• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    heat exchanger configured for a power generation system. the present disclosure relates to a heat exchanger for a power generation system and related methods using supercritical fluids, and in particular to a heat exchanger configured to minimize axial forces during operation.
    公开号:BR112017003614B1
    申请号:R112017003614-2
    申请日:2015-08-21
    公开日:2021-08-17
    发明作者:David S. Stapp
    申请人:Peregrine Turbine Technologies, Llc；
    IPC主号:
    专利说明:

    technical field
    [0001] The present invention relates to a heat exchanger for a power generation system and related methods using supercritical fluids. Background
    [0002] Traditionally, thermodynamic power generation cycles, such as the Brayton cycle, employ an ideal gas, such as atmospheric air. Such cycles are typically open in the sense that, after air flows through the cycle components, it is discharged back to the atmosphere at a relatively high temperature so that a considerable amount of heat generated by the combustion of fuel is lost from the cycle. A common approach to capturing and utilizing waste heat in a Brayton cycle is to use a stove to extract heat from the turbine exhaust gases and transfer it, through a heat exchanger, to the exhaust air from of the compressor. Since such heat transfer increases the temperature of the air entering the combustion chamber, less fuel is needed to reach the desired turbine inlet temperature. The result is improved thermal efficiencies for the overall thermodynamic cycle. However, even in such recovered cycles, thermal efficiency is limited by the fact that the turbine exhaust gas temperature can never be cooled below that of the compressor discharge air, since heat can only flow from a high temperature source to a lower temperature sink. More recently, interest has arisen regarding the use of supercritical fluids, such as supercritical carbon dioxide (SCO2), in closed thermodynamic power generation cycles.
    [0003] Typical thermodynamic power generation cycles, using supercritical fluids, include compressors, turbines, combustion chamber and heat exchangers arranged in a first Brayton cycle, in which the working fluid is a supercritical fluid, and a second Brayton cycle, in which the working fluid is ambient air. The heat exchangers required for heat transfer between the supercritical fluid cycle and the ambient cycle can be large, expensive and impractical to implement. More effectively managing flow cycles can improve heat transfer efficiency in power generation systems that utilize supercritical fluid cycles. summary
    [0004] One embodiment of the present disclosure is a heat exchanger configured for a power generation system. The heat exchanger includes at least one plate arrangement having a first end, a second end opposite the first end along an axial direction. Each plate array includes a plurality of plates stacked relative to one another. At least one plate array defines a first flow configuration and a second flow configuration that is separate from the first flow configuration. The first and second flow configurations extend from the first end to the second end so as to direct the first and second fluids, respectively, through at least one plate arrangement. The heat exchanger includes a housing arrangement that applies a tension force to at least one plate arrangement along the axial direction, such that when at least one plate arrangement is exposed to at least the predetermined temperature, each plate expands at least partially along the axial direction so as to reduce the tensile force applied to the plate arrangement. Brief description of the drawings
    [0005] The above summary, as well as the following detailed description of an embodiment, are best understood when read in conjunction with the accompanying schematic drawings. For the purpose of illustrating the invention, the drawings show an embodiment which is presently preferred. The invention is not limited, however, to the specific instruments disclosed in the drawings. In the drawings:
    [0006] Figure 1 is a perspective view of a heat exchanger according to an embodiment of the present disclosure;
    [0007] Figures 2A and 2B are perspective views of the heat exchanger shown in Figure 1, with collectors and portions of the housing arrangement removed for illustrative purposes;
    [0008] Figure 3A is a perspective view of an outer block used in the heat exchanger shown in Figure 1;
    [0009] Figure 3B is a perspective view of an intermediate block used in the heat exchanger shown in Figure 1;
    [0010] Figure 4 is a perspective view of the collector used in the heat exchanger shown in Figure 1;
    [0011] Figure 5A is a perspective view of a plate arrangement used in the heat exchanger shown in Figure 1;
    [0012] Figure 5B is a detailed perspective view of a portion of the plate arrangement shown in Figure 5A;
    [0013] Figure 5C is an exploded perspective view of the first, second and third plates of the plate arrangement shown in Figure 5A;
    [0014] Figure 6 is a perspective view of a heat exchanger according to another embodiment of the present disclosure;
    [0015] Figure 7 is a plan view of a plate used in the heat exchanger shown in Figure 6;
    [0016] Figure 8A is a perspective view of a heat exchanger according to another embodiment of the present disclosure;
    [0017] Figure 8B is a detailed view of a connector illustrated in Figure 8A;
    [0018] Figure 8C is a cross-sectional view of the heat exchanger illustrated in Figure 8A;
    [0019] Figure 8D is a plan view of a plate used in the heat exchanger shown in Figure 8A; and
    [0020] Figure 9 is a schematic diagram of a power generation system according to an embodiment of the disclosure. Detailed Description
    [0021] Referring to Figure 1, one embodiment of the disclosure is a heat exchanger 2 configured for a power generation system such that the power generation system includes a first closed Brayton cycle in which it includes a first fluid, which may be a supercritical fluid, and a second open Brayton cycle, which includes a second fluid, which may be ambient air. An example of power generation system 100 is described below and illustrated in Figure 9. Heat exchanger 2 is configured to transfer heat from one of the first and second fluids to the other of the first and second fluids, depending on the location of the heat exchanger along the power generation system.
