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    • 专利摘要:
    HEAT EXCHANGE METHOD A heat exchange device is provided with an indirect evaporation heat exchange section. The indirect evaporation heat exchange section is made up of a series of serpentine tubes, and an evaporation liquid is passed down to the indirect heat exchange section. The evaporation liquid is collected in a tank and then pumped upwards to be distributed again through the indirect heat exchange section. An improved heat exchange device is provided with an indirect evaporation heat exchange section consisting of a series of serpentine tubes composed of tube paths, both of normal height and increased between tube paths. A heat exchange section direct flow can be provided in the increased vertical spacing between pipe paths. A secondary spray distribution can also be provided in the increased vertical spacing between pipe paths.
    公开号:BR112015023123B1
    申请号:R112015023123-3
    申请日:2014-03-06
    公开日:2020-12-22
    发明作者:David Andrew Aaron；Zan Liu；Branislav Korenic；John Edward Rule；Preston P. Blay；Philip S. Hollander；Glenn David Comisac；Gregory Michael Lowman
    申请人:Baltimore Aircoil Company, Inc；
    IPC主号:
    专利说明:

    BACKGROUND OF THE INVENTION
    [001] The present invention generally relates to an improved heat exchange apparatus, such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, thermal storage system, air cooler or air heater. More specifically, the present invention relates to a combination or combinations of evaporative heat exchange sections, indirect and direct, or components arranged to obtain improved capacity and performance.
    [002] The invention includes the use of a serpentine type heat exchanger as an indirect heat exchange section. Such an indirect heat exchange section can be combined with a direct heat exchange section, which is usually composed of a filling section, over which an evaporating liquid, such as water, is transferred, usually in a draining operation. down. Such a combined indirect heat exchange section and such a direct heat exchange section together provide improved performance as a global heat exchange apparatus, such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, cooler air heater or air heater.
    [003] Part of the improved performance of the indirect heat exchange section comprising a serpentine type heat exchanger is the ability of the indirect heat exchange section to provide both sensitive heat exchange and latent heat exchange with the evaporating liquid , which is passed or otherwise transported down over and through the indirect heat exchange section. Such indirect heat exchangers are usually composed of a series of serpentine tube paths, with each tube path providing a serpentine circuit. The improved performance of such indirect heat exchangers is obtained by opening the spacing between tube paths, usually horizontal, in one or more of the serpentine coil return curves. Such open spacing in the serpentine coil return curves creates a more efficient cooling zone for the evaporating liquid flowing down over the serpentine coils.
    [004] Various combinations of the heat exchange arrangements are possible according to the present invention. Such arrangements could include an arrangement having an indirect heat exchange section with increased vertical spacing in the series of serpentine tube paths, formed by increased height return curves. In such an arrangement, an evaporation liquid seeps downwards onto and through the indirect heat exchange section with such an evaporation liquid, which is usually water, then leaving the indirect section to be collected in a tank and then pumped upwards to be distributed back down over the indirect heat exchange section. In this reverse flow arrangement, modalities work more efficiently with generally lower spray rates, on the order of 2 - 4 GPM / sq.ft. In other arrangements shown, design spray flow rates may be higher.
    [005] In another arrangement, a combined heat exchanger is provided with an indirect heat exchange section, consisting of serpentine tube paths, over which evaporation liquid is distributed downwards over and through the exchange section Such an indirect heat exchange section is made up of serpentine tube paths, having an increased spacing between one or more height return curves. In addition, a direct heat exchange section composed of filler can be positioned in one or more of the areas of increased vertical spacing, formed by the return curves of the serpentine coil. In this arrangement, the modalities work more efficiently with generally lower spray flow rates, in the order of 2 - 4 GPM / sq.ft. Thus, not only are the modalities presented here more efficient, providing high heat rejection, but they also perform this with less energy requirement for the spray water pump. In other arrangements shown, design spray flow rates may be higher.
