that intercepts the outlet end of the inner passage, and the step of joining and the step of joining the cut edges includes joining the cut edges of the inlet openings so that a first side of a plate joins a second side of an adjacent plate, and so that a feed chamber collector is formed in a volume defined, at least in part, by the respective collector feed openings, the collector feed chamber making fluid communication with the inlet end of the inner passage, and join the cut edges of the outlet openings so that a first side of a plate is joined to a second side of an adjacent plate. And so that a collector discharge chamber is formed in a volume defined at least in part by the respective connected outlet openings, the collector discharge chamber making fluid communication with the outlet end of the internal passage. The collector feed chamber and collector discharge chamber are located within a single collector so that there is no fluid communication between the collector feed chamber and the collector discharge chamber. The heat exchangers described in this provide an increased heat exchange efficiency and therefore, for example, increase the efficiency of the OTEC thermal motor which uses a highly efficient thermal cycle to provide maximum efficiency for the production of electrical energy. The heat exchange in the boiling and condensation processes as well as the materials and design of the heat exchanger limit the amount of energy that can be extracted from each pound (unit of weight) of hot water. However, the heat exchangers used in the evaporator and condenser use large volumes of water and hot water flow with low head loss to limit parasitic charges. Heat exchangers also provide high heat transfer coefficients to increase efficiency. The heat exchangers incorporate materials and designs adjusted for hot and cold water inlet temperatures to increase efficiency. The design of the heat exchanger employs a simple construction method that uses a small amount of material that reduces costs and volumes.
[00019] In some exemplary configurations of the invention, the working fluid is supplied and discharged from each plate of the heat exchangers along a peripheral side edge of the plate, through a collector, in which the inlet and outlet connections are formed integrated with the board and welded to the adjacent board during the assembly process. The collector includes welded connections encapsulated in the epoxy that flows between the plates in the collector region to provide structural reinforcement to the assembly and prevent water from coming in contact with the welded surface. This is an improvement over tube heat exchangers, since each tube can be firmly connected to the heat exchanger plate or to a supply line. For example, in some configurations, as many as four inlet connections and eight outlet connections are required per plate of the heat exchanger. At densities of approximately 20 plates per linear foot, as much as 488 individual connections could be required in a 6.09 m (20 foot) module. This causes a logistical problem, as well as a quality control problem. The connections are also exposed to the marine environment. Advantageously, by using the collector on the lateral peripheral edge of the heat exchanger, the use of pipe connections and the corresponding logistical and quality control problems is entirely eliminated.
[00020] In other configurations of the invention, the heat exchangers described herein are formed of plates that are expanded to form an internal fluid passage, where the expanded regions extend on only one side of the plate leaving the other side essentially flat. This allows consistent maximum and minimum spacing between plates, regardless of whether expansion occurs along the length of the plate. Using plates where expanded regions extend on only one side of the plate (here one-sided plates) mitigate the impact of dimensional inconsistency in the direction of the width associated with the rolling fusion manufacturing process used to form the plates. The rolling fusion process to fuse metals between rollers has inherent issues with respect to dimensional repeatability in the direction of width although the height is consistent. When scroll-joined plates in which the expanded regions extend on both sides of the plate (here called double-sided plates) are stacked on a heat exchanger, dimensional variation can result in configurations in which the expanded sections of adjacent plates are positioned directly opposite each other, resulting in clamping points with higher pressure losses and lower heat transfer than expected. By providing one-sided plates and arranging the plates on the heat exchanger, then the side that extends from a plate facing the flat side of the adjacent plate, avoids the negative effects of dimensional variation. In addition, laboratory results show that pressure losses for a one-sided plate are significantly reduced, with equal flow and nominal spacing to double-sided plates.
[00021] The implementations, configurations, and examples of the invention described herein may be combined as described, or in other combinations of components.
[00022] Details of one or more configurations will be set out in the following description and attached drawings. Other components, objectives and advantages will be apparent to those skilled in the art from the following description and attached drawings and claims. Description of Drawings
[00023] Figure 1 illustrates an exemplary OTEC thermal engine;
[00024] Figure 2 illustrates an exemplary OTEC electric power plant;
[00025] Figure 3 illustrates another exemplary OTEC electric power plant;
[00026] Figure 4 illustrates a sectional view of a heat exchanger arrangement for the OTEC power plant of Figure 3;
[00027] Figure 5 illustrates a shell and tube heat exchanger;
[00028] Figure 6 illustrates a plate heat exchanger;
[00029] Figure 7 illustrates another plate heat exchanger;
[00030] Figure 8 schematically illustrates a multi-stage heat exchange system;
[00031] Figure 9 illustrates a heat exchange module for a multi-stage heat exchange system;
[00032] Figure 10 illustrates a perspective view of a four-stage heat exchange system;
[00033] Figure 11 is a perspective view of a heat exchange module for the multi-stage heat exchange system of Figure 10;
[00034] Figure 12 illustrates a perspective view of a simple heat exchanger arrangement;
[00035] Figure 13 illustrates a perspective view in cross section of the heat exchanger arrangement, as seen along lines 13-13 of Figure 12;
[00036] Figure 13A illustrates an enlarged view of a portion of Figure 13;
[00037] Figure 14 illustrates a plan view of the heat exchange plate;
[00038] Figure 15A illustrates an end view of a flange connector;
[00039] Figure 15B illustrates an exploded view of the flange connector of Figure 15A;
[00040] Figure 16 illustrates a side sectional view of a collector portion including flange connectors;
[00041] Figure 17 illustrates a perspective view of a clamp;
[00042] Figure 18 illustrates a side sectional view of a portion of the heat exchanger arrangement;
[00043] Figure 19 illustrates a P-h diagram of a conventional high pressure steam power cycle;
[00044] Figure 20 illustrates a P-h diagram of a thermal cycle;
[00045] Figure 21 illustrates a sectional view of an expanded portion of a double-sided plate;
[00046] Figure 22 illustrates a sectional view of an expanded portion of a one-sided plate;
[00047] Figure 23 is a flow chart of method steps for fabricating a heat exchanger arrangement including a collector;
[00048] Figure 24 illustrates a schematic plan view of a plate including an air injection port;
[00049] Figure 25 illustrates a schematic plan view of another plate including an air injection port;
[00050] Figure 26 illustrates a plan view of a portion of a plate including the flap;
[00051] Figure 27 illustrates a plate plate and an alignment template used to align the plates on the stack;
[00052] Figure 28 illustrates a sectional view along lines 28-28 of Figure 26;
[00053] Figure 29 illustrates a sectional view of Figure 28 after cutting and joining plate to form a collector chamber;
[00054] Figure 29A is a partial sectional view of a collector feed chamber including overlapping joints;
[00055] Figure 30 illustrates an exploded view of a potting;
[00056] Figure 31 illustrates a schematic side view of the heat exchanger stack arranged with the flap portion of the potting;
[00057] Figure 32 illustrates a side view of two heat exchanger arrangements, in which the collector flange connectors are connected using a clamp;
[00058] Figure 33 illustrates a perspective view in longitudinal section of a partially assembled evaporation unit;
[00059] Figure 34A illustrates an exploded end view of another flange connector;
[00060] Figure 34B illustrates an exploded side view of the flange connector of Figure 34A;
[00061] Figure 35 is a sectional view of a condenser collector illustrating other flange connectors;
[00062] Figure 36 is a top perspective view of an evaporator heat exchanger plate;
[00063] Figure 37 is a sectional view of a portion of the heat exchange plate of Figure 36, as seen along line 37-37;
[00064] Figure 38 is a top view of the heat exchange plate of Figure 36;
[00065] Figure 39 is a top perspective view of a condenser heat exchange plate;
[00066] Figure 40 is a sectional view of a portion of the heat exchange plate of Figure 38, as seen along line 40-40;
[00067] Figure 41 is a top view of the heat exchange plate of Figure 39;
[00068] Figure 42 is a sectional view of a portion of the heat exchange plate, as seen along line 42-42 of Figures 38 and 41;
[00069] Figure 43 is a sectional view of a portion of the heat exchange plate, as seen along line 42-42 of Figures 38 and 41;
[00070] Figure 44 is a sectional view of a portion of the heat exchange plate, as seen along line 42-42 of Figures 38 and 41;
[00071] Figure 45 is a sectional view of a portion of the heat exchange plate, as seen along line 42-42 of Figures 38 and 41;
[00072] Figure 46 is a top view of a heat exchange plate illustrating the location of zones 1, 2, 3 with respect to the plate;
[00073] Figure 47 is a top end view of an arrangement enclosed in a cocoon;
[00074] Figure 48 is a perspective view of the arrangement and cocoon of Figure 47;
[00075] Figure 49 is a perspective view of the arrangement and cocoon of Figure 48 including a handle;
[00076] Throughout the various drawings the same reference symbols indicate similar elements. Detailed Description
[00077] High efficiency multistage heat exchanger devices and systems will be described in this. An exemplary configuration is provided where multi-stage heat exchange devices and components are used in an OTEC power plant, in which hot water supply ducts and cold water supply ducts and heat exchangers are structurally integrated into one floating or terrestrial platform and used to drive a thermal engine. As discussed above, an OTEC process is a process that uses thermal energy from the sun stored in the oceans to generate electricity. The OTEC process uses the temperature difference between hot surface water and cold deep water in tropical regions to operate a Rankine cycle, where hot surface water serves as a heat source and cold deep water serves as a heat sink. heat. Rankine cycle turbines move generators to produce electricity.
[00078] Although heat exchange devices and systems are described in this with reference to OTEC electric power plants, heat exchange devices and systems are not limited to use in OTEC electric power plants. For example, the heat exchange devices and systems described in this may be useful in other applications that require high efficiency heat exchange, such as steam discharge condensers and other waste heat conversion devices and passive cooling systems. nuclear plants, as well as solar desalination plants. Figure 1 illustrates a typical Rankine OTEC 10 cycle thermal engine that includes hot water input from the sea 12, evaporator 14, hot water output from the sea 15, turbine 16, cold water input from the sea 18, condenser 20, water outlet cold sea 21, working fluid duct 22, and working fluid pump 24.
[00079] In operation, engine 10 can use any of a number of working fluids, for example, commercial refrigerants, such as ammonia. Other working fluids may include propylene, butane, R-22 and R-134a, and their substitutes. Hot sea water between approximately 23.88 ° C and 29.44 ° C (75 ° F and 85 ° F) or more is captured at the ocean surface or just below the ocean surface through the hot water inlet. Mar 12 and in turn heats the ammonia working fluid that passes through the evaporator 14. The ammonia boils to a vapor pressure of approximately 942.32 KPa (9.3 atm). The steam is conducted along the working fluid duct 22 towards turbine 16. Ammonia vapor expands as it passes through turbine 16 producing energy to move electric generator 25. Ammonia vapor then enters condenser 20, where it is cooled to liquid condition by the cold seawater captured at a depth of approximately 914.4 m (3000 feet). Cold sea water enters the condenser at a temperature of approximately 40 ° F. The vapor pressure of the ammonia working fluid at a temperature of approximately 10.55 ° C (51 ° F) in condenser 20 is 618.08 KPa (6.1 atm). Thus, a significant pressure differential is available to move the turbine 16 and generate electricity. As the ammonia working fluid condenses the working fluid, the liquid is pumped back to the evaporator 14 by the working fluid pump 24 via the working fluid duct 22.
[00080] The thermal engine 10 in Figure 1 is essentially the same as a Rankine cycle engine used in most steam turbines, except with respect to the fact that it uses different fluids at lower temperatures and pressures. The thermal motor 10 in Figure 1, which is similar to those in commercial refrigeration installations (for example, a thermal pump using electrical energy) except with respect to the fact that the OTEC cycle is carried out in the opposite direction of the thermal source (for example, water hot water from the sea) and the heat sink (for example, water from the depths of the ocean) are used to produce electricity.
[00081] Figure 2 illustrates the components of a conventional floating OTEC electric power plant 200 that includes a vessel or platform 210, hot sea water inlet 212, hot water pump 213, evaporator 214, hot water outlet from the sea 215, a turbocharger 216 cold water pipe 217, cold water inlet 218, hot water pump 219, condenser 220, cold water outlet 221, working fluid duct 222, working fluid pump 224, and tube 230. The OTEC 200 plant can also include generation, transformation, and transmission systems, position control systems, propulsion equipment, or mooring systems, as well as various support and auxiliary systems (for example, to house personnel, systems emergency, drinking water systems, black and gray, fire systems, damage control systems, flotation, and other naval or marine systems).
[00082] OTEC power plant implementations use a basic thermal engine and the systems in Figures 1 and 2 have a relatively low overall efficiency of 3% or less. Because of this low thermal efficiency, OTEC operation requires the flow of large volumes of water through the electrical energy system per kW of generated energy. This, in turn, requires large heat exchangers, having a large heat exchange surface.
[00083] The system and solutions described meet technical challenges to improve the efficiency of OTEC operations and reduce construction and operating costs.
[00084] The OTEC 10 thermal motor described in this one uses a high efficiency thermal cycle to produce electrical energy with maximum efficiency. Heat transfer in boiling and condensation processes, as well as materials and heat exchange projects limit the amount of energy that can be extracted from each pound of hot sea water. The heat exchangers used in the evaporator 214 and condenser 220 use a large volume of hot water and cold water with low pressure drop to limit parasitic loads. Heat exchangers also provide high heat transfer coefficients to increase efficiency. The heat exchangers incorporate materials and designs adjusted to the hot and cold water inlet temperatures, to increase efficiency. The design of the heat exchanger must provide a simple construction, using a small amount of material in order to reduce volume and cost.
[00085] The 216 turbo generators are very efficient and have a low level of internal loss, and can also be adjusted to a working fluid to further increase efficiency.
[00086] Figure 3 illustrates an OTEC system implementation that increases the efficiency of previous OTEC power plants and overcomes many of the associated technical challenges. This implementation comprises a vessel column or platform with heat exchangers and associated hot and cold water piping, integrated with the column.
[00087] Column 310 houses an integral multi-stage heat exchange system for use with an OTEC electric power plant. The column 310 includes a platform 360 superimposed on a submerged portion 311 under the water line 305. The submerged portion 311 comprises a hot water intake portion 340, evaporator portion 344, hot water discharge portion 346, condenser portion 348, cold water intake portion 350, cold water pipe 351, cold water discharge portion 352, machinery deck portion 354.
[00088] In operation, cold sea water at a temperature of 23.88 ° C and 29.44 ° C (75 ° F to 85 ° F) is captured through the cold water catchment portion 340 and descends the column 310 through a cold water duct, structurally integrated with the column (not shown). Due to the large volume requirement of OTEC thermal engine water flow, the cold water ducts direct the flow to the 344 evaporator portion between 500,000 and 6,000,000 gpm. The cold water ducts have a diameter of 1.82 m to 10.66 m (6 to 35 feet) or more. Due to their size, the cold water ducts are vertical structural members of the 310 column. The cold water ducts can be large diameter tubes with sufficient strength to support the 310 column vertically. Alternatively, the cold water ducts can be integrated passages. to the construction of column 310.
[00089] Cold water then flows through the evaporator portion 344 which houses one or more stacked multi-stage heat exchangers configured to operate evaporators 314 to heat working fluid to the vapor condition. Hot sea water is then discharged from column 310 via hot water discharge 346. Hot water discharge can be located or directed via hot water discharge tube to a depth close to the ocean's thermal layer having approximately the same hot water discharge temperature, to limit any environmental impact. The discharge of hot water can be directed to a depth sufficient to prevent thermal recirculation with either the collection of hot water or the collection of cold water.
[00090] Cold sea water is captured at a depth between 762 m and 1280.16 m (2500 and 4200 feet) or more, at a temperature of approximately 40 ° F via cold water pipe 351. Cold sea water enters the column 310 via cold water portion 350. Due to the large water flow requirement of OTEC thermal engines, cold sea water ducts direct a flow of 500,000 to 6,000,000 gpm to condenser portion 348. Such cold water ducts sea have a diameter between 1.82 m and 10.66 (6 and 35 feet) or more. Due to their size, the cold sea water ducts are vertical structural members of the 310 column. Cold water ducts can be large diameter tubes having sufficient strength to support the 310 column vertically. Alternatively, the cold water ducts can be passageways integrated into the construction of column 310.
[00091] Cold sea water then rises through condenser portion 348, which houses stacked multistage heat exchangers, which are configured to operate as 320 condensers where cold sea water cools the working fluid to liquid condition . Cold sea water is then discharged from column 310 via cold sea water discharge 352. Cold water discharge can be located or directed via cold sea water discharge pipe to a depth or close to a thermal layer of the ocean which is approximately at the same temperature as the discharge of cold sea water. The discharge of cold water can be directed to a depth sufficient to avoid thermal recirculation with either hot water or cold water intake.
[00092] The machinery deck portion 354 can be arranged vertically between the evaporator portion 344 and the condenser portion 348. Placing the machinery deck portion 354 under the evaporator portion 344 allows hot water to flow in one line almost straight from capture, through multi-stage evaporators, to discharge. Positioning the machinery deck portion 354 above the condenser portion 348 provides a flow of cold water in an almost straight line from the intake, through the multistage condensers, and to the discharge. The deck deck of machinery 354 includes turbo generators 356. In operation, the hot working fluid heated to the vapor condition flows from the evaporator portion 344 to one or more turbo generators 356. The working fluid expands in the turbo generator generator 356, from there moving the turbine and producing electrical energy. The working fluid then flows to the condenser portion 348, where it is cooled to a liquid condition and pumped to the evaporator portion 344.
[00093] Figure 4 illustrates an implementation of a system, where several multistage heat exchangers 420 are arranged around the periphery of the column 310. In particular, the heat exchangers are arranged so that they extend along a radius in the column 310, in a streaked configuration. The heat exchangers 420 can be evaporators or condensers used in a thermal engine. The peripheral layout of the heat exchangers can be used with an evaporator portion 344 or condenser portion 348 of column 310. The peripheral arrangement can support any number of heat exchangers 420 (for example, a heat exchanger, between 2 and 8 8 to 16 or 32 or more exchangers). One or more heat exchangers 420 can be arranged peripherally on one deck or multiple decks (for example, 2, 3, 4, 5 or 6 or more) of column 310. One or more exchangers can be peripherally moved between two or more decks , so that two exchangers are not vertically aligned overlapping. One or more heat exchangers can be arranged peripherally, so that the exchangers on one deck are vertically aligned with exchangers on an adjacent deck.
[00094] Adjacent heat exchangers 420 may comprise a multistage heat exchange system (for example, 2, 3, 4, 5, 6 or more heat exchange systems). In some configurations, individual heat exchangers 420 are built to provide low pressure loss over the flow of hot water, flow of cold water, and flow of working fluid for each heat exchanger.
[00095] It has been found that multi-stage heat exchange systems allow a high energy transfer to the working fluid from a non-working fluid (eg water) within a relatively low temperature differential, for example example of an OTEC thermal engine. The thermodynamic efficiency of an OTEC plant depends on how close the working fluid temperature approaches the water temperature. The physics of heat transfer determines that the area required to transfer energy increases as the temperature of the working fluid approaches the temperature of the water. Increasing the speed of the water correspondingly increases the heat transfer coefficient to compensate for the increase in surface area. However, increasing the speed of the water can greatly increase the required pumping energy, thereby increasing the parasitic electrical charge in the OTEC plant.