    [0022] Continuing with Figure 1, heat exchanger 2 includes housing arrangement 10, which contains at least one plate arrangement 40, such as first and second plate arrangements 40a and 40b, and a plurality of collectors, such as a first pair of manifolds 90 and a second pair of manifolds 92. The manifolds are configured to direct respective fluids through the heat exchanger 2 to define first and second flow configurations, as explained further below. The heat exchanger 2 includes a first end 4, a second end 6 opposite the first end 2 along an axial direction A, a top 8a and a bottom 8b opposite the top 8a along a vertical direction V that is perpendicular to the axial direction A, and opposite sides 8c and 8d spaced apart along a lateral direction L that is perpendicular to the axial and vertical directions A and V. References to “top”, “bottom”, “side”, “left ”, or “right”, are for illustrative purposes only and should not be limiting. The vertical and transverse directions V and L can be referred to as the first and second directions.
    [0023] Frame arrangement 10 surrounds and supports plate arrangements 40a and 40b. More specifically, the carcass arrangement 10 applies a tension force to at least one plate arrangement 40 along the axial direction A, such that when at least one plate arrangement is exposed to at least a predetermined temperature, the plate arrangement 40 expands at least partially along the axial direction so as to reduce the tensile force applied to plate arrangement 40. The frame arrangement 10 and each plate arrangement 40a and 40b can be made from materials with different coefficients of thermal expansion, such that plate 40a and 40b and shell 10 arrangements expand at different temperatures, or have different rates of expansion at similar temperatures. This results in a limitation on the limiting axial forces applied to the plate arrangement 40 during operation, and can reduce thermal fatigue stresses. This also limits the thermally induced stress on various parts of components, which is the cause of thermal fatigue.
    [0024] Continuing with figures 2A and 2B, the housing arrangement 10 includes a first and second top blocks 12 and 14 coupled respectively to the first and second ends 42a and 44a of the first plate arrangement. The first and second bottom blocks 16 and 18 are respectively coupled to the first and second ends 42b and 44b of the second plate array. An example of top block 12 is shown in Figure 3A. Blocks 14, 16 and 18 are configured similarly to the top block 12 shown in Figure 3A. Housing arrangement 10 also includes central housing panels 20a, 20b, 20c and 20d (20d not shown) disposed between blocks 12 and 16 and blocks 14 and 18. Upper and lower central housing panels 20a and 20d are spaced apart with each other along the vertical direction V. The central casing panels 20b and 20c are spaced from one another along the lateral direction L. Consequently, central casing panels 20a, 20b, 20c and 20d surround a central part of the arrays of plate 40a and 40b, such that the central housing panels 20a, 20b, 20c and 20d are spaced apart from, and not directly connected to, portions of plate arrays 40a and 40b. Housing panels 20a, 20b, 20c and 20d can be evacuated to eliminate heat transfer from plate arrangements 40a and 40b to housing arrangement 10. In addition, one or more pressure sensors (not shown) may be used to monitor leaks. The housing arrangement 10 may further define a closed environment, specifically, the housing arrangement is vacuum sealed.
    [0025] Referring to Figures 2A and 2B, heat exchanger 2 also includes first and second intermediate blocks 22 and 24. First intermediate block 22 is positioned between first ends 42a and 42b of plate arrays 40a and 40b. The second intermediate block 24 is positioned between the second end 44a and 44b of plate arrays 40a and 40b. Consequently, the intermediate blocks 22 and 24 are spaced apart from the first and second plate arrays 40a and 40b with respect to each other along the vertical direction V. As shown in Figure 3B, the intermediate blocks 22 and 24 each respectively include arms 26. and 28, which define a U-shaped opening 30 therebetween. The outer sides of the arms 26 and 28 include cutouts 32 that receive ends of the center side housing panels 20b and 20c such that the housing panels 20b and 20c are aligned with the outer end of the intermediate blocks. Attaching intermediate blocks 22 and 24 to the ends of plate arrays 40a and 40b decouples the mechanical responses, such as expansion and contraction, of each plate array 40a and 40b to fluctuations in temperature exposures during operation. In other words, the first and second plate arrays 40a and 40b can independently expand along the axial direction A when exposed to at least the predetermined temperature.