    [006] In addition, it is also part of the present invention to provide a second spray water distribution arrangement, intermediate, by which the evaporation liquid is distributed downward over the indirect heat exchange sections and, if present, the exchange sections of direct heat, at a point below the top section of the indirect heat exchange section for this arrangement, there are several different modes of operation, which further improve the heat transfer capabilities and the benefits for the customer. In one operating mode, both the upper and intermediate spray sections are active and water spraying over the indirect and direct sections is present. In another operating mode, the intermediate spray section is not active and the upper spray arrangement provides the evaporation liquid for the entire set. In yet another mode of operation, the upper spray section is not active and the intermediate spray section is active, which can provide evaporative cooling for the lower coil section, while providing cooling dry sensitive for the upper dry coil section. In yet another mode of operation, the upper spray section is not active, the intermediate spray section is active, there is selectively no heat transfer from the lower coil section, underneath the intermediate spray section, allowing air flowing upwards it becomes adiabatically saturated through the direct section, if present, before transferring sensitive heat with the top portion of the coil above the intermediate spray section. This latter mode of operation further reduces the amount of water use, while providing lower temperature air to provide sensitive cooling to the upper portion of the coil above the intermediate spray arrangement.
    [007] The heat exchanger or fluid cooler apparatus of the present invention could be operated, in which both air and an evaporating liquid, such as water, are drawn or supplied either through the indirect heat exchange section or the exchange section direct heat, if present. It may be desirable to operate the heat exchanger without a supply of the evaporating liquid, where air would only be drawn through the indirect heat exchange section and through the direct heat exchange section, if present. It is also possible to operate a combined heat exchanger according to the present invention, in which only evaporation liquid would be supplied through or down through the indirect heat exchange section and the direct heat exchange section, if present, and in that air would not be drawn by typical means, such as a fan.
    [008] In the operation of an indirect heat exchange section, a stream of fluid passing through the coil coils is cooled, heated, condensed, or evaporated in either or both of a sensitive heat exchange operation and heat exchange operation latent by the passage of an evaporating liquid, such as water, together with air over the coil coils of the indirect heat exchange section. Such combined heat exchange results in a more efficient operation of the indirect heat exchange section, as it results in the presence of increased spacing, formed in one or more of the return curves of the serpentine tube paths, of the indirect heat exchange section. . Greater efficiency in operation can also be achieved by providing a second or intermediate spray distribution system to provide evaporation liquid to flow down over and through the coils of the indirect heat exchange section. The evaporation liquid, which again is usually water, which generally passes down through the indirect heat exchange section and generally down through the direct heat exchange section, which is typically a filling assembly, if such a section Direct heat exchange is provided in the increased vertical spacing in one or more of the increased height return curves of the coil coils of the indirect heat exchange section. Heat in the evaporation liquid is passed to the air, which is usually drawn down or up through the indirect heat exchange section and out from the closed circuit fluid cooler or heat exchanger assembly through a system. air movement, such as a fan. The evaporation liquid draining from the direct or indirect heat exchange section is typically collected in a tank and then pumped upward for redistribution through the direct or indirect evaporation heat exchange section.
    [009] The type of fan system, whether of induced or forced current, belt drive, gear drive or direct drive can be used with all of the presented modes. The type of fan, either axial, centrifugal or otherwise, can be used with all of the modes shown. The type of tubes, tube material, tube diameters, tube shape, or with fins or without fins, the number of tube passes, number of return curves, number of increased vertical spaces, can be used with all the modalities presented.
    [0010] Still, the coil can consist of tubes or it can be a type of plate fin or it can be any type of plates in any material that can be used with all the modalities presented here. The type of filler, or efficient reverse flow filler, contaminated water application fillers or any material filler can be used with all of the presented modalities.
    [0011] Consequently, it is an objective of the present invention to provide an improved heat exchange apparatus, which could be a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, which includes an indirect heat exchange section with increased spacing formed in one or more return curves of the serpentine tube forming the indirect heat exchange section.
    [0012] It is another objective of the present invention to provide an improved heat exchange apparatus, such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, including a section of indirect heat exchange comprising a series of serpentine tube paths, with increased vertical spacing between one or more of the tube paths, and with a direct heat exchange, positioned in one or more of the areas of the increased vertical spacing.
    [0013] It is another objective of the invention to provide an improved heat exchange apparatus, comprising an indirect heat exchange section composed of coil coils with both a primary evaporation liquid distribution system at, or close to, the upper part of the coil coils and a secondary liquid distribution and evaporation system, positioned below the top of the coil coils. In addition, the primary and secondary evaporation liquid distribution systems can be selectively operated so that water can be preserved.
    [0014] It is another object of the present invention to provide an improved evaporative heat exchange apparatus, such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, including at least at least two indirect heat exchange sections, which comprise a series of serpentine tube paths, with increased vertical spacing between one or more tube paths, and with a direct heat exchange, positioned in one or more of the vertical spacing areas increased between tube paths.