[00096] In some configurations, a four-stage hybrid cascade heat exchange cycle improves the thermodynamic efficiency of the thermal engine, thereby reducing the amount of energy that needs to be transferred between the fluids. This, in turn, reduces the amount of heat exchange surface required. A hybrid cascade heat exchange cycle is described in detail in US Patent Application No. 13 / 209,944 entitled "Staved Ocean Thermal Energy Conversion Power Plant - Cold Water Pipe Connection", and US Patent Application No. 13 / 209,865 entitled "Ocean Thermal Energy Conversion Power Plant, both incorporated in this, by reference, in their entirety.
[00097] The performance of heat exchangers is affected by the temperature difference between the fluids, as well as by the heat transfer coefficient on the heat exchanger surfaces. The heat transfer coefficient generally varies with the speed of the fluid passing through the heat exchanger surfaces. Higher fluid velocities correspondingly require higher pumping energy, thereby reducing the plant's net efficiency. A multi-stage cascade hybrid heat exchange system employing gasket-free open-plate heat exchanger arrangements provides higher fluid speeds and higher efficiencies for the plant, since the heat exchanger arrangements of open flow without gaskets are stacked along the direction of the fluid flow, allowing free flow for the fluid to / through the system as further discussed below. Thus, the pressure losses associated with the fluid supply for the plate heat exchanger arrangement are substantially eliminated, and relatively high speeds are achieved through the heat transfer surfaces of the plates in the arrangement. This can be compared with traditional plate changer arrangements, where high pressure losses occur, while fluids are supplied to the plate, particularly in the supply lines and openings between the lines and plate changer arrangement. In such traditional plate changer arrangements, the pressure losses that occur while a fluid is supplied to the plates allow for a relatively low fluid velocity across the heat transfer surfaces of the plates in the arrangement, providing a relatively low corresponding heat transfer. The hybrid cascade multistage heat exchanger design also provides a lower pressure drop across the exchanger and the installation's vertical arrangement provides a lower pressure drop across the entire system.
[00098] An integrated multistage OTEC power plant can produce electricity using a temperature differential between surface water and deep water in tropical and subtropical regions. Traditional seawater pipes can be eliminated using vessel structures or platforms such as a duct or flow passage. Alternatively, cold water / hot water pipes can use ducts or pipes of sufficient size and strength to provide vertical support or other structural support to the vessel or platform. These sections, duct or integrated passages are formed as structural members of the vessel or platform, hence reducing the requirements for an additional amount of steel. As part of integrated seawater passages, a multistage heat exchange system provides multiple stages of working fluid evaporation, without requiring external nozzles or pipe connections. Integrated multistage OTEC plants allow cold water / hot sea water to flow in its natural direction. The warm sea water descends through the column as it is cooled, before being discharged into a colder area of the ocean. Similarly, cold seawater from the depths of the ocean rises through the column as it is heated, before being discharged into the hottest part of the ocean. This arrangement avoids the need to change the flow direction and the consequent pressure losses. This arrangement also reduces the required pumping energy.
[00099] Multistage heat exchanger systems allow the use of a hybrid cascade OTEC cycle. In multi-stage heat exchanger systems, heat exchangers are stacked to form multiple heat exchanger stages or sections having sea water passing through them in series or condensing the working fluid, as appropriate. In the evaporator section, the sea water passes through a first stage, where some of the working fluid boils as the sea water is cooled. The hot water then lowers the additional battery to the next heat exchanger stage and boils at a slightly lower pressure and temperature. This happens sequentially on the stack. Each stage or section of the heat exchange system supplies steam from the working fluid to a dedicated turbine to generate electricity. Each evaporator stage has a corresponding condenser stage at the turbine outlet. Cold water passes through the condenser cells in reverse order with respect to the evaporators.
[000100] OTEC systems by their nature require large volumes of water, for example, a 100 MW power plant may require, for example, a quantity of water that is greater in orders of magnitude than that required by a coal-size plant similar. In one implementation, a 25 MW power plant may require approximately 1,000,000 gpm of hot water for evaporators, and approximately 875,000 gpm of cold water for condensers. The energy required to pump water with small temperature differences 1.6 ° C to 7.22 ° C (35 ° F to 45 ° F) acts to lower efficiency, while increasing the cost of construction.
[000101] Currently available heat exchangers are insufficient to handle the large volumes of water and high efficiencies required for OTEC exchanger operations. As in Figure 5, housing and tube exchangers have a series of tubes. A set of tubes contains working fluid that must be heated or cooled. The second non-working fluid runs along the tubes being heated / cooled, so that they can introduce or absorb heat, as required. The set of tubes is a bundle of tubes and can be made of several types of tubes, either smooth or finned, etc .. Housing and tube exchangers are typically used for high pressure applications. This is because the shell and tube heat exchangers are robust due to their shape. Housing and tube exchangers are not ideal for the nature of small pressure differential, low pressure, and high volume of OTEC operations. For example, in order to supply the large volumes of fluid required in OTEC operations, traditional tube and housing exchangers require a complicated piping arrangement, which is associated with high pressure losses that increase the pumping energy. In addition, traditional housing and tube exchangers are difficult to manufacture, install, and maintain, particularly in dynamic environments, such as ocean platforms. Heat exchangers also require precise assembly, in particular with regard to the connections of the housing with tubes and internal supports. In addition, housing and tube exchangers often have a low heat transfer coefficient and are restricted with respect to the volume of water they can accommodate.
[000102] Figure 6 shows a plate and frame heat exchanger. Plate and frame heat exchangers can include multiple slightly separated thin plates having a large surface area and fluid flow passages for heat transfer. This stacked plate can be more effective in a given space than the housing and tube exchanger. Advances in gasketing and brazing technology are making plate-type exchangers more and more practical. When used in open loop, these exchangers are usually of the gasket type to allow disassembly, cleaning and periodic inspection. Definitely mounted plate exchangers such as immersion brazed and vacuum brazed plates, often specified for closed loop applications such as refrigeration. Plate changers also differ with respect to the type of plate used and plate configurations. Some plates can be stamped with a "chevron" engraving or other designs, and still others may have fins and / or machined grooves.
[000103] Plate and frame heat exchangers, however, have significant disadvantages in OTEC applications. For example, these types of exchangers require complicated piping arrangements, which do not easily accommodate the large volumes of water required by OTEC systems. Often, gaskets must be precisely adjusted and maintained between pairs of plates, and substantial compressive forces applied to plates and screw gaskets are required to maintain the gasket seals. Plate changers typically require complete disassembly to inspect and repair a defective plate. Materials required for heat exchangers may be limited to titanium and stainless steel, which are expensive materials. These types of plate changers inherently provide relatively equal flow areas for both working and non-working fluid. Flow ratios between fluids are typically 1: 1. As seen in Figure 6, inlet and outlet passages are typically provided on each face of the plate, reducing the surface area of the heat exchanger and complicating the flow path of working fluid and non-working fluid. In addition, plate and frame heat exchangers include complex internal circuitry for nozzles that penetrate all plates. The complex flow paths also cause a significant loss of pressure, which does not contribute to heat transfer.
[000104] Referring to Figure 7, it is proposed in this, in order to overcome the limitations of the plate exchangers described above, the use of heat exchangers in which the working fluid is supplied and discharged from each plate through tubes connected to the lateral edge of the plates, in order to reduce an obstruction on the face of the plate or an impediment to the flow of heat exchanger plate by the working fluid. On these heat exchanger plates, one end of each pipe is joined to the plate using a welded connection while the other end of the pipe is joined to a head using a welded or mechanical joint connection. As discussed further below, each card requires as much as four input connections and eight output connections. At densities of approximately 20 plates per linear foot, as much as 4800 individual connections can be required in a 6.06 m (20 foot) module. This causes problems with respect to logistics and quality control. When used in an OTEC 10 thermal engine, the connections are also exposed to the seawater environment.
[000105] To overcome the limitations of the heat exchangers described above, an open-flow heat exchanger without gasket is provided. In some implementations, individual boards are aligned horizontally in a cabinet, in order to provide a space between each board. A trajectory for the working fluid follows through the interior of each plate, in an arrangement that provides a high heat transfer (for example, alternating coil, chevrons, z arrangement, and the like). The working fluid enters each plate through a collector provided on the side of the plates, in order to reduce obstructions on the face of the plate or impediments to the flow of water by the working fluid, as further discussed below. Non-working fluid, such as water, flows vertically through the cabinet, and fills the space between each of the open-flow plates. In some implementations, the non-working fluid makes contact with all sides of the open-flow plates or with only the front and rear surfaces of the open-flow plates.
[000106] The open-flow heat exchanger without gasket including a collector to supply and discharge the working fluid entirely eliminates the use of pipe connections for the head. In some cases, the input and output connections are formed integrated with the board and soldered to the adjacent board during the assembly process. Once the connections are welded, the assembly can be encapsulated in epoxy, which epoxy flows between the cartridges to provide structural reinforcement to the assembly, and to prevent seawater from contacting the welded surfaces, as discussed further below.
[000107] Referring to Figure 8, a 520 multistage heat exchange system includes multiple heat exchanger modules 521, 522, 523, 524 in a vertically stacked configuration. In this configuration, each of the modules 521, 522, 523, 524 corresponds to a stage of the 520 system. In some implementations, for example, when used as an evaporator 314 in column 310, the stacked heat exchanger modules accommodate the hot water of the sea 570 that descends through the system 520, from the first evaporator module 521 to the second evaporator module 522, third evaporator module 523, and fourth evaporator module 524 (Figure 8). In other implementations, for example, when used as condenser 320 in column 310, hot sea water rises through system 520 from first condenser module 531, to second condenser module 532, third condenser module 533, and fourth condenser module 534. In In one configuration, working fluid 580 flows through working fluid ducts in each heat exchange module horizontally, compared to the vertical flow of hot sea water or cold sea water. The vertical multistage heat exchanger design of the 520 heat exchange system facilitates the design of an integrated heat exchanger vessel (ie a column) eliminates the requirements for interconnecting piping between heat exchanger stages; and ensures that virtually any pressure drop from the heat exchanger systems occurs over the heat transfer surface. Thus, the flow direction can be from top to bottom, or from bottom to top. In some configurations the flow direction can be the natural direction of the water while the water is heated or cooled. For example, when a working fluid is condensed, water can flow through the module arrangement stacked vertically from the bottom to the top, in the natural convection direction as the water is heated. In another example, when a working fluid evaporates, water can flow from the top to the bottom, as the water cools. In still other configurations, the non-working fluid flow can be horizontal in the system, that is, from left to right or right to left. In other configurations, the right flow can be vertical or horizontal, or a combination of horizontal and vertical.
[000108] Figure 9 schematically illustrates details of a single heat exchanger module 524 of the multistage heat exchange system 520. The heat exchanger module 524 supports multiple heat exchanger plates 1022. Non-working fluid 570 flows vertically through the heat exchange module 524 and passes through each of the plates 1022. The full arrows indicate the direction of the flow of the non-working fluid 570, which in this case is water.
[000109] The open-flow heat exchange module 524 includes a cabinet face 1030 and cabinet side 1031. Opposite the cabinet face 1030 can be found the cabinet face 1032 (not shown), and opposite the side of cabinet 1031 can be found on cabinet side 1033. Cabinet faces 1030, 1032, and cabinet sides 1031 and 1033 form a plenum or water duct through which the non-working fluid flows with little (if any) loss of pressure due to the piping. In contrast to a gasketed plate exchanger, described above with reference to Figure 6, the open-flow heat exchange module 524 uses sides and cabinet faces to form a flow chamber containing the non-working fluid 570 (for example, example, sea water), instead of using gaskets between plates to form the flow chamber containing the non-working fluid 580. Thus, the open-flow heat exchange module 524 effectively has no gasket. This aspect of this system provides significant advantages over other plate and frame exchangers that rely on gaskets to isolate the working fluid from the media that provides energy (ie, sea water). For example, the corrosion test of plate and aluminum frame exchangers carried out in NELHA in the 80s and 90s, had to be stopped after only six months due to the amount of leaks that occurred around the gaskets, where biological deposits caused a intense corrosion. Plate and frame exchangers using gaskets rely on compressive forces to seal the gaskets against the plates. To mount the unit, additional space is required to insert uncompressed plates and gaskets, and then a screw arrangement is tightened to about 50% of its original length. Depositors of this have identified gasket problems as the most important obstacle to the use of plate and frame design in an OTEC system.
[000110] In addition, the module solution with inlet and outlet passages mounted on the side edge for the heat exchanger plates eliminates the need for intake and discharge passages typically provided on the face of the plate heat exchanger systems (see , for example, Figure 5). This solution increases the total heat exchanger surface areas of each plate as well as simplifying the flow path of working and non-working fluids. Removing the gaskets between the plates also eliminates significant obstructions that cause resistance to flow. Open-flow heat exchanger modules without gasket reduce back pressure and associated pumping demand, thus reducing the parasitic load associated with the OTEC installation, providing an increase in the production of electrical energy, which can be transmitted to the utility company .
[000111] In the case of an OTEC 320 capacitor, module 524 is opened at the bottom to supply raw cold water and opened at the top to provide unobstructed fluid communication with module 523 above. The final module in the vertical series 521 is open at the top for the raw water discharge system.
[000112] In the case of an OTEC 314 evaporator, module 521 is opened at the top for raw hot water supply and opened at the bottom to provide unobstructed fluid communication to module 522 below. The final module 524 in the vertical series opens at the bottom for the raw hot water discharge system.
[000113] Referring to Figure 10, an exemplary configuration of a multistage heat exchange system 520 used in an evaporator 314 includes four heat exchanger modules 521, 522, 523, 524. In this configuration, each heat exchange module heat corresponds to a stage of the four stages of the heat exchange system 520. The four heat exchanger modules 521, 522, 523, 524 are supported in a support frame 540 which in turn is supported in the evaporator portion 344 by a pillar 550. The four heat exchanger modules 521, 522, 523, 524 are identical, and therefore only the lower module 524 will be described in detail.
[000114] Referring to Figure 11, the heat exchange module 524 includes several heat exchanger arrangements 1000 supported on a support 1002. Support 1002 is configured to cooperatively engage the support frame 540, when mounted on the exchange system multistage heat exchanger 520.
[000115] Referring to Figures 9 and 12 to 13, each heat exchanger arrangement 1000 includes multiple open-flow heat exchanger plates 1022. Each open-flow plate 1022 has a front face 1040 and a back face 1042 and a peripheral face 1044. In each of the heat exchanger arrangements 1000, the heat exchanger plates 1022 are stacked along a geometric axis 1005 that extends perpendicularly to the front and back face 1040, 1042. In the illustrated configuration, the alignment geometry axis 1005 extends horizontally, so that the heat exchanger plates 1022 are arranged horizontally aligned. In addition, a space 1025 is provided between adjacent plates 1022.
[000116] Front face 1040 and back face 1042 provide non-working fluid heat transfer surfaces for each plate 1022. The internal working fluid passage 1055 described further below provides working fluid heat transfer surfaces for each plate 1022. The efficiency of the heat transfer surface can be improved using the shape, treatment, and surface spacing described in this. Material selection, such as aluminum alloys, offers superior economic performance over titanium-based designs. The heat transfer surface comprises 100, 3000, or 5000 Series aluminum alloys. The heat transfer surface may comprise titanium and titanium alloys.
[000117] The peripheral edge 1044 of each plate 1022 includes a top edge 1045, bottom edge 1046, right edge (or rear) 1048, as in Figure 14. As used in this, references to the direction ie "front" and " back "," top and "bottom", "left" and "right" are provided with respect to the orientation of the arrangement shown in Figure 12, which illustrates an evaporator configuration and are not limiting. For example, when module 524 is used in a capacitor configuration, the module 524 is inverted (rotated 180 ° in space around the alignment geometry axis 1005) so that the top edge 1045 of the plate becomes the bottom edge 1045 '(not shown).
[000118] The plates 1022 are arranged in horizontally aligned stacks so that the rear face 1042 of a first plate 1051 faces the front face 1040 of a second plate 1052 adjacent and immediately behind the first plate 1051, and the respective peripheral edges 1044 of each plate are aligned. To ensure that uniform spacing is provided between adjacent plates 105, 1052 (for example, to ensure that each space 1025 has the same dimension) slotted support plates 1006, 1008 are provided on the front and back sides of the stack. The first support plate 1006 is arranged along the front side of the stack and extends from the flap 1070 to the bottom edge of the plates 1022. The second support plate 1008 is arranged along the back side of the stack and extends from the top edge to the bottom edge of the plates 1022. The surfaces facing the stack of the support plates 1006, 1008 include grooves that receive the respective front side edges 1048 or posterior side edges 1047 of each plate in the stack, the slot spacing corresponds to the desired plate spacing.
[000119] Working fluid 580 is supplied and discharged from working fluid passage 1055 at the peripheral edge of each plate 1022 using collector 1080 (Figure 12) to avoid an obstacle to the flow of raw water through spaces 1025 as the non-working fluid passes front face 1040 and back face 1042 of the plurality of plates 1022 in support 1022. For example, in the illustrated configuration, the collector 1080 is provided along the right edge 1048.
[000120] Each of the 1022 plates includes a 1055 working fluid passage internal to the plate. The collector 1080 makes fluid communication with the passage of the working fluid flow 1055 from each plate 1022 of the heat exchanger arrangement 1000 and supplies working fluid to each plate 1022 of the heat exchanger arrangement.
[000121] Referring to Figure 14, the working fluid passage 1055 can be formed of several 1912 mini-channels. The mini-channels that provide internal flow paths in each open flow plate are arranged in an alternating coil arrangement so that the flow of working fluid 580 is substantially perpendicular or cross-flowing with the direction of flow n of non-working fluid 570. In addition, the progression of working fluid 580 through the coil arrangement can generally be parallel to the fluid flow 570 non-working or opposite to the 570 non-working fluid flow direction. In some configurations, guide vanes and variable flow path dimensions can be implemented to smooth the flow distribution between channels, to smoothly direct the fluid to subsequent channels , when the direction of flow is reversed. These and other channel components and configurations are described in US Patent Application No. 13 / 209,944 with the name Staved Ocean Thermal Energy Conversion Power Plant - Cold Water Pipe Connection, incorporated herein by reference in its entirety.