    [0026] Figures 5A and 5B illustrate a first plate arrangement 40a used in heat exchanger 2. The second heat exchanger 40b is substantially similar to the first plate arrangement 40a. Thus, only the first plate arrangement 40a will be described below. Plate array 40a includes a stack of plates including a plurality of plates 70 stacked one against the other, an upper leveling plate 48 and a lower leveling plate 50 (not shown). Plates 46, 48 and 50 may have substantially the same shape. In the illustrated embodiment the plate arrangement 40a includes ten separate plates. However, more than ten or less than ten plates can be used.
    [0027] Continuing with Figures 5A and 5B, the plate arrangement 40a defines the first flow configuration 52, and a second flow configuration 54 that is separate from the first flow configuration 52. Each of the first and second flow configurations 52 and 54 extend from first end 42a to second end 44a to respectively direct first and second fluids through plate arrangement 40a. As illustrated, first end 42a can define an inlet end of plate array 40a and second end 44a can define an outlet end of plate array 40a such that fluids generally flow through end heat exchanger 2 42a to end 44a. Accordingly, the first flow configuration 52 includes a first inlet 53a, defined by the first end 42a of the plate array 40a, and a first outlet end 53b defined by the second end 44a. The second flow configuration 54 includes a second inlet 55a defined by first end 42a and a second outlet 55b by second end 44a of plate array 40a.
    [0028] The heat exchanger 2 is mounted in the cold state such that the plate arrangement 40a is tensioned along the axial direction A. When heating during use, at least a part of the plate arrangement 40a can expand along the axial direction A so as to minimize axial forces when the plate arrangement 40a is exposed to design operating temperatures. For example, plate array 40a includes a first platform segment 56, which defines the first end 42a, a second platform segment 58, which defines the second end 44a, and a serpentine portion that extends between the first platform segment. 56 and second platform segment 58. The serpentine portion includes first and second serpentine segments 60 and 62. Serpentine segments 60 and 62 include notch portions 64 configured to allow expansion and contraction of serpentine segments 60 and 62 along the axial direction A.
    [0029] The first pair of manifolds 90 attached to the first end 42a of the plate array 40a so as to be aligned with the pair of inlets 53a and 55a of the first pair of openings of the first and second flow configurations. The second pair of manifolds 92 connected to the second end 44a of the plate array 40a so as to be aligned with the outlets 53b and 55b.
    [0030] Figure 5C illustrates the configuration of plates that define the arrangement of plate 40a. As noted above, plate stack 46 includes a plurality of arranged plates that define the first and second flow configurations 52 and 54 described above. Figure 5C illustrates three plates in an exploded view. The top and bottom plates are similar and each can be referred to as a first type of plate 70a. Center plate 70b differs from plate 70a and may be referred to as the second type of plate.
    [0031] Consequently, stack 46 includes first and second types of boards that define the flow settings 52 and 54, as detailed below. Plate 70a will be described below, it being understood that plates 70a and 70b are similar, unless otherwise indicated. Plate 70a includes opposite ends 72a and 72b, a left side 72c and a right side 72d opposite the left side 72c along the lateral direction. As illustrated, the left side 72c is disposed on the left side of the page, and the right side 72d is right-to-left 72c on the sheet. The use of “left” and “right” should not be a limiting factor here. Plate 70a also defines a lower surface 71a and an upper surface 71b opposite the lower surface. The bottom surface 71a is a substantially flat one. Top surface 71b defines first and second flow channels 80 and 82. First and second flow channels 80 and 82 will be described further below.
    [0032] Continuing with Figure 5C, plate 70a includes a first platform 74, a second platform 76, and at least one serpentine segment extending from the first platform 74 to the second platform 76. As illustrated, the plate 70a includes a first coil platform 78r and a second coil platform 78l. When the plates are mounted on stack 46, the first platforms for each plate define the first platform segment 56 of the plate array 40a, the second platforms for each plate define the second platform segment 58 of the plate array 40a, the first platforms of serpentine platforms define the first serpentine segment 60 of the plate arrangement 40a, and the second serpentine platforms define the second serpentine segment 62 of the plate arrangement 40a. Each plate further defines a plurality of slots 64 which are elongated along a lateral direction L. Each slot 64 allows each plate 70a to expand, at least partially, along the axial direction A.
    [0033] As described above, each plate defines a first flow channel 80 and a second flow channel 82 that is separate from the first flow channel 80. The first flow channel 80 extends along the first serpentine platform 78r, and second flow channel 82 extends along second coil platform 78l. Plate 70a includes first flow channel portals 84a and 84b disposed, respectively, at opposite ends 72a and 72b of plate 70a. Plate 70a also includes second flow channel portals 86a and 86b disposed at opposite ends 72a and 72b of plate 70a, respectively. Plate 70b, however, includes first flow channel portals 84c and 84d disposed, respectively, at opposite ends 72a and 72b of plate 70b. Plate 70b also includes second flow channel portals 86c and 86d disposed, respectively, at opposite ends 72a and 72b of plate 70b.