    [0015] It is another object of the present invention to provide an improved evaporative heat exchange apparatus, such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, including at least two indirect heat exchange sections, separated by increased vertical spacing with an optional direct heat exchange, positioned in the increased vertical space between indirect heat exchange sections.
    [0016] It is another objective of the present invention to provide an improved evaporative heat exchange apparatus, such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, in which the direct heat exchange sections, positioned in one or more of the areas of the increased vertical spacing between pipe paths or alternatively positioned between the increased vertical space between indirect heat exchange sections are easily accessible and replaceable for service. SUMMARY OF THE INVENTION
    [0017] The present invention provides an improved heat exchange apparatus, which typically consists of an indirect heat exchange section. The indirect heat exchange section provides improved performance by using a serpentine coil arrangement, composed of tube path sections and return curves, with a means of increasing the distance between one or more of the tube paths, of the coil coils. One way to achieve this vertical separation between the tube paths, usually horizontal or inclined, is to by increasing one or more of the return curve radii in the return curves of the serpentine tube paths, in a serpentine coil. Another way to achieve this vertical separation between generally horizontal or inclined pipe paths is to install an intentional vertical spacing between two or more coil coils or other indirect heat exchange sections, such as heat exchanger plates. The tube path sections of a coil arrangement can generally be horizontal and can be slanted downward from the inlet end of the coils towards the outlet end of the coils to improve the flow of fluid current through the same. Such coil coils are designed to allow a fluid stream to be passed through, exposing the fluid stream indirectly to air or an evaporating liquid, such as water, or a combination of air and an evaporating liquid, to provide both sensitive heat exchange and latent heat exchange from the external surfaces of the coils of the indirect heat exchanger coils. Such use of an indirect heat exchanger in the closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater of the present invention provides improved performance and also allows for combined or alternative operation, where only air or just an evaporation liquid or a combination of the two can be passed through, or through the outside of, the coil coils of the indirect heat exchanger.
    [0018] A direct heat exchange section or sections can generally be positioned within the indirect heat exchange section in the vertical spacing between the increased height return curves of the tube paths, usually horizontal, of the serpentine coil. the evaporation liquid is allowed to pass through and through the indirect and direct sections comprising the heat exchange section. Heat is extracted from such an evaporating liquid by an air passage through or through the direct and indirect heat exchange sections by an air movement apparatus, such as a fan. Such evaporation liquid is collected in a deposit at the base of the closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater and pumped back into the distribution, usually down, through or through of the indirect heat exchange section. In addition, a secondary evaporating liquid distribution system can be positioned under the top of the indirect coil coils within the indirect heat exchange section or between two indirect sections in the vertical spacing and selectively operated with the evaporating liquid distribution system. primary, so water can be conserved. BRIEF DESCRIPTION OF THE DRAWINGS
    [0019] In the drawings, figure 1 is a side view of an indirect heat exchanger of the prior art, including a series of serpentine tube paths;
    [0020] Figure 2 is a side view of an indirect heat exchanger of the prior art coil of serpentine;
    [0021] Figure 3 is a side view of a first embodiment of an indirect heat exchanger with a series of thin serpentine tube paths, according to the present invention;
    [0022] Figure 4 is a side view of a second embodiment of an indirect heat exchanger with a series of serpentine tube paths, according to the present invention;
    [0023] Figure 5 is a side view of a third embodiment of an indirect heat exchanger with secondary evaporation liquid distribution according to the present invention;
    [0024] Figure 6 is a side view of a fourth modality of an indirect heat exchanger with direct heat exchange sections according to the present invention;
    [0025] Figure 7 is a perspective view of the fourth embodiment of a closed circuit cooling tower with an indirect heat exchange section with direct heat exchange sections in accordance with the present invention;
    [0026] Figure 8 is a side view of a fifth embodiment of two sections of indirect heat exchanger with five sections of direct heat exchange according to the present invention;
    [0027] Figure 9 is a side view of a sixth modality of two indirect heat exchangers with a section of direct heat exchange according to the present invention;
    [0028] Figure 10 is an end view of a seventh modality of two indirect heat exchangers with direct heat exchange sections in accordance with the present invention;
    [0029] Figure 11 is a side view of an eighth modality of two indirect heat exchangers with direct heat exchange sections and secondary evaporation liquid distribution according to the present invention;
    [0030] Figure 12 is a side view of a ninth modality for two plate-style indirect heat exchangers, with two direct heat exchange sections according to the present invention;
    [0031] Figure 13 is a graph of performance of heat exchangers, constructed in accordance with the present invention.