[000122] It has been found that the working fluid changes phases from liquids to steam along the flow path and consequently the drop in working fluid pressure increases significantly if the same flow passage area is used throughout heat exchanger plate. To reduce the increase in fluid pressure drop along the flow associated with the change in steam quality, the number of parallel flow passages per pass can be increased along the flow path of the working fluid. For example, the heat exchanger plate 1022 in Figure 14 has two 1911 inlet passages, each feeding the corresponding 1912 mini-channels adjacent to bottom edge 1046. The 1912 mini-channels extend along the plate at the first 1914 transition point The flow from two mini-channels feeds six mini-channels at a first 1914 transition point. The flow from four mini-channels feeds six mini-channels at a second 1916 transition point. 1920 transition point and from eight mini-channels to ten mini-channels at a fourth 1922 transition point. The flow from ten mini-channels feeds twelve mini-channels at a fifth 1924 transition point. The resulting twelve mini-channels discharge through the 1918 fluid outlets .
[000123] The two inlet passages 1911 are supplied with working fluid 580 by the collector 1080. In particular, the collector 1080 includes a collector supply chamber 1084 that extends in a direction parallel to the alignment geometric axis 1005 and communicates flowed with each of the four inlet passages 1911 from each plate 1022 of the heat exchanger arrangement 1000. In addition, the collector 1080 includes a collector discharge chamber 1086 that extends in a direction parallel to the geometric axis 1005, and is separate and isolated from the collector discharge chamber 1086 in the collector 1080. Each of the four 1918 inlet passages on each plate 1051, 1052 makes fluid communication with the collector discharge chamber 1086 and the working fluid 590 is discharged from the eight passages outlet to the 1086 collector discharge chamber.
[000124] To facilitate the connection of the working fluid inlets and outlets to the collector 1080, the collector 1080 includes tabs 1070 that connect the right side edge 1078 of the plate 1022. Each tab 1070 is coplanar with the corresponding plate 1022 and includes internal flap entry passages 1911 of plate 1022. In addition, each flap 1070 includes internal flap exit passages 1074 that fluidly forms and forms extensions of each 1918 working fluid exit passage of plate 1022. An inlet opening 1076 is formed on each flap, which defines a portion of the collector discharge chamber 1084, and an outlet opening 1078 is formed on each flap, which defines a portion of the collector discharge chamber, as discussed below.
[000125] Although the collector feed chamber 1084 and the collector discharge chamber 1086 are structurally similar, the collector feed chamber 1084 for a heat exchanger arrangement 1000 used as an evaporator is smaller than the corresponding collector discharge chamber 1086. This is achieved by forming the flap inlet opening 1076 with a smaller diameter than the flap outlet openings 1078. This difference in size reflects the fact that the working fluid 580 enters the evaporator in liquid condition and the same fluid flows out of the evaporator in the gas condition. Therefore, when the heat exchanger arrangement 1000 is employed as a condenser, the collector supply chamber 1084 is larger than the corresponding collector discharge chamber 1086.
[000126] In use, the collector feed chamber 1084 for the heat exchanger arrangement 1000 used as an evaporator is located lower (for example, after the top edge of the plate 1045) than the collector discharge chamber 1086 This is because the working fluid 580 enters the plate 1022 from the collector supply chamber 1084 in the liquid condition and exits in the gas condition to the collector discharge chamber 1086. Therefore, when the heat exchanger arrangement 1000 is employed in a condenser the relative positions of the collector feed chamber 1084 and collector discharge chamber 1086 with respect to the top edge 1045 are inverted and the flap 1070 is displaced towards the bottom of the plate. The 1085 orifice in the condenser then communicates with the 1911 channels, which opens the working fluid gas to the top of the cartridge to communicate with the 1918 channels. The gas changes phase and the working fluid in the condition liquid falls and is collected at the bottom of the cartridge in channels 1912 in communication with orifice 1084 through which the working fluid in the liquid condition is discharged.
[000127] The collector 1080 includes a collector housing 1088 housing all the flaps 1070 of the plates 1020 within the heat exchanger arrangement 1000. The housing 1088 has an outer periphery in the form of a box and can be formed from a rigid material such as polysulfate-based epoxy resin (hereinafter "epoxy"). Encapsulating the flaps 1070 including the collector feed chamber 1084 and the collector discharge chamber 1086 (evaporator; feed and discharge are inverted for the condenser) in epoxy, welds provided between adjacent flaps 1070 are reinforced and secondary time against leakage of the working fluid are provided. In addition, the encapsulation of the 1070 flaps in epoxy serves to adjust and maintain the spacing of the plate, and structurally reinforce the collector 1080 since the epoxy acts with stiffening reinforcement. Furthermore, advantageously, the encapsulation also seals all joints of contact with non-working fluid 580 (for example, sea water).
[000128] Referring to Figures 15A and 15B, collectors 1080 of adjacent heat exchanger arrangements 1000 within heat exchange module 524 are connected using flange connectors 2000 which allow fluid communication between adjacent collectors 1080, or connection with a fluid supply line. In particular, a flange connector 2000 is provided at each end of the collector feed chamber 1084 and at each end of the collector discharge chamber 1086. Each flange connector 2000 is a frusto-tapered tube including a 2016 shaped side wall. so that the first end of the connector 2002 is larger in size than the second end of the opposite connector 2010 and that the side walls of the connector are curved between the first end of the connector 2002 and the second end of the connector 2010.
[000129] Referring to Figures 12, 15, 16 and 17, the first connector end is used to join the internal flange connector 2000 with the corresponding flange connector 2000a of an adjacent collector 1080 or to a supply line or discharge 2020. The first connector 2002 includes a rim 2004 and an O-ring 2007 is provided in a groove 2006 on the 2008 end face of the first end of the connector 2002. The O-ring 2007 provides a seal that prevents the leakage of fluid from work 580 on the connection surface. In use, a clamp 2022 (Figures 16 and 17) is used to secure the first connector end 2002 of a flange connector 2000 to the first connector end 2002 of the adjacent flange connector 2000a so that the respective second faces 2008 meet , and a fluid communication is provided between the corresponding collector chambers. An exemplary clamp for this purpose is a two-screw high-pressure sanitary clamp.
[000130] The second connector end 2010 has a slightly larger external diameter than that of the corresponding collector supply chamber 1084 or collector discharge chamber 1086, and includes a stepped portion or ferrule 2014 that extends longitudinally outwardly from one face end cap 2021 of the second connector end 2010. The stepped portion 2014 has an outer diameter that corresponds to the inner diameter of the collector feed chamber 1084 or collector discharge chamber 1086. In use, the stepped portion 2014 is received in the corresponding chamber collector supply 1084 or collector discharge chamber 1086, and the second connector end 2010 is attached to the collector 1080. In some configurations, the second collector end 2010 is welded to the collector 1080.
[000131] It should be appreciated that the heat exchanger modules 524, 523, 522, and 521 have similar components and are vertically aligned, so that the horizontally aligned plates 1022 in a module align vertically over the plates in the module below. The spaces 1025 between plates 1022 in a module vertically align with the spaces 1025 between plates 1022 in the module below.
[000132] Referring to Figure 18, which illustrates a side wall sectional view of a portion of the heat exchanger liquid 524, an exemplary implementation of the plate arrangement in a heat exchanger arrangement 1000 includes at least one first open-flow heat exchanger plate 1051 having an outer surface including at least one front face 1041 and one rear face 1042. In use, the outer surface makes fluid communication and is surrounded by non-working fluid 570, such as cold water gross. The first open-flow plate 1051 also includes an internal passage 1055 in fluid communication with a collector 1080 and configured to receive working fluid 580 via the collector 1080. At least one second open-flow heat exchanger plate 1052 is horizontally aligned with the first open-flow heat exchanger plate 1051, so that the front outer face 1040 of the second plate 1052 faces the rear outer face 1042 of the first plate 1051. The first open-flow plate 1051 is substantially identical to the second open-flow plate 1052. That is, like the first plate 1051, the external surfaces of the second plate 1052 make fluid communication and are surrounded by the non-working fluid 570. In addition, the second plate 1080 is configured to receive the fluid working 580.
[000133] The first 1051 open-flow heat exchanger plate is separated from the second 1052 heat exchanger plate through space 1025, and non-working fluid 570 flows through this space 1025. Working fluid 580 flows through of the 1055 working fluid flow passages.
[000134] As described above in some implementations, an isolated 524 heat exchanger module can be dedicated to a stage of a hybrid cascade OTEC cycle. In some implementations, four heat exchanger modules 521, 522, 523, 524 are vertically aligned, as shown and described in Figures 8 and 10. In some implementations, modules having working fluid supply lines and fluid discharge lines workpieces connected to a collector 1080 are located at the peripheral edge 1044 of each plate. This prevents working fluid ducts from being located on faces 1040, 1042 and prevents the flow of working fluid on the faces of plates 1051, 1052 and non-working fluid on the faces of plates 1040 and 1042.
[000135] For example, a multistage heat exchange system without gasket may include the first stage of the heat exchange module comprising open-flow plates in fluid communication with first working fluid flowing through an internal passage in each of the one or more open-flow plates. The working fluid can be supplied and discharged from each plate via the first collector, including a fluid supply chamber 1084 and a fluid discharge chamber 1086, each chamber connected to a peripheral edge of each individual plate. A second stage of the heat exchange module vertically aligned with the first stage of the heat exchange module is also included. The second stage of the heat exchange module includes one or more open-flow plates in fluid communication with a second fluid flowing through an internal passage in each of the open-flow plates. Again, the second working fluid is supplied and discharged to / from each individual plate via a second collector including a fluid supply chamber 1084 and fluid discharge chamber 1086, each chamber connected to the peripheral edge of each individual plate. A non-working fluid, such as water, flows first through the first stage of the heat exchange module around each of the open-flow plates, allowing for a heat exchange with the first working fluid. The non-working fluid then passes through the second stage of the heat exchange module around each of the open-flow plates, allowing for a heat exchange with the second working fluid.
[000136] The first stage of the heat exchange module includes a plurality of horizontally aligned open-flow plates having a space between each plate. The second stage of the heat exchange module also includes a plurality of horizontally aligned open flow plates having a space between each plate within the second stage heat exchange module. The plurality of open flow plates and spaces in the second stage of the heat exchange module are vertically aligned with the plurality of open flow plates and spaces in the first stage heat exchange module. This reduces pressure losses in the non-working fluid flow through the first and second stage heat exchanger modules. Pressure losses in the non-working fluid are also reduced by the fact that the non-working fluid is discharged directly from one module to the next, thereby eliminating the need for an extensive and massive piping system. In some configurations, support plates 1006, 1008 used to maintain spacing of individual plates 1022 in arrangement 1000, and arranged adjacent to the lateral edges of plate 1047, 1048, form the duct through which the non-working fluid flows.
[000137] Due to the open-flow arrangement of the plates in each arrangement of each stage of an exemplary four-stage OTEC system, the flow ratio of the non-working fluid to the working fluid is increased from the ratio 1: 1 typical of conventional plate heat exchanger systems. In some implementations, the non-working fluid flow ratio is greater than 1: 1 (for example, greater than 2: 1, greater than 10: 1, greater than 20: 1, greater than 30: 1, greater than 40: 1, greater than 50: 1, greater than 60: 1, greater than 70: 1, greater than 80: 1, greater than 90: 1, or greater than 100: 1).
[000138] When a multistage arrangement of the heat exchanger modules is used as a condenser the non-working fluid (eg cold sea water) enters the first stage of the heat exchange module at a temperature lower than the temperature in that the non-working fluid enters the second stage heat exchange module, and the non-working fluid then enters the second stage of the heat exchange module at a lower temperature than the temperature at which the non-working fluid work enters the third stage heat exchange module; and the non-working fluid enters the third stage of the heat exchange module at a temperature generally lower than the temperature that the non-working fluid enters the fourth stage heat exchange module.
[000139] When the multistage arrangement of heat exchanger modules are used as an evaporator, the non-working fluid (eg hot sea water) generally enters the first stage of the heat exchange module at a higher temperature than when the non-working fluid enters the second stage of the heat exchange module and the non-working fluid then enters the third stage of the heat exchange module at a higher temperature than when the non-working fluid enters the heat exchange module third stage; and the non-working fluid enters the third stage of the heat exchange module at a temperature generally higher than it enters the fourth stage of the heat exchange module.
[000140] When a multistage arrangement of heat exchanger modules is used as a condenser, the non-working fluid (eg, ammonia) generally leaves the first stage of the heat exchange module at a temperature lower than the temperature at which the working fluid exits the second stage heat exchange module, and the working fluid exits the second stage of the heat exchange module at a lower temperature than the temperature at which the working fluid exits the heat exchange module third stage heat; and the working fluid exits the third stage of the heat exchange module at a temperature generally lower than the temperature at which the working fluid exits the fourth stage heat exchange module.
[000141] When a multistage arrangement of heat exchanger modules is used as an evaporator, the working fluid (eg ammonia) generally leaves the first stage of the heat exchange module at a temperature higher than the temperature at which the working fluid exits the second stage heat exchange module, and working fluid exits the second stage of the heat exchange module at a temperature generally higher than the temperature at which the working fluid exits the heat exchange module third stage heat; and the working fluid exits the third stage of the heat exchange module at a temperature generally higher than the temperature at which the working fluid exits the fourth stage heat exchange module.
[000142] An exemplary heat balance from a four-stage OTEC cycle implementation is described in this one, and generally illustrates these concepts.
[000143] In some implementations, a heat exchange system without gasket includes a first stage of the heat exchange module having open-flow plates. Each plate includes an external surface having at least one front face and one rear face surrounded by a non-working fluid. Each plate also includes an internal passage in fluid communication with a first working fluid flowing through the internal passage. The working fluid is supplied and discharged from each plate by supply and discharge lines dedicated to each plate.
[000144] The four-stage heat exchange system also includes a second stage of the heat exchange module vertically aligned with the first stage of the heat exchange module; The second stage of the heat exchange module includes one or more open-flow heat exchanger plates substantially similar to those of the first stage, and vertically aligned with the plates of the first stage.
[000145] A third stage of the heat exchange module substantially similar to the first and second stage heat exchanger modules is also included and being vertically aligned with the second stage of the heat exchange module. A fourth heat exchanger stage of substantially similar to the first, second, and third stages of the heat exchange module is included and vertically aligned to the third stage of the heat exchange module.
[000146] In operation, the non-working fluid flows through the first stage of the heat exchange module, and wraps around each open-flow plate, for interaction with the first working fluid that flows within the flow passages on each plate. . The non-working fluid then flows through the second stage of the heat exchange module, for thermal interaction with the second working fluid. The non-working fluid then flows through the second stage of the heat exchange module for thermal interaction with the second working fluid, before flowing through the third stage of the heat exchange module, for thermal interaction with the third fluid of work. The non-working fluid flows through the third stage of the heat exchange module for thermal interaction with the third working fluid before flowing through the fourth stage of the heat exchange module for thermal interaction with the fourth working fluid. The non-working fluid is then discharged from the heat exchange system.
[000147] The small temperature differential of OTEC operations (typically between 35 ° F and 85 ° F) requires an unobstructed heat exchanger plate design for the flow of non-working and working fluid. In addition, the plate must provide a sufficient surface area to withstand the conversion of low temperature elevation energy from the working fluid.
[000148] Conventional electrical power generation components typically use a combustion process with a large temperature rise system, such as a power-steam cycle. Since environmental issues and non-compensated fossil fuel supply issues are gaining importance, Low Temperature Lift Energy Conversion (LTLEC) systems, as well as OTEC systems described in this one, which use sources Renewable energy sources, such as solar, and oceanic energy, are correspondingly gaining importance. Although steam-power cycles use gas from combustion processes, and usually at very high temperatures, the LTLEC cycle uses low temperature energy sources ranging from 30 ° C to 100 ° C. Therefore, the temperature difference between the heat source and the heat sink of the LTLEC cycle is much smaller than that of the steam cycle.
[000149] Figure 19 shows the process of a high temperature steam power cycle in a pressure-enthalpy (P-h) diagram. The thermal efficiency of the steam cycle is in the range of 30% to 35%.
[000150] In contrast, Figure 20 shows an LTLEC cycle diagram such as those used in OTEC operations. Thermal efficiency for an LTLEC cycle is 2% to 10%. This is almost a third or a tenth of a high temperature steam power cycle. Thus, an LTLEC cycle needs much larger heat exchangers than a conventional power cycle.
[000151] The heat exchanger plates described in this provide a high heat transfer performance, also a low pressure drop on the side of the heat source and heat sink to limit the power requirements that affect the efficiency of the system. These heat exchanger plates designed for OTEC and LTLEC cycles can include the following components: 1 a working fluid flow path having a mini-cane design - this can be provided with a scroll-cast aluminum heat exchanger plate , and provides a large heat transfer area between the working fluid and the non-working fluid; 2 a space provided between the plates in order to significantly reduce the pressure drop in the heat source and non-working fluid heat breaker - Thus, a relatively wide fluid flow area can be provided for the heat source and heat sink. heat, while maintaining a relatively narrow fluid flow area for the power cycle working fluid; 3 a setting of progressively changing the number of channels per pass within the working fluid flow passages can reduce the working fluid pressure drop by changing the phase along the flow - the number of channels on the plate can be designed accordingly with the working fluid operating conditions and heat exchanger geometry; 4 a corrugated workflow or channel configuration can increase heat transfer performance; 5 within the fluid flow channels and between parallel channels, both ends of the inner channel wall walls of the flow channel can be curved to smoothly direct the fluid to the subsequent channels when the flow direction is reversed and the distance is not uniform at from the ends of the inner channel walls to the side wall can be used between the parallel channels.
[000152] The above aspects can reduce the pumping power required for the system, and improve the heat transfer performance.
[000153] Referring again to Figures 13, 13A and 18, heat exchanger plates joined by mini-channel scrolling 1051 and 1052 are shown in perspective. A counterflow between the working fluid 580 and the non-working fluid 570 is provided. When used as an evaporator, the non-working fluid 570 (for example, sea water) enters the top edge 1045 of the plates 1051, 1052 and leaves the bottom edge 1046 of the plates 1051, 1052. The working fluid 580 (for example, example, ammonia) enters the 1048 right edge of the plates via collector 1080 in liquid condition and evaporates, and finally changes to vapor condition absorbing thermal energy from non-working fluid at a higher temperature. The steam generated leaves the plates through the right edge 1048 via the collector.
[000154] The plates 1051, 1052 can be formed using a rolling fusion process, so that 1055 working fluid flow channels are arranged on the plate itself. Scroll fusion is a manufacturing process whereby two metal panels are fused by heat and pressure, and then expanded with high pressure air to create flow channels between two panels. Before melting, a carbon-based material is printed on the outer surface of a first panel in an arrangement that corresponds to the desired path of the workflow channels. The second panel is then applied over the first panel and the two panels are then rolled through a roller press to form a single plate where the two panels are completely fused everywhere except where there is a carbon material . At least one channel is printed on the peripheral edge where a vibrating mandrel is inserted between the two panels, creating a hole in which pressurized air is inserted. The pressurized air causes the metal to deform and expand in order to create internal channels, with two panels being prevented from melting into each other. There are two means by which a roll fusion can be made, a continuous process, where a sheet of metal runs continuously through rollers, and a batch process, where pre-cut panels are processed individually.