    [0034] The differences between plate 70a, or the first type of plate, and plate 70b, of the second type of plate, is the location of the flow channel portals along opposite ends 72a and 72b of the plates. More specifically, plate 70a includes first and second channel flow portals configured as inputs 84a and 86a that are arranged closer to the left side 72c than to the right side 72d, and the first and second channel flow portals configured as outputs 84b and 86b which are arranged closer to the right side 72d than to the left side 72c. Plate 70a may be referred to as a “right exit” plate. Plate 70b, however, includes first and second channel stream portals configured as inputs 84c and 86c that are disposed closer to the right side 72d than to the left side 72c, and the first and second channel stream portals configured as outputs 84d and 86d that are arranged closer to the left side 72c than to the right side 72d. Plate 70b may be referred to as a “left exit” plate. The first and second plates 70a and 70b are alternately stacked such that the first and second channel streams of each first plate 70a define the first stream configuration 52, and the first and second channels of each second plate 70b define the second configuration. flow 54. At least a portion of the first flow channel 80 and the second flow channel 82 are parallel to each other along the platform portions.
    [0035] Figures 6 and 7 illustrate a heat exchanger 302 according to another embodiment of the present disclosure. Heat exchanger 302 is similar to heat exchanger 2. Similar components of each heat exchanger have similar reference signs. In accordance with the illustrated embodiment, heat exchanger 302 includes housing arrangement 10 and plate arrangement 340a. In addition, each plate array 340a includes a plurality of stacked plates, including a first type plate 370a and a second type plate 370b. Each plate defines a single coil segment 360 that extends between the ends of platform 56 and 58. In addition, plate 370a defines a single flow channel 352 that extends along coil platform 360. The plate arrangement 340A defines portals 384 and 386. The frame arrangement 10 applies a tension force to the plate arrangement 340a along the axial direction A, such that when the plate arrangement 340a is exposed to at least a predetermined temperature, the arrangement of plate 340a expands at least partially along the axial direction A so as to reduce the tensile force applied to the plate arrangement 340a.
    [0036] Figures 8A-8D illustrate heat exchanger 402 according to another embodiment of the present disclosure. Heat exchanger 402 is similar to heat exchanger 2. Similar components of each heat exchanger have similar reference signs. Heat exchanger 402 includes a housing arrangement 410 and at least one plate arrangement 440a including a first end, a second end opposite the first end along the axial direction A.
    [0037] Each plate arrangement 440a includes a plurality of plates 470 stacked relative to one another along the lateral direction L. The heat exchanger defines a first flow configuration 442 through the plate arrangement 440a and the second flow configuration 444 which is defined by openings between adjacent plates 470 in each plate array 440a. A plurality of plate arrays 440a can be disposed end to end along the axial direction A.
    [0038] The 410 frame arrangement includes frame panels 415a and 415b, and a pair of compression rails 420a and 420b. Each compression rail 420a and 420b includes a first end and second end opposite the first end along the axial direction A. The compression rails 420a and 420b apply a force to the plate arrangement 440a along the lateral direction L. compression can be made of ceramic materials such as silicon carbide. Heat exchanger 402 also includes a first coupler arrangement 450a that couples the first ends of the compression rail pair 420a and 420b to one another, and a second coupler arrangement 450b that couples the second ends of the compression rail pair 420a and 420b each other. The first coupler arrangement 450a is coupled to an inlet end of a first plate arrangement 440a so that the first coupler arrangement 450a defines an inlet path for a fluid within the first plate arrangement 440a. The second coupler arrangement 450b is coupled to the outlet end of a second plate arrangement 440n such that the second coupler arrangement 450b defines an outlet path for fluid to exit the second plate arrangement 450n. As shown in Figure 8D, each plate 470 includes a first curved cutout 472, a second curved cutout 474, a center cutout 475, and a slot 476 that extends from the first curved cutout 472 to the second curved cutout 476. 470 defines an internal flow channel 478. Flow channels 478 of each plate in heat exchanger 402 define the first flow configuration.
    [0039] Figure 9 is a schematic diagram of a power generation system 100 in accordance with an aspect of the disclosure. The power generation system 100 includes a first closed Brayton cycle 102, in which the working fluid may be a supercritical fluid, and a second open Brayton cycle 104, in which the working fluid may be ambient air. The first Brayton cycle 102 and the second Brayton cycle 104 respectively include a supercritical fluid flow path 106 and an air fluid flow path 108. The flow paths 106 and 108 are, in one embodiment, separate so that little or no mixing occurs between the supercritical fluid and the air between the two flow paths 106 and 108.