    [0032] Figure 14 is an end view of an embodiment of an indirect heat exchanger with direct heat exchange sections in accordance with the present invention;
    [0033] Figure 15 is an end view of plate-style indirect heat exchangers with direct heat exchange sections in accordance with the present invention; DESCRIPTION OF THE PREFERRED EMBODIMENT
    [0034] Referring now to figure 1, a serpentine product 10, evaporatively cooled, of the prior art, which could be a closed circuit cooling tower or an evaporation condenser. Both of these products are well known and can operate wet form in evaporation mode or can operate with the spray pump 12 off, when ambient conditions or lower loads allow. Pump 12 receives the coldest sprayed fluid, evaporated cooled, usually water, from the cold water tank 11 and pumps it to the spray water head 19, where water is expelled from the nozzles or holes 17 to distribute water over the coil 14. The spray water head 19 and the nozzles 17 serve to distribute the water evenly over the top of the coil (s) 14. As the cooler water is distributed over the top of the serpentine 14, motor 21 rotates fan 22, which induces or draws ambient air inwards through inlet shutters 13, upwards through serpentine 14, then through stream eliminators 20, which serve to prevent the stream from leaving the unit, and then the heated air is blown into the room. Air generally flows in a flow direction contrary to falling spray water. Although figure 1 and all subsequent figures are shown with the axial fan 22 inducing or pulling air through the unit, the current fan system can be a fan system of any style, which moves air through the unit, including, but not limited to, not limited to, induced current and forced current. Additionally, the motor 21 can be a belt drive, as shown, gear drive or directly connected to the fan. It should be understood that, in all of the modalities presented, there are many circuits in parallel with pipe paths, but only the outer circuit is shown for clarity. Serpentine 14 is shown with an inlet tank 15 and outlet tank 16, which connect to all of the serpentine tubes having normal height return curve sections 18.It should also be understood that the number of circuits within the serpentine coil it is not a limitation of the modalities presented. Referring now to figure 2, the prior art coil 30 has inlet and outlet tank 37 and 31, respectively, is supported by coil clips 32 and 38 with central support 41. There are two circuits that come from the inlet tank, shown as tube paths, generally horizontal, 39 and 40. Coil 30 is constructed with small radius or normal return curves 36 with a small slope to allow proper drainage. In some prior art coils, this inclination of tube paths, generally horizontal, may vary with the last set of tube paths, at the base, having a greater inclination. The spacing 35 between pipe paths, on the left side 235, can be seen as approximately zero and consequently allows very little interaction between the falling spray water and generally the air flowing backwards before the spray water hits the next one. set of tube paths. Similarly, the largest space 33 and 34 between pipe paths, usually horizontal, is seen as slightly larger, but there is still insufficient interaction between the falling spray water and generally the air flowing backwards before the spray water crashes against the next set of tube paths, compared to the modalities presented here. In addition, there is not enough space in the interstices 33, 34 or 35 to install a direct heat exchange section, such as reverse flow filling, or to install an intermediate spray system to further increase the cooling of the spray water, as in the modalities presented here.