[000155] Referring to Figure 21, in some configurations, two identical panels 1060 are cast by rolling to form the plate 1022 '. For example, the panels are approximately 1.05-1.2 mm thick, 1545 mm long and 350 mm wide and made from the same material. Channels are formed between the joined metal panels, having an arrangement that corresponds to the desired trajectory of the workflow channels by blow molding as discussed above. The 1055 channels are formed with a width between 12 and 13.5 mm and a height of about 2 mm. Once the panels used to form the internal channels being identical, both channels 1060 are deformed during expansion, to form the internal channels, and the channels expand outwardly uniformly on each panel 1060. Both sides (for example, front face 1040 and rear face 1042) of the resulting plate 1051 are profiled and include outwardly extending regions that correspond to expanded sections at the location of the working fluid flow channel 1055. The resulting plate configuration is called a double-sided.
[000156] When a first plate 1051 and second plate 1052 each having a double-sided plate configuration are placed adjacent in a stacked configuration in a 1000 heat exchanger arrangement, plates 1051 and 1052 can be received in one configuration nested. In a nested configuration, plates 1051 and 1052 can be arranged slightly offset from one another, so that the protruding regions of a 1051 plate are within the spaces between the protruding regions of adjacent plate 1052. However, although the fusion process by scrolling provides a plate having a consistent height, there are inherent issues of dimensional repeatability in the direction of the length. This means that the location of each portion of the channels cannot be reliably controlled. For example, in some cases, the protruding regions of the plates are not at the design distance from the top edge 1045 of the plate 1051. During laboratory tests of heat exchangers employing double-sided plates, variations have been found to result dimensions in protruding regions of adjacent plates located in opposite directions from each other resulting in clamping points in the 1025 plate separation, causing higher pressure loss and lower than expected heat transfer.
[000157] Referring to Figure 22, in some configurations, two non-identical panels 1060, 1062 having the same peripheral shape are fused by scroll to form the plate 1022, which meets the dimensional variability problems described above with respect to the configuration of double-sided plate. The two panels 1060 and 1062 are not identical because they have different flow limits. This can be accomplished, for example, by providing panels 1060 and 1062 having different thicknesses or made of different materials. Channels are formed between the fused metal panels having an arrangement that corresponds to the desired path of 1055 working fluid flow channels by blow molding, as discussed above.
[000158] The 1055 working fluid flow channels have a relatively wide width w a relatively low height h to increase the active heat transfer area between the two fluids while reducing the volume of the entire heat exchanger plate. The width w of channels can vary between about 10 mm and about 15 mm (for example, more than 11 mm, more than 12 mm, more than 13 mm, less than 14 mm, less than 13 mm, and / or less than 12 mm). The height h of the channels can vary between about 1 mm and about 3 mm (for example, more than 1.25 mm, more than 1.5 mm, more than 1.75 mm, more than 2 mm, less than 2.75 mm, less than 2.5 mm, less than 2.25 mm and / or less than 2 mm). The spacing between channels can be between about 4 mm and about 8 mm (for example, more than 4.5 mm, more than 5 mm, more than 5.5 mm, less than 7.5 mm, less than 7 mm, and / or less than 6.5 mm).
[000159] The difference in the flow limit of the panels used to form the plate is controlled, so that only one of the 1060 panels is deformed during expansion to form internal channels. In this case, the channels expand outwards from only one side of the plate 1022, resulting in a plate 1022 in which one side (i.e. the front face 1040) includes outwardly protruding regions that correspond to the location of the fluid flow channel. work 1055, and in which the other side (ie the back face 1042) is not deformed, and thus remains generally flat. The resulting plate configuration is called a one-sided plate.
[000160] In the configuration illustrated in Figures 10 to 14, the plates 1051 and 1052 are formed with a one-sided plate configuration. When plates 1051 and 1052 are placed adjacent in a stacked configuration in a heat exchanger arrangement 1000, plates 1051, 1052 are arranged so as to face 1041 of a plate 1052, having protruding regions that correspond to expanded sections in location of the working fluid flow channel, face the rear face 1042 of the adjacent plate 1051, which is generally flat. In addition, adjacent plates 1051, 1052 are arranged so that a space is formed between the front face 1040 of a plate 1052 and the rear face 1042 of adjacent plate 1051. In an exemplary configuration, the adjacent plates 1051, 1052 have a 8 mm edge spacing providing a minimum space dimension between the 1051, 1052 plates of 2.2 mm in locations that correspond to the protruding regions, and a maximum space dimension between the 1051, 1052 plates of 4.8 mm in locations between protruding regions.
[000161] The one-sided plate configuration mitigates the impact of dimensional inconsistency in the direction of the width due to the rolling fusion process. In this configuration, the spacing between adjacent plates has maximum space and minimum space, regardless of where the expansion along the length occurs. Laboratory results confirmed that pressure losses are significantly reduced compared to the double-sided plate configuration for fluid flows and equal nominal spacing.
[000162] In addition, when plate heat exchanger arrangements having a double-sided plate configuration are formed, there is no need to nest, so that the protruding regions of a 1051 plate are within the spaces between the protruding regions of the plate adjacent 1052. Instead, one-sided plates 1051, 1052 are arranged so that the front face 1040 of a plate 1052 having protruding regions faces the generally flat rear face 1042 of adjacent plate 1051. In addition, the regions protrusions are aligned in a direction parallel to the 1005 alignment geometry axis. Although the heat transfer on the flat surface is generally lower than on a surface having protruding regions, this effect is compensated, at least partially, by the turbulence in the space 1025 between plates , caused by the presence of protruding regions in the fluid flow path, resulting in a low pressure drop, but at an increased speed entered in space 1025.
[000163] In all configurations, a non-working fluid flow area is provided wider than the working fluid flow area in the 1055 working fluid flow channels. This arrangement reduces the pressure drop on the sides of heat source fluid and heat sink.
[000164] Referring to Figure 23, a method for making a heat exchanger arrangement 1000 will be described.
[000165] In step 3000, the method includes providing a heat exchanger plate 1022 having an internal fluid passage 1055 arranged in a predetermined design that corresponds to the desired flow path of the working fluid 580. In some configurations, the heat exchanger plate 1022 is provided providing a first panel 1060 and a second panel 1062 and applying an adhesion inhibiting agent to the surface of the first panel 1060 in a predetermined design. The first and second panels are then stacked, so that a melting agent is between the first and second panels. The first and second stacked panels 1060 and 1062 are then rolled together to form a plate 1022.
[000166] The scroll cast plate 1022 is expanded by injecting air between the first and second panels 1060, 1062 to form an expanded plate 1022 having an internal passage 1055. To control the amount of expansion (e.g., h) of the passage internal 1055, and allow different amounts of expansion in different regions of plate 1022, plate 1022 is placed in an expansion template (not shown) during expansion of the passage. The expansion template includes a pair of rigid plates arranged in parallel to the rigid plates having zones with different spacing between them. The 1022 plate is placed in the template in order to be sandwiched between the rigid plates, while the air is injected. Rigid plates limit the amount of passage expansion during air injection according to the arrangement of the zone. For example, in some configurations, the first zone corresponding to the location of the tab 1070 has a first height h1 which is greater than a second height h2 of a second zone which corresponds to the location of 1912 mini-channels.
[000167] Referring to Figure 24, the 1930 air injection port is provided on plate 1022 to facilitate air injection. The 1930 air injection inlet is formed in a 1932 air injection flap located at a peripheral edge 1044 of the 1022 plate. In an illustrated configuration, the 1932 air injection flap and 1930 air injection inlet are located in a side edge 1048 of plate 1022. This position is advantageous since it lies outside the flow path of the non-working fluid 570, and thus does not negatively affect flow pressures and along the fluid. However, the air injection flap 1032 and the air injection inlet 1032 can be provided at other locations on the peripheral edge 1045 or bottom end 1046 (shown in Figure 25).
[000168] After the plate 1022 is expanded, the air injection port 1930 is closed, for example, by clamping the air injection flap and then being fused, for example, by welding. This procedure is performed on all 1022 plates used for the stack (as discussed below) except for the end plates of the stack. In the two extreme plates of the stack, the air injection inlet remains open allowing the ventilation of gases formed in the plates during subsequent manufacturing steps such as brazing; however, the air injection inlets are subsequently closed and fused. In some configurations, the 1032 air injection flap is also used as a connection point, to connect the air from the heat exchanger 1000 to the mounting structures on the heat exchange module 524.
[000169] In configurations where a one-sided plate configuration is employed the method additionally includes providing a first 1060 panel having a lower flow limit than the second 1062 panel. Then during the step of injecting air into the plate the first 1060 panel is deformed by the pressure of the injected air and the second panel remains undeformed by the pressure of the injected air.
[000170] In step 3001, referring to Figure 26, openings are cut in the expanded plate 1022 that intersect the inner passage 1055. More specifically, a flap entry opening 1076 is formed in the flap 1070 at a location that intersects all flap entry passages 1072. In addition, a flap entry opening 1078 is formed on flap 1070 at a location that intersects all flap exit passages 1074. As seen in Figure 26, the fusion inhibiting agent is applied in an arrangement (see hatched areas) that allows adequate reinforcement to allow the precise cutting of the plate. For example, the circular area that corresponds to the internal space of the inlet and outlet opening in the expanded manner, but instead includes a molten portion. In some configurations, cutting is achieved, for example, using a high speed saw having a pilot drilling insert, which helps maintain alignment during cutting or other cutting processes, such as machining or water jet.
[000171] In some configurations, the use of a one-sided plate configuration, in which the first panel 1060 expands in relation to the second panel 1062, the cutting opening is made larger in the first panel 1060 (for example, on the expanded side plate 1022) than on the second panel 1062 (for example, on the unexpanded side of plate 1022).
[000172] In step 3002, the steps of providing a heat exchanger plate 1022 having an internal fluid passage 1055 and cutting openings in plate 1022 are repeated for each plate 1022 of the heat exchanger arrangement 1000, until reaching the number of cut plates 1022.
[000173] In step 3003, the cut plates 1022 are stacked for use in forming a heat exchanger arrangement 1000. In the illustrated configuration, 48 plates 1022 are stacked so that they are arranged on top of each other, where the front faces 1040 are oriented in the same direction and normal to the alignment geometric axis 1005. In particular, the plates 1022 are arranged in an alignment template, to provide a stack of plate 2030 having peripheral edges 1044 and cut openings 1076 and 1078 aligned. It should be understood that a greater or lesser number of plates 1022 can be stacked, and that the number of plates in pile 2030 is determined by the specific application.
[000174] Referring to Figure 27, precise alignment of the 1022 plates can be achieved by stacking cut plates on the alignment template, including one or more alignment devices. In the illustrated configuration, alignment devices include rectangular rods 2032 and cylindrical mandrels 2034, strategically arranged in the jig. When the plates 1022 are placed in the template, the cut openings 1076, 1078 are placed over the mandrels 2034 and the peripheral edge 1044 is placed, so that the rods 2032 cover the inner corners 2036 provided on the peripheral edge 1044 of each plate 1022.
[000175] In configurations where the stacked plates employ a one-sided plate configuration, the step of stacking further comprises arranging the plates 1022, so that the first external heat exchange surface of a plate (i.e. front face 1040) and faces the second external heat exchange surface (ie back face 1042) of an adjacent plate. To ensure that uniform spacing is provided between adjacent plates, slotted support structure plates 1006, 1008 are provided in front of and behind the stack, as discussed above.
[000176] With the cut plates 1022 stacked and aligned, the chucks 2034 are removed from the alignment template to allow the formation of the collector feed chamber 1084 and collector discharge chamber 1086 within the corresponding opening as discussed in step 3004. The 2032 rods remain in place to keep the stack aligned in subsequent steps. In addition, the alignment template remains with the stack assembly to form a cocoon-like encapsulation for the arrangement 1000, to protect it from damage, and, in cooperation with support panels 1006, 1008 serves to channel the flow of fluid from work for the spaces 1025 between the plates 1022, and over the active surface area of heat transfer.
[000177] Referring to Figure 29, in step 3004, the cut edges of the cut openings 1076, 1078 of a first plate 1051 are joined to the corresponding cut edges of an adjacent plate 1052. When the plates are aligned in step 3003, the expanded regions, which correspond to flap entry passages 1072 and flap exit passages 1074, are also aligned in a direction parallel to the alignment geometry axis 1005. In addition, referring to Figures 26, 28 and 29, during expansion of the plate, at least one panel 1060 forming the plate is deformed so that the respective panels 1060, 1062 are locally spaced to provide the passage of the working fluid 1055. Consequently, the back face 1042 of a plate 1051 touches (or almost comes across) the front face 1040 of a second plate 1052 adjacent and underlying the first plate 1051. On each plate 1022 in stack 2030, the front face 1040 is joined to the back face 1042 of the plate above it throughout the entire circle. circumference of each cut-in opening 1076 and cut-out opening 1078. In addition, the back face of each plate in the stack 2030 is joined to the front face 1040 of the underlying plate along the entire circumference of each cut entrance opening 1076 and opening cut-out 1078. The respective faces 1040 and 1042 are joined continuously to form annular joints impermeable to fluid 1082, for example, with TIG welding (welding with tungsten electrode protected by inert gas) (TIG welding) autogenous TIG welding, TIG welding by deposition (sputter) or laser welding. In Figure 29, welds are represented by zigzag lines.
[000178] This procedure results in a collector feed chamber 1084 within the 2030 pile defined in part by the series of annular joints formed at the connection of each adjacent plate along cut openings 1076 and a collector discharge chamber 1086 (shown in Figure 29) defined in part by the annular joints 1082 that correspond to the connection of each adjacent plate along the cut openings of the outlet 1078. In each plate of the stack 2030, the expanded region in each of the cut openings in fluid communication with the channels 1012 of the working fluid passage 1055 as discussed above. For example, the collector feed chamber 1084 makes fluid communication with the inlet passage 1922 via the flap between passage 1072. In addition, the collector discharge chamber 1086 makes fluid communication with the outflow passage 1918 via the outflow passage. with flap 1072. Due to the sealed nature of the annular joints, fluid communication is prevented between the internal passage 1055 and the external surfaces of the plates 1022, and thus also between the working fluid 580 and the non-working fluid 570.
[000179] Referring to Figure 29A, in configurations in which the cut opening is made larger inside the first panel 1060 (for example, on the front face 1040) than inside the second panel 1062 (for example, on the rear face 1042), when the plates are stacked, the L joints are formed. For each plate 1022 in stack 2030, the front face 1041 is joined to the rear face 1042 of the plate above it in the overlapping joint (for example, along the entire circumference of each cut-in opening 1076 and cut-out opening 1078). In addition, the back face 1042 of each plate in stack 2030 is joined to the front face 1040 of the plate below it at the overlapping joint L (for example, along the entire circumference of each cut-in opening 1076 and cut-out opening 1078) . The respective faces 1040, 1042 are joined continuously, for example, by welding, to form a fluid impermeable annular joint 1082.
[000180] As discussed above, the amount of expansion of flap passages 1072, 1074 in flap 1070, at least in the vicinity of the cut openings 1076, 1078, is made greater (for example, having a higher channel height h) than the passage of working fluid 1055 into the plate 1022. With this arrangement, the spacing between adjacent plates 1022 (i.e. plates 1051, 1052) is maintained, while allowing the formation of annular joints.
[000181] In step 3005, again, referring to Figure 16, the flange connector 2000 is welded to the cut flap entry opening and cut flap opening 1078 formed on the outward facing surfaces of the end plates 1022 used to form the stack 2030.
[000182] For the upper end plate 1022u, a flange connector 2000 is attached to the front face 1040 in both openings - cut inlet opening 1076 and cut out outlet 1078. For example, a flange connector 2000 is placed in opening 1076 and 1078 and welded to the cut edge along the entire circumference of each respective opening 1076, 1078, in order to provide a fluid impermeable connection. In addition, the rear face 1042 of the upper end plate 1022u is joined to the front face 1040 of the plate below it along the entire circumference of each cut-in opening 1076 and cut-out opening 1078. The respective faces are continuously merged to form a 1082 fluid impermeable ring.
[000183] The lower end plate 1022u is similarly treated. That is, for the bottom end plate 1022u, the flange connector 2000 is attached to the back face 1042 in both openings - cut inlet opening 1076 and cut out opening 1078. For example, a flange connector 2000 is placed in each opening 1076, 1078 and welded to the cut edge along the entire circumference of each respective opening 1076, 1078, in order to provide an annular connection impermeable to fluid 1082. In addition, the front face 1040 of the lower end plate 1022u is fused to the rear face 1042 of the plate above it along the entire circumference of each cut-inlet opening 1076 and cut-out opening 1078. The respective faces 1040, 1042 are continuously fused to form a fluid impermeable annular joint 1082.
[000184] In step 3006, the formation of the collector 1080 is completed, encapsulating the joined flaps 1070 of the heat exchanger arrangement 1000 in plastic material such as epoxy, to form a collector housing 1088 that encloses all the flaps 1070 of the plates 1020 within the heat exchanger arrangement 1000. The collector housing 1088 is defined by the external surfaces of the epoxy.
[000185] Encapsulation is achieved by placing the joined flaps on the 2030 stack in a 2050 vase, filling it with epoxy, filling the spaces between the inside of the 2050 vase and the outer surface of the joined flaps 1070, allowing the epoxy to cure, and, leaving vessel 250 to remain as part of the assembly.
[000186] Referring to Figure 30, due to the complex shape of the flaps 1070 that extend from the lateral edge 1048 of each plate and include flange connectors 2000 extending outside the outer surfaces of the same, the vessel 2050 is formed with structure multi-piece, which can be mounted on flaps 1070 and around flange connectors 2000. In particular, vessel 2050 is made of plastic, for example, polycarbonate and has a first side wall portion 2052, a second portion of side wall 2054, and a third portion of side wall 2056, which can be assembled together to form the vessel.
[000187] The first side wall portion 2052 includes three sides 2052a, 2052b, 2052c and bottom 2052d. The three sides 2052a, 2052b, 2052c are joined together and also with the bottom 2052d and extend from it. An upper edge 2052e of the first side wall portion 2052 includes cut-out semicircular portions 2052f sized to receive a side wall 2006 of the flange connector 2000. The second side wall portion 2054 number three sides 2054a, 2054b, 2054c. The three sides 2054a, 2054b, 2054c are joined together. In addition, a lower edge 2054e of the second side wall portion 2054 includes cut out semicircular portions sized to receive a side wall 2006 of the flange connector 2000. The third side wall portion 2056 includes a flat panel side having a first edge 2056a, a second edge 2056b, a third edge 2056c, and a fourth edge 2056d.