    [0040] The power generation system 100 includes compressors, turbines, one or more combustion chambers, and a plurality of heat exchangers connected along flow paths 106 and 108. The heat exchangers include a plurality of heat exchangers. cross cycle heat 132, 134, 136, and 138. As used herein, the term "cross cycle heat exchanger" refers to a heat exchanger that receives air or both air and flue gas from the combustion cycle. aspirates air 104 as well as a supercritical fluid from the supercritical fluid cycle 102 and transfers heat between the fluids in the two cycles. Additionally, the power generation system 100 includes a recovery heat exchanger 130 along the supercritical fluid flow path 106. As used herein, the term "recovery heat exchanger" refers to heat transfers between the supercritical fluid discharged from the SCO2 turbine and the supercritical fluid discharged from the SCO2 compressor in supercritical fluid cycle 102. Power generation system 100 may also include valves 122, flow meters 140, mixing junctions 124, and one or more controllers configured to control the operation of system 100. Any one to all heat exchangers 130, 132, 134, 136, and 138 may be similar to heat exchanger 2, 302, or 402 as described above.
    [0041] Continuing with Figure 9, initially a stream 202 of supercritical fluid is fed into the inlet of a compressor 110, which may be an axial, radial, reciprocating or similar type compressor. Compressor 110 may be referred to as SCO2 first compressor 110. Compressor 110 includes a shaft 112 operatively connected to a turbine 114. Turbine 114 may be referred to as SCO2's first turbine 114. Flow meter 140 along stream 202 measures a flow rate of the supercritical fluid supplied to the compressor inlet. Flowmeter 140 facilitates control of total SCO2 accumulation in the 102 supercritical fluid cycle as well as transient flow behavior. In one aspect, the supercritical fluid enters the SCO2 110 compressor inlet after it has been cooled and expanded, as discussed below, to a temperature and pressure that are close to their critical points. The term "supercritical fluid" refers to a fluid in which there are no separate liquid and gas phases, and the term "critical point" of a supercritical fluid refers to the lowest temperature and pressure at which the substance can be considered. in a supercritical state. The terms "critical temperature" and "critical pressure" refer to the temperature and pressure at the critical point. For carbon dioxide, the critical point is approximately 31.05°C (304.2°K) and 7.35 MPa. In one embodiment, the supercritical fluid entering compressor 110 is cooled to at least ± -271.14°C (2°K) of its critical point. In a further embodiment, the supercritical fluid entering compressor 110 is cooled to within ± -272.15°C (1°K) of its critical point. In yet another embodiment, the supercritical fluid entering compressor 110 is cooled to within ± -272.95°C (0.2°K) of its critical point.
    [0042] Continuing with Figure 9, after compression in the SCO2 compressor 110, the supercritical fluid discharge stream 4 is divided into first and second portions as first and second discharge streams 206 and 208. Streams 206 and 208 can be referred to herein as compressor discharge currents 206 and 208. The split allows the first part of the discharge stream 204, from compressor 110, to be recovered and the remaining part to be heated directly by a series of heat exchangers 134 and 132 by cycling air fluid through the flow path. 108. As illustrated, discharge current 204 is divided through valve 122a which may be in electronic communication with a controller (not shown). The controller operates or actuates valve 122a to direct flow through flow path 106 as required. In one aspect, valve 122a is configured to direct between 55% to about 75% of the discharge stream 204 to the first discharge stream 206. The flow balance of the discharge stream 204 is directed to the second discharge stream 208. In another aspect, valve 122a is configured to direct about 67% of the discharge stream 204 to the first discharge stream 206.
    [0043] Continuing with Figure 9, the first discharge stream 206 of the supercritical fluid is directed to the recovery heat exchanger 130 where heat is transferred from the heated SCO2 exiting the turbine 116 to the first discharge stream 206. 219 of heated SCO2 discharged from recovery heat exchanger 130 is routed to junction 124a and mixed with stream 210 of heated SCO2 exiting cross-cycle heat exchanger 134.
    [0044] As shown in Figure 9, the second discharge stream 208, from the SCO2 compressor 110, is directed to the cross-cycle heat exchanger 134. In the cross-cycle heat exchanger 134, the heat from the gas is combustion in flow path 108 is transferred to second discharge stream 208 of SCO2. Stream 210 discharged from heat exchanger 134 mixes with stream 219 of SCO2 from recovery heat exchanger 130 at junction 124a, as discussed above. Junction 124a may be joined, i.e., connected to conduits, or may include a mixing apparatus.