    [0035] With reference to figure 3, a cooling tower according to the first embodiment of the invention is shown in 70, with the coldest spray water being pumped from the cold water tank 71 by pump 72 for the arrangement of spray head 79 with nozzles or orifices 78 to distribute water evenly over coil 75. Motor 81 operates fan 82 to induce air first through inlet shutters 73, generally up through coil 75, then through eliminators 80 , then unloading it into the environment. The first modality of coil 75 has an alternating combination of narrow return curves 76 and large radius return curve 83 on serpentine coil 75. The substantially wide return curve 83 forms a spray water cooling zone 74, in which spray water is additionally cooled by air flowing upwards before contacting the next set of pipe paths, having normal or narrow return curves 76. In this embodiment, coil 75 has four sets of three rows of narrow curve radius or normal 76, separated by three intentionally large return curves 83, forming three large spray water cooling zones 74 within coil assembly 75. Coil 75 is shown with inlet tank 77 and outlet tank 84, which connect all streamer tubes. It should be noted in this and all other embodiments that inlet tank 77 and outflow tank 84 can be reversed, depending on the particular application and is not a limitation of the invention. The first modality is shown with tube paths, usually horizontal, with a slight pitch or inclination from one end to the other to allow the coils to drain better and help the condensers, so that the liquid condensate can be drained from easier way. It should be noted that, for simplicity, all other modalities are shown without a tube pass, but it must be understood, that tubes can be inclined or not. The first modality shows twelve tube paths, usually horizontal, or, as they are commonly called, passes; however, other embodiments can employ any number of tube paths, or passes, and are not a limitation of the invention. Once when the spray water 265 leaves the base of the coil 75, there is additional cooling of the spray water before the spray water cascades down into the cold water basin 71. Substantial space 74 between rows of curve tubes narrow return 76 allows the spray water droplets to be cooled by the air flowing in reverse before capturing more heat from the next set of pipe paths. The height of the spray water cooling zone 74 must be at least 2.54 cm (one inch). Users in the art will recognize that the number of tube paths or passes, the number of spray water cooling zones 74, and the height of the spray water cooling zone 74 can be optimized to achieve the desired performance and overall height of the spray. modality 70. Furthermore, the tubes can be of any diameter or shape and are not a limitation of the invention.
    [0036] With reference now to figure 4, a cooling tower according to a second mode 130 is shown. Components in second mode 130 including cold water bowl 131, pump 132, inlet shutters 133, spray arrangement 140 nozzles or orifices 139, inlet tank 138, outlet tank 144, current eliminators 141, motor 142 and fan 143, are shown to be identical and function in the same way as those shown in the first mode, serpentine 134 in the second mode has been altered to illustrate the variation that users in the art can make to optimize performance and height. In serpentine 134 there are still twelve pipe paths, generally horizontal, as in the first modality, but serpentine 134 now has six sets of two narrow or normal return curve pipe paths, separated by five large spray water cooling zones 136 formed by large return curves 135. It should be noted that the pipe paths in coil 134 are shown as horizontal, for clarity, but can be inclined or oblique, as shown in the first embodiment. In this in all other modalities, the tube paths, usually horizontal, are shown as horizontal, for clarity, but they can be oblique or inclined. The second modality shows a variation in the first modality and it should be noted that the number of pipe runs, between large spray water cooling zones, the number of large spray water cooling zones, number of total pipe runs, the height of the large spray water cooling zones can also be varied to optimize the performance and height of the unit.
    [0037] With reference to figure 5, a cooling tower according to a third modality is shown in 180. The components in the third modality 180 including the cold water basin 181, pump 182, inlet blinds 183, primary spray arrangement 194, the nozzles or holes 192, inlet tank 191, outlet tank 198, current eliminators 195, motor 116 and fan 197, all work in the same way as those shown in the first embodiment. Serpentine 189 has normal height return curves 190 and increased height return curves 184A. Within the large spray water cooling zone 184, the third mode 180 also contains the secondary or intermediate spray tank 187 with the nozzles or holes 185 to uniformly spray coil 189 with additional spray water, stream eliminators 188, and selectively operated valves 193 and 186. It should be noted that, instead of valves 193 and 186, two spray pumps can be used to perform the same modes of operation. It should also be noted that the two large spray water cooling zones 184, shown, formed by large 184 A return curves, can also have a direct section, if desired. There are four main modes of operation with mode 3. The first mode of operation is with the spray pump 182 on, with valves 186 and 193 open, water is sprayed over the top of serpentine 189 and also inside serpentine 189. The spray flow variation and greater full spray flow in the base section of coil 189 causes the unit 180 to operate more efficiently. During mode one, the fan can operate at any desired speed or can be turned off. For the second mode of operation, valve 193 can be closed, allowing only spray water to flow over the base section of coil 189. In this mode hybrid, the bottom part of coil 189 operates in evaporative cooled mode, while the top section of coil 189 above stream eliminators 188 operates dry. This mode of operation can serve to save water and also reduce the water column if During mode two, the fan can operate at any desired speed 310 or can be turned off. The third mode of operation can be by turning off the spray pump 182, so that only sensitive cooling of the coil 189 is carried out.