[000188] During assembly of the 2050 vessel, the heat exchanger unit 1000 is placed over the first side wall portion so that the joined flaps 1070 extend into the space defined by the three sides 2052a, 2052b, 2052c and bottom 2052c and flanges 2000 are arranged within the cutout portion 2052f. The second side wall portion 2054 is then placed along the first upper edge of the side wall portion 2052e, so that the first side of the first side wall portion 2052a joins the first side of the second side wall portion 2054a , the second side of the first side wall portion 2052b joins the second side of the second side wall portion 2054b, the third side of the first side wall portion 2052c joins the third side of the second side wall portion 2054b, and the flanges 2000 are received at the cutout portion of the side wall portion 2052f. Finally, the third side wall portion 2056 is placed joined to the first and second side wall portions 2052, 2054 so that the first edge of the third side wall portion 2056a joins the first sides 2052a, 2054a of the first and second portions of side wall 2052, 2054, the second edge of the third side wall portion 2056b joins bottom 2052d of the first side wall portion 2052, and the third edge of third side wall 2056c joins the third sides 2052c, 2054c of the first and second side wall portions 2052, 2054. With the vessel 2052 mounted, the joined flaps 1070 are enclosed by the side wall portions 2052,2054,2056.
[000189] Referring to Figure 31, in the assembled configuration, the 2050 vessel includes an open upper end and is sized to enclose the joined flaps 1070 while minimizing the amount of epoxy filler required. The 2050 vessel is filled from the bottom with cured epoxy and maintains the plate spacing to seal all sea water joints, and furthermore reinforces the 1000 heat exchanger arrangement. In addition, the epoxy provides a support of supplementary welded joint and reinforcement of the assembly, an additional barrier against the leakage of internal fluid from the welded joint that could occur, and a solid mounting surface for the arrangement of joined plates. During encapsulation, the fluid passages of each flange connector 2000 are closed to prevent contamination of the collector chambers 1084, 1086 with encapsulation material. Once encapsulated, the fluid passages are cleaned to allow proper operation of the respective flange connectors 2000, in particular to allow fluid flow through them. Once the connectors 2000 are cleaned, the heat exchanger unit 1000 is terminated.
[000190] Referring to Figures 11 and 32, when a heat exchange module 524 is formed including several heat exchanger arrangements 1000, the collector 1080 of each individual heat exchanger arrangement 1000 is joined to the collector 1080 of the arrangements heat exchanger 1000. In particular, the respective flange connectors of the collector measuring chamber 1084 of the adjacent heat exchanger arrangements 1000 are joined so that the collector feed chamber 1084 communicates fluidly with each heat exchanger arrangement. heat 1000 of module 524. Similarly, the respective flange connectors 2000 of collector discharge chamber 1086 of adjacent heat exchanger arrangements 1000 are joined, so that the collector discharge chamber communicates fluidly with each heat exchanger arrangement. heat 1000 from module 524. Flange connectors 2000 from adjacent heat exchanger arrangements 1000 are joined using clamp 2020. In the illustrated configuration, 12 heat heat exchanger 1000 are connected, using a common collector, and provide the heat exchanger module 524. It should be understood, however, that a greater or lesser number of heat exchanger arrangements 1000 can be used to form module 524 and the number employed depends on the requirements of the specific application.
[000191] Referring to Figures 10 and 33, the heat exchanger arrangements 1000 connected by a common collector 1080 are supported on support 1002. The heat exchanger arrangements 1000 connected collectors 1080 and support 1002 together form a stage of heat exchanger. In an illustrated configuration, the 520 multistage heat exchange system is a four-stage module heat exchanger that allows use of a hybrid cascade OTEC cycle and thus includes four heat exchanger modules 521, 522, 523, 524 (only the second and fourth stages being shown in Figure 330. Each module is received and supported on the support frame 540 when mounted on the heat exchange system 520. In some configurations, the support 1002 of each heat exchange module is provided with rails ( (not shown) that engage the respective rails 2080 included in the support frame 540 to facilitate assembly of heat exchanger modules 521, 522, 523, 524 in the heat exchange system 520. For example, mounted on rails with continuous plastic contact surfaces , bracket 1002 allows linear extraction to remove and maintain individual arrangements 1000. In addition, during arrangement maintenance, a temporary head connector can replace an arrangement 1000 and m a 524 module until arrangement 1000 is replaced, allowing continuous heat transfer operation with the heat exchanger, providing only a partial reduction in energy transfer.
[000192] In the illustrated configuration, the evaporator portion 344 of the column 310 includes a central pillar 550 and a support frame 540 supported on each of opposite sides 552 and 554 of the pillar 550. A similar arrangement is provided within the condenser portion 320 .
[000193] The flange connector 2000 described welded to the collector 1080 includes a stepped portion 2014 inside the collector chamber provides alignment and improves the strength of the welded joint. However, the 2000 flange connector is not limited to being fixed to the collector by welding. For example, the flange connector 200 flow path fixed to the collector 1080 per m, of adhesive. Referring to Figures 34A and 34B in some configurations, using adhesive, the second end of connector 2010 can be modified, so that the bonding surface has a larger area. In particular, the modified flange connector 2000 'may include a second end of connector 2010' having a lip 2018 'that extends radially outward and provides a large surface area for bonding.
[000194] Referring to Figure 35, an inlet flange connector 2000 '' is connected to a collector feed chamber 1084 of a condenser, and an outlet flange connector 2000 '' is connected to the corresponding discharge chamber collector connector 1086. The 2000 ”inlet flange connector has a smaller diameter than the 2000” outlet flange connector, but similar in the rest it is similar. For this reason, only the 2000 '' inlet flange connector will be described. The inlet flange connector 2000 '' similar to the previously described flange connector 2000 illustrated in Figure 15B includes the first staggered portion 2014, which has the outside diameter dimensioned to correspond to the internal diameter of the corresponding collector feed chamber 1084 or discharge chamber of collector 1086. In addition, the inlet flange connector 2000 '' includes a second staggered portion 2015 disposed adjacent the end face 2012 of the second end of connector 2010, so that the end face 2012 defines a step between the first stepped portion 2014 and the second stepped portion 2015. The second stepped portion 2015 has an outside diameter smaller than that of the first end of the 2002 connector and greater than that of the first stepped portion 2014. During the fabrication of the arrangement, the first stepped portion 2014 is inserted and welded opening the entry (or exit) of the flap. During this procedure the second staggered portion 1015 serves to balance the heat dissipation between the tab 1070 of the heat exchanger plate 1022 and the inlet flange connector 2000 ''.
[000195] Referring to Figures 36 to 38, an alternative heat exchange plate 3022 that is configured for use in evaporators is similar to the heat exchange plate 1022, described above with reference to Figure 14. With a view to similarity, Equal components receive the same reference numbers. The heat exchange plate 3022 includes a working fluid passage 3055 including several parallel mini-channels 1912 having an alternating coil design. To accommodate changes in the working fluid (for example, changes from the liquid to the vapor condition), the number of parallel flow passages per pass is increased along the flow path of the working fluid from the inlet to the outlet of the passage. For example, the heat exchanger plate 3022 in Figure 46 has four inlet passages 1911, each feeding the corresponding minichannels 1912 adjacent to bottom edge 1046. Minichannels 1912 extend along the plate in a serpentine manner, from bottom edge 1046 to top edge 1045. Here, "top" and "bottom" refer to the orientation of the heat exchanger plate in the normal operating position. In Figure 38, the evaporator heat exchanger plate 302 is illustrated in its operating position, with the top edge 1045 overlapping the bottom edge 1046. The flow of four mini-channels feeds six mini-channels at a first 3914 transition point. The flow of six mini-channels feeds eight mini-channels at a second 3916 transition point. The flow of eight mini-channels feeds ten mini-channels at a third 3920 transition point, and the flow of ten mini-channels feeds twelve mini-channels at a fourth 3922 transition point. the resulting twelve mini-channels discharge through the 1918 fluid outlets.
[000196] The four inlet passages 1911 are supplied with working fluid 580 in liquid condition by the collector feed chamber 1084 via flap inlet pass 1072, and the twelve outlet passages 1918 discharge working fluid in the vapor condition. collector discharge chamber 1086 via flap outlet passages 1074.
[000197] Although the collector feed chamber 1084 and the collector flaps 1086 are structurally similar, the collector feed chamber 1084 is different in size from the corresponding collector discharge chamber 1086. For example, the heat exchanger plate 3022 configured for use as a heat exchanger as part of arrangement 1000 on the evaporator (Figures 36 to 38), the collector feed chamber 1084 is smaller than the corresponding collector discharge chamber 1086. This is achieved by forming the flap entry openings 1076 with a smaller diameter than the 1078 flap outlet openings. This size difference reflects the fact that the working fluid 580 enters the evaporator in the liquid condition at the inlet, thus requiring a lower overall flow volume than the same fluid when leaves the evaporator in the gas condition at the outlet. Therefore, for a 4022 heat exchanger plate configured for use as part of arrangement 1000 in a condenser (Figures 39-41) the collector feed chamber 1084 is larger than the corresponding collector discharge chamber 1086.
[000198] Referring to Figures 39 to 41, a 4022 heat exchanger plate configured for use in a condenser is similar to the 3022 evaporator heat exchanger plate described above with respect to Figures 36 to 38. In view of the similarity, Equal components receive the same reference numbers. The heat exchanger plate 4022 includes a working fluid passage 4055 including several parallel mini-channels 1912 having an alternating coil design. The number of 1911 working fluid inlet passages aligned with a geometric axis parallel to the direction of the non-working fluid flow is greater on the condenser heat exchanger plate 4022 than on the evaporator heat exchanger plate 3022 to accommodate a volume relatively greater fluid at the entrance of a condenser (for example, gas) than at the entrance of an evaporator (for example, liquid). To accommodate these phase changes in the working fluid (for example, changes from gas to liquid), the number of parallel flow passages per passage is decreased along the flow path of the working fluid from the passage inlet to the outlet of the ticket. For example, the heat exchange plate 4022 in Figure 39 has eight inlet passages 1911, each of which feeds twelve corresponding mini-channels 1012 adjacent to the top edge 1045. Mini-channels 1912 extend along the plate, in a serpentine manner, from the top edge 1045 to the bottom edge 1046. In Figure 41, the condenser heat exchanger plate 4022 is shown face down in relation to its operating position with the bottom edge 1046 overlapping the top edge 1045. The flow of twelve mini-channels feeds ten mini-channels at a first transition point 4914. The flow of ten mini-channels feeds eight mini-channels at a second transition point 4916. The flow of eight mini-channels feeds six mini-channels at a third transition point 4920, and the flow of six mini-channels feeds four mini-channels at a fourth 4922 transition point. The resulting four mini-channels discharge through 1918 fluid outlets.
[000199] The eight 1911 inlet passages are supplied with working fluid 580 in steam condition by the collector feed chamber 1084 via the 1072 flap inlet pass, and the four 1918 outlet passages discharge the working fluid in liquid condition in the collector discharge chamber 1086 via the flap outlet passage 1074.
[000200] On both plates - condenser heat exchanger plate 4022 and evaporator heat exchanger plate 3022 - the mini-channels 1912 extend along the plate, in a serpentine manner, from the top edge 1045 to the edge of bottom 1046. Minichannels 1912 include linear regions 1912a, curved regions 1912b and distributive channels 1912c. The curved regions 1912a extend in parallel to the top edge 1045. The curved regions 1912 connect adjacent linear regions 1912a and are adjacent to the right edge of plate 1047 or the left edge of plate 1048. Distributive channels 1912c are channels that branch off from one another. a mini-channel in the corresponding curved region 1912. The distribution channels 1912c make fluid communication with the corresponding curved region 1912c via the inlet fluid distribution 1912d that opens towards the collector end of the heat exchanger plate 3022, 4022. In particular, each distribution channel 1912c communicates with the mini channel 1912 in a single location (for example, fluid distribution port 1912d) and each distribution channel 1912 is arranged in a generally triangular region, defined by adjacent curved regions 1912b and corresponding plate edge 1047 or 1048 Each 1912c distributive channel is branched to provide mini distributional channels, which are configured to substantially fill the generally triangular region. It should be noted that the distributive channels are placed in areas of heat exchanger plates 3022, 4022 that, in other configurations, were not covered by fluid work flow passages, for example, in the spaces between 1912 serpentine mini-channels and edges of plate 1045, 1046, 1047, 1048. By placing the distributive channels in these areas, a larger surface area of the heat exchanger is provided for the working fluid. In addition, by placing the distribution channels in these areas, substantially the entire front surface is covered by the 1912 minichannels, thereby preventing the association of unused areas of work fluid, and losses are reduced.
[000201] The condenser heat exchanger plate 4022 and evaporator heat exchanger plate 3022 are each provided with a cutout 3066, 4066 formed on the right edge of the plate 1047. The cutout 3066, 4066 opens at the different edge of the plate 10437 in a location joining the flap 1070 and is generally V-shaped when viewed facing the front face 1040. During the fabrication of the arrangement, vessel 2050 is received within cut 3066 4066. With the provision of cut 3066, 4066 during the potting step of manufacturing the heat exchanger arrangement 1000, vessel 2050 can wrap a larger portion of each flap 1070, allowing the epoxy to be placed around a larger portion of each flap 1070 than an arrangement in which the 1022 plates are formed without V-cutouts.
[000202] As previously discussed, plate 1022 includes multiple zones, where each zone corresponds to a region in which the 1912 minichannels are allowed to expand to a particular height. The condenser heat exchanger plate 3022 and condenser heat exchanger plate 4022 are provided with three zones. For example, referring to Figures 38 and 42 to 46, the evaporator heat exchanger plate 3022 includes a first zone Z1 arranged on tab 1070 (for example, collector region see Figures 38, 42, 45 and 46), a second zone Z2 that extends along the first edge 1047 between the tab 1070 and the bottom edge (for example, entry passage region seen in perspective Figures 38, 43 and 46), and a third zone Z3 that extends between the first and second zones Z11 and Z21 and the second edge 1048 (for example, active area, see Figures 38, 44 and 46). Of the three zones, the 1912 minichannels in the first zone Z11 have the highest height. The 1912 minichannels in the second Z2 have a lower height than the minichannels in the first Z2 zone, and greater than the 1912 minichannels in the third Z3 zone.
[000203] The 4022 condenser heat exchanger plate also includes three zones. Referring to Figures 41 to 46, as the evaporator heat exchanger plate 3022, the condenser heat exchanger plate includes a first zone Z1 arranged on tab 1070, (for example, collector region, see Figures 41, 42, 45) and second zone Z2 that extends along the first edge 1047 between the flap 1070 and the bottom edge 1046 (for example, the entrance passage region, see Figures 41 and 43) and a third zone Z3, which extends between the first and second zones Z1 and Z2, and the second edge 1048 (for example, active area, see Figures 41 and 44). Of the three zones, the 1912 minichannels in the first zone Z1 have the highest height. The 1912 minichannels in the second Z2 zone have a height that is less than that of the minichannels in the first Z2 zone and greater than the height of the 1912 minichannels in the third Z3 zone.
[000204] For example, in some configurations, the height of the 1912 mini-channels in the first Z1 zone is about 5 mm, the height of the 1912 mini-channels in the second Z21 zone is about 3 mm, and the height of the 1912 mini-channels in the third zone is about 2 mm. When in an array 1000, the mini-channels of the first Z11 zone of a plate 3022, 4022 top the adjacent plate, so that substantially no space 1025 is formed between adjacent plates in the first zone Z1. Within the second zone Z2, a space 1025 of about 2 mm is provided between adjacent plates while a space 1025 of about 4 mm is provided between adjacent plates in the third zone Z3. The height of zones Z1, Z2, Z3, and the arrangement of zones Z1, Z2, Z3, is configured to help maintain the flow of non-working fluid in the active area of the heat exchanger plate. The active area is the area of the plate in which substantially most of the heat transfer occurs between the working fluid and the non-working fluid and generally corresponds to the location of serpentine flow channels and distributional channels. Thus, as in Figure 46, the active area of the heat exchanger plate is generally located in the third zone Z3. Because the third zone is formed of mini-channels having a small height in relation to the height in the first and second zones Z1 and Z2, a relatively large space 1025 results between adjacent plates, when stacked providing less resistance to flow in this area, and, therefore, the working fluid tends to flow through this area.
[000205] Referring to Figures 47-49, in some respects, an arrangement 1000 of heat exchanger plates 1022, 3022, 4022, can be surrounded by a generally tubular housing (e.g., cocoon) 5000 that surrounds the arrangement 1000. The cocoon 5000 includes a side wall 5002, a first open end 5004, and a second open end 5006, opposite the first open end 5004. The first open end 5004 defines an inlet of the cocoon 5000, which allows non work is directed to the spaces 1025 between adjacent plates 1022, 3022, 4022 of the arrangement 1000. The second open end 5004 defines an end of the cocoon 5000, which allows the non-working fluid to escape from the space 1025, after passing over the plate front and rear surfaces 1040 and 1042. The side wall 1080 also includes an opening 5008 configured to receive the collector, so that the collector 1080 extends through the opening 5008 when the arrangement is wrapped gone through the 5000 cocoon.
[000206] The side wall of the cocoon 5002 is a set formed of a first side wall member 5012 and second side wall member 5014. Each side wall member 5012 and 5014 is L-shaped when viewed in cross section, where the first side wall member 5012 is identical to the second side wall member 5014. In particular, the first side wall member 5014 includes a first side 5012a and a second side 5012b at one end of the first side 5012a and extending perpendicular to the first side 5012a . Similarly, the second side wall member 5014a includes a first side 5014a and a second side 5014b at one end of the first side 5014a, and extending perpendicular to the first side 5014a. In the assembled state, the first side wall side 5012 cooperates with the second side wall member 5014 to form a tube having a rectangular cross section and including sides 5012a, 5012b, 5014a, 5014b. The heat exchanger plates 1022, 3022, 4022 are supported in the grooves 5010 formed on the inner surface of opposite sides 5012a, 5014a of the cocoon side wall 5002. The grooves 5010 are parallel and equally spaced in a direction parallel to the alignment axis 1005. The slot spacing corresponds to the desired distance between plates 1022, 3022, 4022. Each slot 5010 is configured to receive and support a heat exchanger plate. Once the first and second side wall members 5012 and 5014 are L-shaped and identical, the assembly of the cocoon is simplified, and ensures alignment of the grooves 5010 on the opposite sides 5012a and 5014a of the cocoon.
[000207] Referring to Figure 49, in some respects, the guard includes a 5030 handle arranged on the outer surface of the 5012a side. The handle 5030 can be selectively attached and detached from the side 5012a and used to facilitate the handling of the arrangement 1000, particularly during installation in a heat exchanger module 524.
[000208] The cocoon 5000 provides several advantages. For example, the 5000 cocoon is configured to space 1022, 3022, 4022 heat exchanger plates and help keep them in a parallel spaced relationship during assembly and operation. For example, the cocoon 5000 keeps the heat exchanger plates in a parallel stacked arrangement having the desired plate spacing, through which the template and / or alignment mandrels described above with respect to step 3003 of the fabrication arrangement method heat exchanger 1000 may not be required, simplifying the manufacturing process. Cocoon 5000 protects heat exchanger plates 1022, 3022 4022 from damage to external structures during shipment and during assembly with other arrangements in heat exchanger modules 524. In use, cocoon 5000 directs the non-working fluid 1000, and maintains the flow of non-working fluid within the array and over the active area.
[000209] In addition, although heat exchange devices and systems have been described with respect to OTEC plant evaporators / condensers, heat exchange devices and systems are not limited to such applications. For example, the heat exchange devices and systems described in this would also be useful for other applications that require a high efficiency heat exchange, such as steam discharge condensers, and other devices for using waste heat, and cooling systems. liability of nuclear power plants.
[000210] Illustrative configurations selected from the heat exchanger device and respective manufacturing method have been described above in some detail. It should be understood that only structures considered necessary to clarify the configuration were described in this one. Other conventional structures and auxiliary components and accessories of the system are presumably known and understood by those skilled in the art. Furthermore, while a working example of the device and method has been described, the device and method are not limited to the described working example, and many modifications and changes may come to be imagined, and introduced or added to the present invention by those skilled in the art. technical.