    [0045] The mixed stream 212 is supplied to the cross-cycle heat exchanger 132. In the cross-cycle heat exchanger 132, heat is transferred from the flue gas in the flow path 108 to the mixed stream of SCO2. Cross-cycle heat exchanger 132 discharges stream 214 of heated SCO2.
    [0046] The heated SCO2 stream 214 from the heat exchanger 132 is directed to the inlet of the first SCO2 turbine 114. The first SCO2 turbine 114 may be axial flow, radial flow, mixed, or similar type turbine. The first SCO2 turbine 114 expands the SCO2 and produces movement in the shaft that drives the SCO2 compressor 110, through the shaft 112. After expansion in the first SCO2 turbine 114, current 215 is recirculated through a second SCO2 turbine 116 which produces shaft motion to a generator 120, via shaft 118. Generator 120 may provide output power to system 100. In an alternative embodiment, cycle 102 may include a turbine 114 with shaft 118 connected to turbine 114 and generator 120. In such an embodiment, discharge current 16 could discharge from turbine 114 into a valve 1202b.
    [0047] Continuing with Figure 9, the discharge current 216 from the second SCO2 turbine 116 can be divided into first and second portions as discharge current 218 and discharge current 202. Discharge current 218 and discharge stream 202 may be referred to as first and second discharge streams 18 and 202. As illustrated, valve 1202b may divide discharge stream 216 into first and second discharge streams 18 and 202. The controller operates or actuates valve 122b. In one aspect, valve 122b is configured to direct between 70% to about 90% of the discharge stream 216 within the second discharge stream 202. The flow balance of the discharge stream 216 is directed to the first discharge stream 218. In another aspect, valve 122b is configured to direct about 80% of the discharge current 216 into the second discharge stream 202. Regardless of which way the discharge current 216 of the SCO2 turbine is split, the first discharge current 218 is directed to cross-cycle heat exchanger 136 and cooled by the flow of air passing through heat exchanger 136 along flow path 108.
    [0048] The second discharge stream 202 is directed to the recovery heat exchanger 130, where heat from the discharge stream 202 is transferred to the first discharge stream 206 from the SCO2 compressor 110. In other words, the recovery heat exchanger 130 cools the discharge stream 202 of SCO2. Discharge stream 224 of the cooled SCO2 from recovery heat exchanger 130 is mixed with an input stream 202 from heat exchanger 136 at a junction 124b. From junction 124b, mixed stream 126 is routed to cross-cycle heat exchanger 138 (which may be optional). For example, mixed stream 126 can be directly routed to compressor 110. As noted above, in cross-cycle heat exchanger 138, heat from mixed stream 126 of SCO2 is transferred to flow path 108 of the air loop. 104. Current 128 from the cooled SCO2 is routed through a chiller 126 (which may be optional) and is returned to the compressor input of SCO2 110 as stream 202. Additional SCO2 from a supply 109 can be fed into stream 202 of SCO2 directed to the SCO2 compressor 110 to compensate for any SCO2 leakage from the system. In either case, the current from SCO2 202 is returned to the inlet of compressor 110 and the compression-heating-expansion-cooling steps are repeated.
    [0049] Continuing with Figure 9, the air aspiration cycle 104, part of the overall system 100, forms an open flow path 108. Initially, ambient air 101 is supplied to an aspirated air compressor 150 which may be a axial, reciprocating, radial, or similar type compressor. Compressor 150 includes a shaft 152 operatively connected to a turbine 154. Compressed air stream 230 from compressor 150 is then heated in heat exchanger 138 (which may be optional) by transferring heat from the mixed stream of SCO2 2026 is discharged from turbine 116 through heat exchangers 130 and 136, as discussed above. The heated compressed air stream 232 is then directed to the heat exchanger 136, where heat from the SCO2 stream 218 (from the SCO2 turbine 116) is transferred to the compressed air stream 232. Discharge stream 234 is directed to combustion chamber 158. Combustion chamber 158 increases the temperature of compressed air stream 234 above the temperature required at the turbine inlet of turbine 154. Compressor 150 can operate via driven shaft 152. by turbine 154. Combustion chamber 158 may receive a stream of fuel 103, such as fossil fuels or other fuel. Combustion chamber 158 may operate by means of a solar collector or nuclear reactor to produce system heat or some other heat source, including the combustion of waste, biomass, or bi-derived fuels. Flue gas discharge stream 236 from combustion chamber 158 may be directed to turbine 154, where it is expanded. Hot expanded flue gas stream 220 is directed to heat exchanger 132 where heat is transferred from the hot flue gas to mixed stream 212 of SCO2 discussed above. After exiting heat exchanger 132, hot flue gas stream 241 is routed to heat exchanger 134, where heat is transferred from the hot flue gas to SCO2 discharge stream 208 of SCO2 compressor 110 , as discussed above. Discharge stream 107 from heat exchanger 134 can be discharged to atmosphere.