    [0038] With reference now to figure 6, a cooling tower according to a fourth mode is shown in 210. The components in the fourth mode 210 including the cold water bowl 211, pump 212, inlet blinds 213, spray arrangement 221. The nozzles or holes 220, inlet tank 219, outlet tank 225, current eliminators 222, motor 223 and fan 224, work in the same way as that presented in the first mode. Note that there are alternating normal or narrow return curves 218 and then larger return curves 217 forming the large spray water cooling zone 214 on coil 216. In this preferred embodiment there is at least one direct heat exchange section. direct heat exchange 215 can be a countercurrent fill, which is installed within the large spray water cooling zone 214. direct section 215 increases the efficiency of the spray water cooling within the large spray water cooling section 214. In this modality, there are repetition sets of four tube paths, or passes, with narrow radius or normal return curves 218, each following three large radius curves 217 forming three large spray water cooling zones 214 for exist within the constraints of the streamer. In this case, up to three direct sections can be used, if desired, and as shown. The efficiency obtained in cooling the spray water between the tubes 214 far exceeded the loss of air flow from the added direct sections or filling decks to the apparatus 210. The type of direct section can be counter current filling, filling contaminated water or any substrate that increases the spray water surface area within the large spray water cooling zone. In serpentine 216, there are still twelve 330 pipe paths, generally horizontal, as in the first modality, but serpentine 216 now has four sets of three narrow return curve pipe paths 218, separated by three large spray water cooling zones 214. It should be noted that the pipe paths in coil 216 are shown as horizontal, for clarity, but can be tilted or oblique, as shown in the first embodiment. It should be noted that the number of pipe runs between large spray water cooling zones, the number of large spray water cooling zones, the number of total pipe runs, the height of the large water cooling zone spraying can all be varied to optimize performance and unit height. In addition, it should be noted that any means can be used to support the direct sections within the large spray water cooling zones on the indirect coil 216 within the spray water cooling zone 214. One such support means would be to support the direct section 215 on the indirect pipe paths in the coil 216. Another such method would be for the direct section 340 to be placed on top of small bars that are installed in the pipe paths of the indirect section 216, so that the direct section does not directly contacts the indirect section. Another such method would be for the direct section to be supported by a frame structure so that the direct section does not come into direct contact with the indirect section. Figure 7 is a perspective view of a cooling tower 280 according to the fourth embodiment. More specifically, the cross-sectional views show that direct sections 285 can be easily removed for cleaning and replacement by opening or removing panels 284. Removing panels 284 allows access to also clean the indirect heat exchanger 283. It should be noted that panels 284 could be connected to selectively open partially during operation to act as fresh air inlets. In mode 280, indirect coil 283 is shown with panels 284 removed, for clarity, where the large spray water cooling zones are positioned. A means to support the direct sections within the large spray water cooling zones on the indirect coil 283 may be the direct section 285 resting on the indirect section, or sitting on small bars that are installed on top of the indirect section 283 or any means for suspending the direct section without touching the indirect section, if desired. The means for installing the direct section within the large spray cooling zone is not a limitation. The spray water inlet 287 serves to distribute the spray water evenly to the top of the coil 283. The air inlet 282 is shown without the inlet shutters installed, so that the inside of the cold water basin 281 can be View. The inlet of coil 286 and the outlet of coil 289 are shown for connection to the incoming fluid to be cooled or condensed. The fan shaft 288 is connected to the fan and motor (shown) and the fan system draws air through the air inlet 282 through indirect coil 283 and the direct sections 285 through the current eliminators (not shown) and then generally to top to the environment.
    [0039] With reference now to figure 8, a cooling tower according to a fifth mode is shown in 250. The components in the fifth mode 250, including the cold water basin 251, the pump 252, inlet blinds 253, arrangement spray nozzles 265, nozzles or orifices 264, inlet tank 263, outlet tank 275, current eliminators 266, motor 267 and fan 268 operate in the same way as that shown in the first mode. The fifth embodiment 250 uses at least two separate coils 261 and 256. Coil 261 has inlet and outlet tanks 263 and 275, respectively, while serpentine 256 has inlet and outlet tanks 258 and 276, respectively. Coil 261 and coil 256 can be channeled in a series or in 370 a parallel arrangement, when desired. Coil 261 and coil 256 are shown with three sets of two pipe paths, with narrow return curve 262 and 257, and both with two large spray water cooling zones 260 and 255, formed by large return curves 260A and 255A, respectively. It should be noted that coils 261 and 256 are separated by a large spray water cooling zone 272 and this zone optionally has a direct heat exchanger 270 installed inside it. It should be understood that, in all large spray water cooling zones 260, 272 and 255, users in the art may have empty space, an intermediate spray arrangement or direct heat exchange 259, 270 and 254, respectively, installed as shown. It should be understood that the main feature in modality 250 is that it uses more than one coil compared to the previous modalities, which can be used for other optimization and manufacturing reasons 380.