权利要求:
Claims (15)
[0001]
1. Heat exchange plate (1022), characterized by the fact that it comprises: a front face (1040), which defines a first heat exchange surface, a rear face (1042) on one side of the heat exchanger plate opposite the front face, the rear face defining a second heat exchange surface; a peripheral edge (1044); a collector region (1070) extending outwardly from the peripheral edge; an internal fluid passage (1055) disposed between the front face and the rear face, the surface of the internal fluid passage defining a third heat exchange surface, the internal fluid passage comprising: a fluid inlet (1076, 1078) having an entrance area; a fluid outlet (1076, 1078) having a different outlet area than the inlet area; and parallel fluid channels, each fluid channel of the parallel fluid channels configured to direct the fluid in parallel from the inlet to the outlet, the parallel fluid channels including at least one transition point (1914, 1916, 1920, 1922, 1924 ) between the fluid inlet and the fluid outlet, where the number of fluid channels changes; where the fluid inlet and fluid outlet are arranged in the collector region, and each inlet and outlet opens in a plane parallel to the front face.
[0002]
2. Heat exchange plate, according to claim 1, characterized by the fact that: one of a) and b), in which a) the entrance area is smaller than the exit area, and the number of channels fluid increases by at least one transition point and b) the inlet area is larger than the outlet area, and the number of fluid channels decreases by at least one transition point; and the parallel fluid channels comprise at least four transition points.
[0003]
3. Heat exchange plate according to claim 1, characterized by the fact that the heat exchanger plate comprises: a first edge, a second edge spaced and extending in parallel to the first edge, a third edge extending between the first edge and the second edge, and a fourth edge spaced and extending parallel to the third edge, the fourth edge extending between the first edge and the second edge, in which the parallel fluid channels extend along a serpentine path between the first edge and the second edge and include linear regions extending in parallel from the first edge, curved regions that connect adjacent linear regions, the curved regions arranged adjacent to a third or fourth edge, and a distributive channel in communication fluid with a curved region, the distributional channel arranged between adjacent curved regions, for example, the distributional channel is configured to fill substantially and a generally triangular region, defined between a curved region, an adjacent curved region and the corresponding third or fourth edge.
[0004]
4. Heat exchange plate according to claim 1, characterized by the fact that the heat exchange plate comprises a first edge, a second edge spaced and extending in parallel to the first edge; wherein parallel fluid channels extending along a serpentine path between the first edge and second edge including linear regions extending in parallel with the first edge and curved regions connecting adjacent linear regions, at least one curved region including one distributional channel disposed between adjacent curved regions, for example, where the distributional channel has a distributary fluid inlet that is in fluid communication with a corresponding curved region.
[0005]
5. Heat exchange plate according to claim 4, characterized by the fact that the plurality of curved regions includes a distribution channel (1912c) and each distribution channel communicates with an internal fluid passage in a single location, and it is branched to provide distributional mini-channels (1912) and optionally in which the entrance of the distributional channel opens towards the first end.
[0006]
6. Heat exchange plate according to claim 1, characterized by the fact that the peripheral edge comprises at least one linear lateral edge (1047), and a cut-out region (3066, 4066) that opens along the edge linear lateral, where the collector region extends out of at least one linear lateral border in a normal direction to the linear lateral border, and the indented region is adjacent to the collector region.
[0007]
7. Heat exchange plate according to claim 1, characterized in that the peripheral edge comprises a first edge (1046), a second edge (1045) spaced and extending in parallel to the first edge, a third edge (1047) extending between the first edge and the second edge, and a fourth edge (1048) spaced and extending in parallel from the third edge, the fourth edge extending between the first edge and the second edge, where the region of the collector (1070) extends outwardly from the third edge (1047) and includes a side portion aligned with the first edge (1046), and a cutout region (3066, 4066) is formed on the third edge that extends inwardly from the third edge, the cut region joined to the collector region, for example, where the cut region is generally triangular when viewed facing the front face.
[0008]
8. Heat exchange plate, according to claim 1, characterized by the fact that: the front face comprises regions extending outwards that correspond to the location of the internal fluid passage, the regions extending outwards extend in a given location in an extension that is defined by the height of the internal fluid passage in this given location, where the height refers to a dimension in the normal direction to the front face, the regions that extend outwards including a first zone that corresponds to a first height of internal fluid passage, a second zone corresponding to a second height of internal fluid passage, where the first height of internal fluid passage is greater than the second height of internal fluid passage, in which the first zone is arranged in the collector region and the second zone is arranged outside the collector region.
[0009]
Heat exchange plate according to claim 8, characterized by the fact that it additionally comprises a peripheral edge bordering the front and back faces, in which the peripheral edge includes a first edge, a second edge, spaced and extending in parallel from the first edge, and a third edge extending between the first edge and second edge, a fourth spaced edge and extending in parallel from the third edge, the fourth edge extending between the first edge and second edge, where a collector region extends outward from the third edge, the first zone is arranged in the collector region, and the second zone extends along the third edge, between the collector region and the second edge.
[0010]
10. Heat exchange plate according to claim 8 or 9, characterized by the fact that it additionally comprises a third zone corresponding to a third height of internal fluid passage, where the second height of internal fluid passage is greater that the third height of internal passage of fluid, and the third zone extends between the first and second zones and the fourth edge.
[0011]
11. Heat exchange plate, according to claim 1, characterized by the fact that it additionally comprises a flange connector (2000) fixed to a collector (1080), in which the flange connector (2000) is for connecting the collectors of adjacent heat exchanger arrangements (1000) and allow fluid communication between them.
[0012]
Heat exchange plate according to claim 11, characterized in that the flange connector is a collector connector comprising: a tubular body including a first end, the first end including an annular groove and a member sealer arranged in the groove; a second end opposite the first end, the second end configured to be attached to a collector; a fluid passage extending between the first end and the second end; and an outer diameter that varies from the first end to the second end and where optionally one from a) and b), where: a) where the tubular body is in frusto-conical shape, and the first end has an outer diameter greater than of the second end, and b) where the second end comprises a stepped portion, through which the outer diameter of the second end is smaller than that of the first end.
[0013]
13. Heat exchanger, characterized by the fact that it comprises two or more heat exchanger plates, as defined in claim 1, in which the heat exchanger plates are in a stacked arrangement, so that each plate of exchanger of heat is spaced from the adjacent heat exchanger plate, the space between adjacent heat exchanger plates defining an external fluid passage, each external fluid passage configured to receive a first fluid (570), in which a collector (1080) it has fluid communication with the entrance of each heat exchanger plate, and a housing (1088) that involves the stacked plate arrangement, the housing configured to support heat exchanger plates in a spaced relationship, in which the housing comprises a opening configured to receive the collector, and the collector extends through the opening.
[0014]
Heat exchanger according to claim 13, characterized in that the housing comprises a side wall, a first open end, and a second open end, opposite the first end, the first open end defining the entrance of the first fluid to the respective external passage and the second open end defining the output of the respective first fluid from the external passage.
[0015]
15. Heat exchanger according to claim 13, characterized by the fact that the housing comprises four sides, arranged to form a rectangle when viewed from its cross section, and an internal surface of a pair of opposite sides of the housing is formed having parallel grooves, and each groove configured to receive and support a heat exchanger plate, for example, wherein the housing is a set of a first sidewall member and second sidewall member, each sidewall member having a L shape in the cross section, where the first side wall member is identical to the second side wall member.