    [0050] The above description is provided for purposes of explanation and is not to be construed as limiting the invention. While the invention has been described with reference to preferred aspects or preferred methods, it is understood that the words which have been used herein are words of description and illustration, as opposed to words of limitation. Additionally, although the invention has been described herein with reference to particular structure, methods and aspects, the invention is not intended to be limited to the details described herein, as the invention extends to all structures, methods and uses which fall within the scope of scope of the appended claims. Those skilled in the art, having the benefit of the teachings of this specification, can make numerous modifications to the invention, as described herein, and changes can be made without departing from the scope and spirit of the invention as defined by the appended claims.
    权利要求:
    Claims (20)
    [0001]
    1. A heat exchanger configured for a power generation system, said heat exchanger (2) comprising: - at least one plate arrangement (40, 40a, 40b, 340a, 440a, 440n, 450n) including a first end ( 42a, 42b), a second end (44a, 44b) opposite the first end (42a, 42b) along an axial direction, each plate array (40, 40a, 40b, 340a, 440a, 440n, 450n) including a plurality of plates (70, 46, 48, 40, 70a, 70b, 370a, 370b, 470) stacked relative to one another, the at least one plate array defining a first flow configuration (52, 442) and a second flow configuration (54, 444) which is separated from the first flow configuration (52, 442), the first and second flow configurations extending from the first end (42a, 42b) to the second end (44a, 44b) so as to direct first and second fluids, respectively, through at least one plate arrangement (40, 40a, 40b, 340a, 440a, 440n, 450n), ca. characterized by the fact of a housing arrangement (10, 410) that applies a tension force to at least one plate arrangement (40, 40a, 40b, 340a, 440a, 440n, 450n) along the axial direction, in such a way that when at least one plate arrangement (40, 40a, 40b, 340a, 440a, 440n, 450n) is exposed to at least the predetermined temperature, each plate expands at least partially along the axial direction so as to reduce the tensile force applied to the plate array (40, 40a, 40b, 340a, 440a, 440n, 450n).
    [0002]
    2. Heat exchanger according to claim 1, characterized in that at least one plate arrangement includes a first platform segment (56) defining the first end (42a, 42b), a second platform segment (58) defining the second end (44a, 44b) and at least one serpentine segment extending between the first platform segment (56) and the second platform segment (58).
    [0003]
    3. Heat exchanger according to claim 2, characterized in that at least one coil segment is a first coil segment (60) and a second coil segment (62) that is separate from the first coil segment ( 60).
    [0004]
    4. Heat exchanger according to claim 1, characterized in that the at least one plate arrangement is a first plate arrangement (40a) and a second plate arrangement (40b), such that the first and the second plate arrangement (40a, 40b) can independently expand along the axial direction (A) when exposed to at least the predetermined temperature.
    [0005]
    5. Heat exchanger according to claim 1, characterized in that the at least one plate arrangement is a first plate arrangement (40a) and a second plate arrangement (40b), and the first plate arrangement ( 40a) and the second plate arrangement (40b) are spaced apart from each other along a vertical direction (V) which is perpendicular to the axial direction (A).
    [0006]
    6. Heat exchanger according to claim 2, characterized in that the at least one plate arrangement is a first plate arrangement (40a) and a second plate arrangement (40b), and the heat exchanger (2 ) further comprise a first intermediate block (22) disposed between the first ends (42a, 42b) of the first and second plate arrays, and a second intermediate block (24) disposed between the second ends (44a, 44b) of the first and second slab arrays, such that the first and second intermediate blocks (22, 24) are separated from the first slab array (40a) from the second slab array (40b).
    [0007]
    7. Heat exchanger according to claim 1, characterized in that the at least one plate arrangement is a first plate arrangement and a second plate arrangement, and the first plate arrangement and the second plate arrangement are spaced relative to each other along the axial direction (A).
    [0008]
    8. Heat exchanger according to claim 1, characterized in that the first flow configuration (52) includes a first inlet (53a) defined by the first end (42a) of at least one plate arrangement (40a) and a first outlet (53b) defined by the second end (44a) of the at least one plate array, the second flow configuration (54) including a second inlet (55a) defined by the first end (42a) of the at least one array. of plate (40a) and a second outlet (55b) defined by the second end (44a) of at least one plate array (40a).
    [0009]
    9. Heat exchanger according to claim 8, characterized in that it further comprises a first pair of collectors (90) attached to the first end (42a) of at least one plate arrangement (40a), and a second pair of manifolds (92) attached to the second end (44a) of at least one plate array (40a), the first pair of manifolds (90) being aligned with a first pair of openings (53a and 55a) of the first and second configurations of flow, the second pair of manifolds (92) being aligned with a second pair of openings (53b, 55b) of the first and second flow configurations.