    [0040] Referring now to figure 9, a cooling tower according to the sixth mode is shown at 300. The components in the sixth mode, including the 301 cold water basin, 302 pump, 303 inlet shutters, spray arrangement 312, the nozzles or holes 311, eliminators 313, the motor 314 and the fan 315 work in the same way as that presented in the first modality. The sixth modality 300 also uses at least two separate indirect heat exchange coils, as shown with 308 and 304 having inlet deposits 310 and 306, respectively, and outlet deposits 317 and 318, respectively. Coil 308 and coil 304 can be channeled in a series or in a parallel arrangement or even with different fluids, as is well known in the art. Coil 308 and coil 304 are shown with six sets of two pipe paths, with normal or narrow return curves 309 and 305, respectively, and both coils do not have a large spray water cooling zone within them. However, coils 308 and 304 are separated by a large spray water cooling zone 316 and this zone optionally has a direct heat exchanger 307 installed inside it. It should be understood that in all large spray water cooling zones 316 there may be empty space for additional spray water cooling, an intermediate spray arrangement or direct heat exchange, installed, shown as 307. Both modes 250 and 300 have at least two indirect heat exchangers. It should be understood that mode 250 uses more than one indirect heat exchanger or coil and that each coil has a large spray water cooling zone inside the coil, while mode 300 has at least two indirect heat exchangers without large zones of spray water inside the coil, but the vertical separation between coils forms the large spray water cooling zone. It should be noted that any number of pipe runs, per coil section, can be used, any number of indirect coil sections can be used and any height of the spray water cooling zone between the indirect coil section can be used not it is a limitation to the invention. One of the coils shown in modality 300 can also be made with large spray water cooling zones inside the coils.
    [0041] With reference now to figure 10, a cooling tower according to the seventh modality is presented in 330. This modality has all the same characteristics as the predicted figures, but it should be noted that the modality has been rotated to show the wall divider 332 and pump 333 more clearly. In this embodiment, there are substantially wide return curves 346 forming a spray water cooling zone 347, where the spray water is additionally cooled by the air generally flowing upwards before contacting the next set of pipe paths, having return curves normal or narrow 345. In this embodiment there are four sets of three rows of narrow radius return curves 345, separated by three intentionally large return curves 346 forming three large spray water cooling zones 338 410 within coil sets 336 and 345. In this water-saving modality, left coil 335 and right coil 344 can be bare tubes of any tube diameter or any tube shape, be spiral finned, finned plate or be plate coils. The coils 335 and 344 can be operated both in a wet way with pumps 333 and 343, both connected, and a coil can be operated in a wet way and a dry operation by having, for example, pump 333 on and pump 343 off, or both coils 335 and 344 can be operated dry by having pumps 333 and 343 turned off. Note that wall 332 prevents water and air from migrating from side to side during operation. It should be noted that the number of sets of rows of narrow radius and large radius curves forming the spray water cooling zones is not a limitation of the invention.