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引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

---

US2038172A|1935-09-14|1936-04-21|Christopher J Haley|Wooden pipe joint|

---

US2156544A|1936-10-16|1939-05-02|Raskin Walter|Embossed tube evaporator plate for refrigerating systems|

---

US2263182A|1940-01-30|1941-11-18|Macpherson Harold Nolan|Wood stave pipe|

---

US2619811A|1950-05-02|1952-12-02|Nash Kelvinator Corp|Refrigerant evaporator|

---

US2648217A|1950-07-13|1953-08-11|Glenn V Gladville|Silo construction|

---

US2827774A|1955-03-10|1958-03-25|Avco Mfg Corp|Integral evaporator and accumulator and method of operating the same|

---

US2900175A|1958-03-28|1959-08-18|Tranter Mfg Inc|Plate heat exchange unit|

---

US3095014A|1958-07-02|1963-06-25|Conch Int Methane Ltd|Stave secured sectional insulated conduit|

---

US3334399A|1962-12-31|1967-08-08|Stewart Warner Corp|Brazed laminated construction and method of fabrication thereof|

---

US3368614A|1963-06-24|1968-02-13|Olin Mathieson|Heat exchanger|

---

US3246689A|1963-12-23|1966-04-19|Johns Manville|Heating or cooling wall panels|

---

US3312056A|1964-03-09|1967-04-04|Lagelbauer Ernest|Super temperature dual flow turbine system|

---

US3502141A|1965-12-23|1970-03-24|Nasa|Method of improving heat transfer characteristics in a nucleate boiling process|

---

US3524476A|1967-09-28|1970-08-18|Us Navy|Pipe wall shear damping treatment|

---

US3538955A|1967-10-16|1970-11-10|James H Anderson|Suspended submarine pipe construction|

---

US3558439A|1967-12-28|1971-01-26|James H Anderson|Water desalting process and apparatus|

---

US3599589A|1967-12-29|1971-08-17|Mc Donnell Douglas Corp|Earthquake-resistant nuclear reactor station|

---

GB1277872A|1968-06-06|1972-06-14|Delaney Gallay Ltd|Improvements in and relating to heat exchangers|

---

US3837308A|1971-05-24|1974-09-24|Sanders Associates Inc|Floating power plant|

---

US3805515A|1971-06-11|1974-04-23|Univ Carnegie Mellon|Modularized sea power electrical generator plant|

---

US3795103A|1971-09-30|1974-03-05|J Anderson|Dual fluid cycle|

---

US4036286A|1972-11-02|1977-07-19|Mcdonnell Douglas Corporation|Permafrost stabilizing heat pipe assembly|

---

US4002200A|1972-12-07|1977-01-11|Dean Products, Inc.|Extended fin heat exchanger panel|

---

DE2518683C3|1975-04-26|1981-04-09|4P Verpackungen Gmbh, 8960 Kempten|Heat exchanger made from two aluminum sheets connected to one another|

---

US4235287A|1975-05-02|1980-11-25|Olin Corporation|Heat exchange panel|

---

US4006619A|1975-08-07|1977-02-08|James Hilbert Anderson|Tube expander utilizing hydraulically actuated pistons|

---

US4265301A|1976-04-06|1981-05-05|Anderson James H|Heat exchanger support construction|

---

US4014279A|1976-04-28|1977-03-29|Trw Inc.|Dynamic positioning system for a vessel containing an ocean thermal energy conversion system|

---

US4048943A|1976-05-27|1977-09-20|Exxon Production Research Company|Arctic caisson|

---

US4030301A|1976-06-24|1977-06-21|Sea Solar Power, Inc.|Pump starting system for sea thermal power plant|

---

US4179781A|1976-07-26|1979-12-25|Karen L. Beckmann|Method for forming a heat exchanger core|

---

US4131159A|1976-07-26|1978-12-26|Karen L. Beckmann|Heat exchanger|

---

US4062189A|1976-09-29|1977-12-13|Pacific Power And Protein, Inc.|Method of preventing the accumulation of micro-organisms in thermal energy conversion systems|

---

US4055145A|1976-09-29|1977-10-25|David Mager|System and method of ocean thermal energy conversion and mariculture|

---

US4087975A|1977-03-29|1978-05-09|The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration|Ocean thermal plant|

---

US4209061A|1977-06-02|1980-06-24|Energy Dynamics, Inc.|Heat exchanger|

---

US4139054A|1977-10-28|1979-02-13|Sea Solar Power|Plate-fin heat exchanger|

---

US4358225A|1978-05-02|1982-11-09|Hollandsche Beton Groep N.V.|Deep ocean conduit|

---

US4753554A|1978-07-28|1988-06-28|Westinghouse Electric Corp.|Submerged flexible piping system with neutral buoyancy|

---

US4210820A|1978-08-17|1980-07-01|The United States Of America As Represented By The United States Department Of Energy|Open cycle ocean thermal energy conversion system structure|

---

US4210819A|1978-08-17|1980-07-01|The United States Of America As Represented By The United States Department Of Energy|Open cycle ocean thermal energy conversion steam control and bypass system|

---

US4231312A|1978-08-21|1980-11-04|Global Marine, Inc.|Flexible ocean upwelling pipe|

---

US4281614A|1978-08-21|1981-08-04|Global Marine, Inc.|Connection of the upper end of an ocean upwelling pipe to a floating structure|

---

US4234269A|1978-08-21|1980-11-18|Global Marine, Inc.|Deployment, release and recovery of ocean riser pipes|

---

US4201263A|1978-09-19|1980-05-06|Anderson James H|Refrigerant evaporator|

---

US4209991A|1978-09-19|1980-07-01|Sea Solar Power|Dynamic positioning of sea thermal power plants by jet propulsion|

---

US4229868A|1978-10-26|1980-10-28|The Garrett Corporation|Apparatus for reinforcement of thin plate, high pressure fluid heat exchangers|

---

US4231420A|1978-11-20|1980-11-04|Sea Solar Power|Heat exchanger with controls therefor|

---

US4350014A|1978-11-30|1982-09-21|Societe Anonyme Dite: Sea Tank Co.|Platform for utilization of the thermal energy of the sea|

---

US4290631A|1979-04-06|1981-09-22|Sea Solar Power|Submarine pipe construction|

---

US4282834A|1979-07-19|1981-08-11|Sea Solar Power|Boiler structure embodying a plurality of heat exchange units|

---

US4254626A|1979-08-14|1981-03-10|Sea Solar Power|Deaerating system for sea thermal power plants|

---

US4749032A|1979-10-01|1988-06-07|Rockwell International Corporation|Internally manifolded unibody plate for a plate/fin-type heat exchanger|

---

NL173670C|1979-10-30|1984-02-16|Hollandsche Betongroep Nv|FLOATING INSTALLATION WITH A PIPE SUSPENDED TO THE RESTRICTION.|

---

US4301375A|1980-01-02|1981-11-17|Sea Solar Power, Inc.|Turbo-generator unit and system|

---

US4384459A|1980-10-14|1983-05-24|Johnston Harold W|Ocean energy and mining system|

---

US4334965A|1980-12-31|1982-06-15|Standard Oil Company|Process for recovery of olefinic nitriles|

---

JPS6354882B2|1981-03-20|1988-10-31|Tokyo Shibaura Electric Co|

---

US4731072A|1981-05-11|1988-03-15|Mcneilab, Inc.|Apparatus for heating or cooling fluids|

---

JPS6235596B2|1981-06-17|1987-08-03|Mitsubishi Electric Corp|

---

NZ201673A|1981-09-11|1986-07-11|R J Pollard|Flat plate heat exchanger core with diversion elements to allow several fluid passes through core|

---

US4434112A|1981-10-06|1984-02-28|Frick Company|Heat transfer surface with increased liquid to air evaporative heat exchange|

---

JPS59130963A|1983-01-13|1984-07-27|Fujifuki Kimiyoshi|Iron wire fixing tool|

---

JPS59130963U|1983-02-18|1984-09-03|

---

US4497342A|1983-06-20|1985-02-05|Lockheed Missiles & Space Company, Inc.|Flexible retractable cold water pipe for an ocean thermal energy conversion system|

---

JPS6028681A|1983-07-27|1985-02-13|Fuji Xerox Co Ltd|Detector of abnormal temperature rise|

---

JPS6028681U|1983-08-03|1985-02-26|

---

JPH021989B2|1984-04-17|1990-01-16|Saga Daigakucho|

---

US4700543A|1984-07-16|1987-10-20|Ormat Turbines Ltd.|Cascaded power plant using low and medium temperature source fluid|

---

US4578953A|1984-07-16|1986-04-01|Ormat Systems Inc.|Cascaded power plant using low and medium temperature source fluid|

---

JPS6149995A|1984-08-20|1986-03-12|Showa Alum Corp|Lamination type heat exchanger|

---

US4548043A|1984-10-26|1985-10-22|Kalina Alexander Ifaevich|Method of generating energy|

---

US4893673A|1984-10-31|1990-01-16|Rockwell International Corporation|Entry port inserts for internally manifolded stacked, finned-plate heat exchanger|

---

US4603553A|1984-12-11|1986-08-05|R & D Associates|Ballistic cold water pipe|

---

JPS61149507A|1984-12-24|1986-07-08|Hisaka Works Ltd|Heat recovery device|

---

CN1003317B|1985-08-31|1989-02-15|奥马蒂系统公司|Cascaded power plant using low and medium temp. source fluid|

---

DE3543893C2|1985-12-12|1988-01-28|Mtu Muenchen Gmbh|

---

US5057217A|1987-06-25|1991-10-15|W. L. Gore & Associates, Inc.|Integral supported filter medium assembly|

---

GB8719473D0|1987-08-18|1987-09-23|Cesaroni A J|Headers for heat exchangers|

---

WO1990001659A1|1988-08-15|1990-02-22|Siddons Ramset Limited|Evaporator plate|

---

US5104263A|1988-10-05|1992-04-14|Sekisui Kagaku Kogyo Kabushiki Kaisha|Underground pipe for a thrust boring method and a connecting construction of the underground pipe for the same|

---

GB8905432D0|1989-03-09|1989-04-19|Gen Electric Co Plc|A heat exchanger|

---

JP2680674B2|1989-04-12|1997-11-19|財団法人電力中央研究所|Ocean / waste heat temperature difference power generation system|

---

EP0420993B1|1989-04-13|1995-02-15|Mitsubishi Cable Industries, Ltd.|Catheter|

---

US5101890A|1989-04-24|1992-04-07|Sanden Corporation|Heat exchanger|

---

JPH02287094A|1989-04-26|1990-11-27|Zexel Corp|Heat exchanger|

---

JPH0446289A|1990-06-11|1992-02-17|Hitachi Ltd|Mounting method for pipe flange for refrigerating device|

---

US5074280A|1991-03-13|1991-12-24|Lennox Industries Inc.|Sectional high efficiency heat exchanger|

---

US5123772A|1991-04-15|1992-06-23|Coupling Corporation Of America|Threaded assembly with locking capability|

---

JPH0726789B2|1992-04-09|1995-03-29|工業技術院長|Condensing device and method for open-cycle ocean thermal energy conversion|

---

US5217788A|1992-05-11|1993-06-08|Brentwood Industries|Corrugated sheet assembly|

---

JPH05340342A|1992-06-08|1993-12-21|Toshiba Corp|Ocean thermal energy conversion device|

---

KR0143540B1|1992-08-27|1998-08-01|코오노 미찌아끼|Stacked heat exchanger and method of manufacturing the same|

---

US5359989A|1993-03-04|1994-11-01|Evcon Industries, Inc.|Furnace with heat exchanger|

---

JPH0798193A|1993-09-30|1995-04-11|Hisaka Works Ltd|Plate type heat exchanger|

---

US5513494A|1993-12-14|1996-05-07|Otec Developments|Ocean thermal energy conversion system|

---

US5582691A|1993-12-14|1996-12-10|Flynn; Robert J.|Ocean thermal energy conversion system|

---

US5555838A|1994-10-31|1996-09-17|Seatek International, Inc.|Ocean thermal energy conversion platform|

---

GB9426208D0|1994-12-23|1995-02-22|British Tech Group Usa|Plate heat exchanger|

---

US5656345A|1995-06-07|1997-08-12|Illinois Tool Works, Inc.|Adhesive compositions and adhesively joined pipe segments|

---

US5769155A|1996-06-28|1998-06-23|University Of Maryland|Electrohydrodynamic enhancement of heat transfer|

---

FR2754595B1|1996-10-11|1999-01-08|Ziemann Secathen|HEAT EXCHANGER, AND HEAT EXCHANGE BEAM, AND RELATED WELDING AND PROCESSES|

---

JPH10137877A|1996-11-05|1998-05-26|Zexel Corp|Manufacture of tube heat exchanger|

---

US5983624A|1997-04-21|1999-11-16|Anderson; J. Hilbert|Power plant having a U-shaped combustion chamber with first and second reflecting surfaces|

---

NO984239L|1997-09-16|1999-03-17|Deep Oil Technology Inc|Procedure for mounting a floating offshore structure|

---

CA2268999C|1998-04-20|2002-11-19|Air Products And Chemicals, Inc.|Optimum fin designs for downflow reboilers|

---

FR2779754B1|1998-06-12|2000-08-25|Technip Geoproduction|DEVICE FOR TRANSPORTING AND LAYING A BRIDGE OF AN OIL PLATFORM FOR EXPLOITATION AT SEA|

---

FR2782341B1|1998-08-11|2000-11-03|Technip Geoproduction|INSTALLATION FOR OPERATING A DEPOSIT AT SEA AND METHOD FOR ESTABLISHING A COLUMN|

---

US6472614B1|2000-01-07|2002-10-29|Coflexip|Dynamic umbilicals with internal steel rods|

---

SE516416C2|2000-05-19|2002-01-15|Alfa Laval Ab|Plate package, heat transfer plate, plate heat exchanger and use of heat transfer plate|

---

BR0113395A|2000-08-21|2005-12-20|Coflexip|Buoyancy system for a buoyancy structure and application, lifting duct, methods of designing a buoyancy system, increasing the redundancy of a buoyancy and applying buoyancy to a component and a lifting duct and apparatus to provide buoyancy to a lifting duct|

---

FR2821144B1|2001-02-22|2003-10-31|Coflexip|FLEXIBLE DUCT WITH ANTI-THRUST FILM|

---

JP4134520B2|2001-03-14|2008-08-20|株式会社デンソー|Heat exchanger|

---

US6948884B2|2001-03-14|2005-09-27|Technip France|Vortex-induced vibration reduction device for fluid immersed cylinders|