    [0010]
    10. Heat exchanger according to claim 1, characterized in that the plurality of plates (70, 46, 48, 40, 70a, 70b, 370a, 370b, 470) are stacked relative to one another along a vertical direction (V) that is perpendicular to the axial direction (A).
    [0011]
    11. Heat exchanger according to claim 1, characterized in that the plurality of plates (70, 46, 48, 40, 70a, 70b, 370a, 370b, 470) are stacked relative to one another along a lateral direction that is perpendicular to the axial direction (A).
    [0012]
    12. Heat exchanger according to claim 1, characterized in that each plate defines a first flow channel (80) and a second flow channel (82) that is separate from the first flow channel (80) .
    [0013]
    13. Heat exchanger according to claim 1, characterized in that two different plates define a first flow channel and a second flow channel that is separate from the first flow channel.
    [0014]
    14. Heat exchanger according to claim 12, characterized in that each plate includes a first platform (74), a second platform (76), and at least one coil segment extending from the first platform ( 74) to the second platform (76).
    [0015]
    15. Heat exchanger according to claim 14, characterized in that the at least one coil segment is a first coil platform (78r) and a second coil platform (78l), and the first flow channel (80 ) extending along the first serpentine platform (78r), and the second flow channel (82) extending along the second serpentine platform (78l).
    [0016]
    16. Heat exchanger according to claim 12, characterized in that each plate includes opposite ends (72a, 72b), a left side (72c) and a right side (72d) opposite the left side (72c), being that a first plate (70a) of at least one plate array includes first and second inlets (84a, 86a) of flow channels that are arranged closer to the left side (72c) than the right side (72d), and first and second outlets (84d, 86d) of the flow channel which are arranged closer to the right side (72d) than to the left side (72c).
    [0017]
    17. A heat exchanger according to claim 16, characterized in that a second plate (70b) of at least one plate arrangement includes first and second inlets (84c, 86c) of the flow channels that are further disposed. closer to the right side (72d) than the left side (72c), and first and second outlets (84d, 86d) of the flow channel that are arranged closer to the left side (72c) than the right side (72d) .
    [0018]
    18. Heat exchanger according to claim 17, characterized in that the first and second plates (70a, 70b) are stacked alternately such that the first and second channels of each first plate (70a) define the first flow configuration (52), and the first and second channels of each second plate (70b) define the second flow configuration (54).
    [0019]
    19. Heat exchanger according to claim 12, characterized in that each plate includes a lower surface (71a) and an upper surface (71b) opposite the lower surface (71a), wherein the lower surface (71a) is flat, and the upper surface (71b) defines the first and second flow channels (80, 82).
    [0020]
    20. Heat exchanger according to claim 13, characterized in that a part of the first flow channel (80) and the second flow channel (82) are parallel to each other.
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    同族专利:
    公开号 | 公开日
    JP6921915B2|2021-08-18|
    KR20170054411A|2017-05-17|
    CN106574518B|2019-05-10|
    WO2016029184A9|2017-03-16|
    CN106715840A|2017-05-24|
    WO2016029174A9|2016-08-04|
    US20160084584A1|2016-03-24|
    US10254048B2|2019-04-09|
    JP6594412B2|2019-10-23|
    WO2016029174A1|2016-02-25|
    WO2016029184A1|2016-02-25|
    EP3183433A1|2017-06-28|
    CN106715840B|2019-11-19|
    EP3183527A1|2017-06-28|
    US10101092B2|2018-10-16|
    BR112017003614A2|2017-12-05|
    JP2017526855A|2017-09-14|
    US20160053638A1|2016-02-25|
    US20190128615A1|2019-05-02|
    EP3183433B1|2019-10-09|
    EP3183527B1|2019-12-04|
    JP2020024084A|2020-02-13|
    US11073339B2|2021-07-27|
    CN106574518A|2017-04-19|
    EP3614092A1|2020-02-26|
    JP6702636B2|2020-06-03|
    KR20170057283A|2017-05-24|
    BR112017003616A2|2017-12-05|
    JP2017525925A|2017-09-07|
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    法律状态:
    2020-02-04| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-05-04| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-07-06| B09W| Correction of the decision to grant [chapter 9.1.4 patent gazette]|Free format text: REFERENTE A RPI 2626 DE 04/05/2021 |
    2021-08-17| 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 21/08/2015, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US201462040988P| true| 2014-08-22|2014-08-22|
    US62/040,988|2014-08-22|
    PCT/US2015/046400|WO2016029174A1|2014-08-22|2015-08-21|Heat exchanger for a power generation system|
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