---

US7258510B2|2001-03-29|2007-08-21|Masasuke Kawasaki|Systems and methods useful in stabilizing platforms and vessels having platforms and legs|

---

JP4732609B2|2001-04-11|2011-07-27|株式会社ティラド|Heat exchanger core|

---

US6451204B1|2001-04-12|2002-09-17|Sea Solar Power, Inc.|Ocean power plant inlet screen|

---

WO2003060368A1|2001-12-29|2003-07-24|Technip France|Heated windable rigid duct for transporting fluids, particularly hydrocarbons|

---

US20030140838A1|2002-01-29|2003-07-31|Horton Edward E.|Cellular SPAR apparatus and method|

---

US20030172758A1|2002-03-12|2003-09-18|Anderson J. Hilbert|Load equalization in gear drive mechanism|

---

US6942019B2|2002-03-25|2005-09-13|Ltx Corporation|Apparatus and method for circuit board liquid cooling|

---

US6663343B1|2002-06-27|2003-12-16|Sea Solar Power Inc|Impeller mounting system and method|

---

US6634853B1|2002-07-24|2003-10-21|Sea Solar Power, Inc.|Compact centrifugal compressor|

---

GB2391281B|2002-07-26|2005-11-02|Coflexip Stena Offshore Ltd|Seal assembly|

---

AU2003272090B2|2002-10-02|2008-08-07|Showa Denko K.K.|Heat exchanging tube and heat exchanger|

---

JP2006336873A|2002-10-02|2006-12-14|Showa Denko Kk|Heat exchanging tube and heat exchanger|

---

US6718901B1|2002-11-12|2004-04-13|Technip France|Offshore deployment of extendable draft platforms|

---

JP4212888B2|2002-12-26|2009-01-21|三菱化学エンジニアリング株式会社|Plate type catalytic reactor|

---

CN2670889Y|2003-07-28|2005-01-12|张曼丽|Wide-channel plane smelting heat exchanger|

---

FR2858841B1|2003-08-14|2007-02-09|Technip France|METHOD OF DRAINING AND EXHAUSTING GAS FROM PERMEATION OF A FLEXIBLE TUBULAR DRIVE AND CONDUCT SUITABLE FOR ITS IMPLEMENTATION|

---

US20070028626A1|2003-09-02|2007-02-08|Sharp Kabushiki Kaisha|Loop type thermo siphon, stirling cooling chamber, and cooling apparatus|

---

FR2859495B1|2003-09-09|2005-10-07|Technip France|METHOD OF INSTALLATION AND CONNECTION OF UPLINK UNDERWATER DRIVING|

---

JP2005127650A|2003-10-27|2005-05-19|Hitachi Ltd|Plate fin type regenerative heat exchanger and gas turbine power generation system|

---

FR2861894B1|2003-10-31|2008-01-18|Valeo Equip Electr Moteur|DEVICE FOR COOLING A POWER ELECTRONIC|

---

JP4119836B2|2003-12-26|2008-07-16|株式会社コベルコマテリアル銅管|Internal grooved heat transfer tube|

---

FR2865028B1|2004-01-12|2006-12-29|Ziepack|THERMAL EXCHANGER AND EXCHANGE MODULE RELATING THERETO|

---

US7343965B2|2004-01-20|2008-03-18|Modine Manufacturing Company|Brazed plate high pressure heat exchanger|

---

FR2865484B1|2004-01-28|2006-05-19|Technip France|STRUCTURE FOR TRANSPORTING, INSTALLING AND DISMANTLING THE ELEMENTS OF A FIXED PETROLEUM PLATFORM AND METHODS OF IMPLEMENTING SUCH A STRUCTURE|

---

US20060008695A1|2004-07-09|2006-01-12|Dingrong Bai|Fuel cell with in-cell humidification|

---

WO2006042178A1|2004-10-08|2006-04-20|Technip France|Spar disconnect system|

---

US7328578B1|2004-10-15|2008-02-12|Eduardo Saucedo|Integrated OTEC platform|

---

US7431623B1|2004-10-15|2008-10-07|Eduardo Saucedo|Modular vertical floating pipe|

---

KR101104278B1|2005-03-30|2012-01-12|한라공조주식회사|Plate for heat exchanger|

---

US7594683B2|2005-04-13|2009-09-29|National Oilwell Varco, L.P.|Pipe elevator with rotating door|

---

FR2886711B1|2005-07-13|2008-11-21|Technip France Sa|DEVICE FOR REGULATING THE FLAMMING OF SUB-MARINE PIPES|

---

EP1788335A1|2005-11-18|2007-05-23|Methanol Casale S.A.|Method for the production of a plate type heat exchanger and related heat exchanger|

---

US7472742B2|2005-12-01|2009-01-06|General Electric Company|Heat sink assembly|

---

JP2007278568A|2006-04-05|2007-10-25|Matsushita Electric Ind Co Ltd|Heat exchanger|

---

US7380544B2|2006-05-19|2008-06-03|Modine Manufacturing Company|EGR cooler with dual coolant loop|

---

US20070289303A1|2006-06-15|2007-12-20|Prueitt Melvin L|Heat transfer for ocean thermal energy conversion|

---

JP4765829B2|2006-08-11|2011-09-07|株式会社デンソー|Ejector refrigeration cycle unit|

---

FR2905444B1|2006-08-30|2009-12-25|Technip France|TUBULAR DRIVING CARCASE IN STRIP FILLING AND DRIVING COMPRISING SUCH A CARCASS|

---

FR2906595B1|2006-09-29|2010-09-17|Technip France|FLEXIBLE TUBULAR FASTENING FIT WITH HIGH RESISTANCE|

---

US7610949B2|2006-11-13|2009-11-03|Dana Canada Corporation|Heat exchanger with bypass|

---

US20080295517A1|2007-05-30|2008-12-04|Howard Robert J|Extraction of noble gases from ocean or sea water|

---

US7900452B2|2007-06-19|2011-03-08|Lockheed Martin Corporation|Clathrate ice thermal transport for ocean thermal energy conversion|

---

US8001784B2|2007-07-13|2011-08-23|Bruce Marshall|Hydrothermal energy and deep sea resource recovery system|

---

US20090077969A1|2007-09-25|2009-03-26|Prueitt Melvin L|Heat Transfer Methods for Ocean Thermal Energy Conversion and Desalination|

---

FR2921994B1|2007-10-03|2010-03-12|Technip France|METHOD OF INSTALLING AN UNDERWATER TUBULAR CONDUIT|

---

FR2923522B1|2007-11-13|2010-02-26|Technip France|DEVICE FOR MEASURING THE MOVEMENT OF A DEFORMABLE SUBMARINE CONDUCT|

---

CA2710197C|2007-12-21|2015-11-24|Technip France|Spar with detachable hull structure|

---

US7735321B2|2008-01-15|2010-06-15|Lockheed Martin Corporation|OTEC cold water pipe system|

---

FR2927651B1|2008-02-19|2010-02-19|Technip France|UPLINK COLUMN INSTALLATION METHOD|

---

US20090217664A1|2008-03-03|2009-09-03|Lockheed Martin Corporation|Submerged Geo-Ocean Thermal Energy System|

---

KR100953907B1|2008-03-06|2010-04-22|차재현|Base plate for evaporating refrigerant and evaporator using thereof|

---

US7870732B2|2008-04-01|2011-01-18|Fang Sheng Kuo|Submarine cold water pipe water intake system of an ocean thermal energy conversion power plant|

---

US7851080B2|2008-04-09|2010-12-14|Gm Global Technology Operations, Inc.|Battery cooling plate design with discrete channels|

---

US8079508B2|2008-05-30|2011-12-20|Foust Harry D|Spaced plate heat exchanger|

---

US7735322B2|2008-06-06|2010-06-15|Fang Sheng Kuo|Wave elimination system for ocean thermal energy conversion assembly|

---

US8025834B2|2008-06-13|2011-09-27|Lockheed Martin Corporation|Process and apparatus for molding continuous-fiber composite articles|

---

US8540012B2|2008-06-13|2013-09-24|Lockheed Martin Corporation|Heat exchanger|

---

US8550153B2|2008-10-03|2013-10-08|Modine Manufacturing Company|Heat exchanger and method of operating the same|

---

US7882703B2|2008-10-08|2011-02-08|Lockheed Martin Corporation|System and method for deployment of a cold water pipe|

---

CN201301785Y|2008-11-05|2009-09-02|上海海事大学|High-efficiency ocean thermal energy power-generation device|

---

TWI367990B|2008-11-14|2012-07-11|Ind Tech Res Inst|Ocean thermal energy conversion power plant and condensor thereof|

---

US8182176B2|2008-11-21|2012-05-22|Lockheed Martin Corporation|Tendon-supported membrane pipe|

---

US8146362B2|2008-12-04|2012-04-03|Lockheed Martin Corporation|OTEC system|

---

US8117843B2|2008-12-04|2012-02-21|Lockheed Martin Corporation|Ocean thermal energy conversion system|

---

KR20100074435A|2008-12-24|2010-07-02|서진욱|A plate heat exchanger|

---

US8250847B2|2008-12-24|2012-08-28|Lockheed Martin Corporation|Combined Brayton-Rankine cycle|

---

US8567194B2|2009-01-16|2013-10-29|Lockheed Martin Corporation|Floating platform with detachable support modules|

---

US8353162B2|2009-02-14|2013-01-15|Lockheed Martin Corporation|Recoverable heat exchanger|

---

FR2945098B1|2009-04-30|2011-05-27|Technip France|DEVICE FOR PROTECTING AT LEAST ONE CONDUIT LOCATED AT THE BOTTOM OF A WATER EXTEND AND ASSOCIATED FLUID TRANSPORT ASSEMBLY|

---

US8070389B2|2009-06-11|2011-12-06|Technip France|Modular topsides system and method having dual installation capabilities for offshore structures|

---

EP2470419B1|2009-08-26|2015-11-04|Technip France|Heave stabilized barge system for floatover topsides installation|

---

WO2011035943A2|2009-09-28|2011-03-31|Abb Research Ltd|Cooling module for cooling electronic components|

---

US9777971B2|2009-10-06|2017-10-03|Lockheed Martin Corporation|Modular heat exchanger|

---

GB2474428B|2009-10-13|2012-03-21|Technip France|Umbilical|

---

ES2503065T3|2009-10-21|2014-10-06|Technip France|System and procedure of vertical axis floating wind turbine module|

---

GB0918589D0|2009-10-23|2009-12-09|Technip France|Methods of reel-laying a mechanically lined pipe|

---

US8152949B2|2009-11-20|2012-04-10|Lockheed Martin Corporation|Pultruded arc-segmented pipe|

---

AU2010324620B2|2009-11-30|2014-10-02|Technip France|Power umbilical|

---

US20110127022A1|2009-12-01|2011-06-02|Lockheed Martin Corporation|Heat Exchanger Comprising Wave-shaped Fins|

---

US8899043B2|2010-01-21|2014-12-02|The Abell Foundation, Inc.|Ocean thermal energy conversion plant|

---

US9086057B2|2010-01-21|2015-07-21|The Abell Foundation, Inc.|Ocean thermal energy conversion cold water pipe|

---

KR102052726B1|2010-01-21|2019-12-06|더 아벨 파운데이션, 인크.|Ocean thermal energy conversion power plant|

---

US8083902B2|2010-05-25|2011-12-27|King Fahd University Of Petroleum And Minerals|Evaporative desalination system|

---

CN106864672B|2010-05-28|2019-09-06|洛克希德马丁公司|Subsea anchor system and method|

---

JP2013531178A|2010-07-14|2013-08-01|ジアベルファウンデーション，インコーポレイテッド|Industrial ocean thermal energy conversion process|

---

EP2413045B1|2010-07-30|2014-02-26|Grundfos Management A/S|Heat exchange unit|

---

US20120043755A1|2010-08-20|2012-02-23|Makai Ocean Engineering Inc.|System and Method for Relieving Stress at Pipe Connections|

---

US9670911B2|2010-10-01|2017-06-06|Lockheed Martin Corporation|Manifolding arrangement for a modular heat-exchange apparatus|

---

US9388798B2|2010-10-01|2016-07-12|Lockheed Martin Corporation|Modular heat-exchange apparatus|

---

US8776538B2|2010-10-01|2014-07-15|Lockheed Martin Corporation|Heat-exchange apparatus with pontoon-based fluid distribution system|

---

US8444182B2|2010-11-04|2013-05-21|Sea Energy Technology Co, Ltd.|Water intake pipe of ocean thermal energy conversion power plant|

---

US20120186781A1|2011-01-25|2012-07-26|Technip France|Online pigging system and method|

---

US8651038B2|2011-01-28|2014-02-18|Technip France|System and method for multi-sectional truss spar hull for offshore floating structure|

---

US9513059B2|2011-02-04|2016-12-06|Lockheed Martin Corporation|Radial-flow heat exchanger with foam heat exchange fins|

---

US20120201611A1|2011-02-07|2012-08-09|Technip France|Method and apparatus for facilitating hang off of multiple top tension riser or umbilicals from a compensated tensioning deck|

---

US8430050B2|2011-02-24|2013-04-30|Technip France|System and method for deck-to-column connection for extendable draft offshore platforms|

---

EP2508831B1|2011-04-07|2015-12-16|Alfa Laval Corporate AB|Plate heat exchanger|

---

BR112014002798A2|2011-08-09|2017-03-07|Lockheed Corp|Method and apparatus for rotary friction welding of pipe ends in the heat exchanger|

---

US20130042612A1|2011-08-15|2013-02-21|Laurence Jay Shapiro|Ocean thermal energy conversion power plant|

---

US20130153171A1|2011-12-14|2013-06-20|Lockheed Martin Corporation|Composite heat exchanger shell and buoyancy system and method|

---

EP2897911B1|2012-09-21|2017-08-09|Höganäs AB |Method for use of new iron powder composition|

---

US9408298B2|2014-03-18|2016-08-02|Eaton Corporation|Flexible circuit Rogowski coil|KR102330226B1|2014-01-20|2021-11-22|더 아벨 파운데이션, 인크.|Vessel-mounted ocean thermal energy conversion system|

---

EP3614092A1|2014-08-22|2020-02-26|Peregrine Turbine Technologies, LLC|Heat exchanger for a power generation system|

---

CN106999999A|2014-12-22|2017-08-01|诺维尔里斯公司|Cladded sheet materials for heat exchanger|

---

US10670312B2|2015-06-10|2020-06-02|Lockheed Martin Corporation|Evaporator having a fluid distribution sub-assembly|

---

US9655281B2|2015-06-26|2017-05-16|Seagate Technology Llc|Modular cooling system|

---

NO342528B1|2016-01-29|2018-06-11|Sperre Coolers As|Heat exchange system|

---

IT201600097320A1|2016-09-28|2018-03-28|Saipem Spa|Cross-flow heat exchanger|

---

EP3638971A4|2017-06-11|2020-06-03|Zvi Livni|Plate and shell heat exchanging system having a divided manifold tube|

---

CN108118296A|2017-12-08|2018-06-05|北京创昱科技有限公司|A kind of coldplate|

---

ES2885829T3|2017-12-22|2021-12-15|Cockerill Maintenance & Ingenierie Sa|Heat exchanger for a molten salt steam generator in a concentrated solar power plant |

---

WO2020082003A1|2018-10-19|2020-04-23|Timothy Burke|Undersea hydrothermal energy transfer system with removable redundant units|

---

IT201800021274A1|2018-12-27|2020-06-27|Cga Tech S R L|HEAT EXCHANGER AND RELATIVE METHOD OF IMPLEMENTATION|

---

JP6934609B2|2019-04-17|2021-09-15|パナソニックＩｐマネジメント株式会社|Heat exchanger and freezing system using it|

---

FR3097293B1|2019-06-17|2022-03-04|Naval Energies|Device for connecting two portions of a pipe and installation comprising such a device|

---

US11107595B2|2019-06-28|2021-08-31|Palvannanathan Ganesan|Floating nuclear reactor protection system|

---

USD903070S1|2019-07-05|2020-11-24|Cooler Master Co., Ltd.|Heat dissipation plate|

---

WO2022039795A1|2020-08-17|2022-02-24|Terrapower, Llc|Heat exchanger configuration for nuclear reactor|

法律状态:
2018-11-21| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

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2019-11-19| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

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2020-07-07| B06A| Patent application procedure suspended [chapter 6.1 patent gazette]|

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2020-11-10| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

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2021-01-19| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 15/10/2013, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

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申请号 | 申请日 | 专利标题

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US201261714538P| true| 2012-10-16|2012-10-16|

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US61/714,538|2012-10-16|

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US201261720591P| true| 2012-10-31|2012-10-31|

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US61/720,591|2012-10-31|

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PCT/US2013/065004|WO2014062653A1|2012-10-16|2013-10-15|Heat exchanger including manifold|

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