    [0042] With reference now to figure 11, a cooling tower according to an eighth mode is 420 shown in 390. The components in the eighth mode, including the cold water basin 391, pump 392, inlet shutters 393, upper spray 410, nozzles or orifices 408, inlet tank 407, outlet tank 416, current eliminators 41 1, motor 412 and fan 413 work in the same way as that presented in the first mode. The eighth mode 390 contains two sections of indirect heat exchange. The indirect upper section 405 has inlet or outlet deposits 407 and 416, respectively, extended surface area fins 415, and can be seen with normal or narrow return curves 406 and also return curves of large radius 403, which form the large spray water cooling zone 404. It should be noted that the two large spray water cooling zones 404, shown on top coil 405, may also have a direct section, such as 394, installed, if desired. The lower indirect section 396 has inlet and outlet deposits 398 and 417, respectively, and also normal or narrow return curves 397 and large return curves forming a large spray water cooling zone 395. The eighth mode 390 also contains the secondary or intermediate spray tank 401 with nozzles or orifices 399 to uniformly spray coil 396 with spray water, current eliminators 402, and selectively operated valves 409 and 400. It should be noted that, instead of 409 and 400 valves, two spray pumps can be used to perform the same modes of operation. In this eighth hybrid mode, there are five modes of operation. The first mode of operation is with a spray pump 392 on, with valves 409 and 400 both open and water is sprayed over the top of coil 405 and also over coil 396. During mode one, the fan can operate in any desired speed or can be turned off. For the second mode of operation, pump 392 is turned on and valve 409 is opened and valve 400 is closed. This allows less energy from the spray pump to be consumed and slightly less unit capacity when desired. During mode two, the fan can operate at any desired speed or can be turned off. For the third mode of operation, valve 409 is closed and valve 400 is opened, allowing only spray water to flow over indirect bottom coil 396. In this hybrid mode, bottom coil 396 operates in evaporatively cooled mode, while coil upper 405 above the current eliminators 402 operates dry. This mode of operation can serve to save water, reduce the water column or be used to desuperheat, if desired. During mode three, the fan can operate at any desired speed or it can be turned off. In a fourth operating mode, valve 409 is closed and valve 400 is opened again, allowing only spray water to flow over bottom coil 396, but this time the heat transfer to coil 396 is switched off so that no there is no heat transfer between the pipe paths, coil 396 and spray water. Now, the spray water together with the direct section 394 operates to cool adiabatically the air that has entered the 393 inlet shutters to have the dry bulb temperature of the proposed wet bulb air temperature. In this way, the upper operating coil section 405 can operate in a sensitive dry cooling mode, while consuming much less water. During mode four, the fan can operate at any desired speed or can be turned off. The fifth mode of operation is with the spray pump 392 off and the unit operates in dry mode to sensibly cool the indirect heat exchangers 405 and 396.
    [0043] With reference now to figure 12, a closed circuit cooling tower or condenser according to a fifth modality is shown in 470. The components in the ninth modality, including the cold water basin 471, pump 472, inlet shutters 473, inlet tank 477, outlet tank 476, upper spray arrangement 482, nozzles or orifices 481, current eliminators 483, motor 484 and fan 485, work in the same way as that presented in the first mode. The ninth modality 470 uses at least two separate heat exchangers, of the indirect heat exchange plate style, shown as 487 and 488. The plate coil 487 and the plate coil 488 can be channeled in a series or in an arrangement parallel, as is well known in the art. Plate coil 487 has inlet and outlet tanks 477 and 476, respectively, while plate coil 488 has inlet and outlet tanks 490 and 491, respectively. The plate coil 487 and 488 are each shown with approximately forty-eight sets of parallel plates 480 or cassettes, in which there are internal passages, in which the heat transfer fluid to be cooled or condensed moves and also open channels external between the sealed plates, where the evaporation fluid, usually water, generally flows downwards and the air flow generally flows upwards in countercurrent. Plate coil heat exchangers 487 and 488 are separated by a large spray water cooling zone 479 and this zone optionally has a direct heat exchanger 478 installed inside it. Below the plate coil 488, there is another large spray water cooling zone 475 and optionally has a direct heat exchange section 474 within it. It should be understood that all large spray water cooling zones 479 and 475 may have empty space for additional spray water cooling, an intermediate spray arrangement or installed direct heat exchange. It should be understood that the plate coils 487 and 488 do not have large spray water cooling zones 475 within them, but the plate coils are separated by large spray water cooling zones. It should be noted that any number of plates, plate style, plate material, plate size, plate pattern and plate height, can be used and is not a limitation of the invention. It should also be noted that any height of the spray water cooling zones, greater than 2.54 cm (one inch), may exist and are not limitations of the invention.
    [0044] Figure 13 is a graph showing data from the prior art unit shown in figure 1 and the heat exchanger perfected in the fourth modality using indirect and direct sections. Specifically, the process fluid is represented both in the prior art modality and in the fourth modality by the upper solid line (curve PF TempTest) showing the closed circuit cooling tower, cooled the indirect serpentine fluid, in this case water, from 100 F to 88 F. It should be noted that in the prior art coil test, the upper dotted line shows the spray water temperature at the top and bottom of the coil being approximately 86F, while the maximum spray water temperature that has been reached it's about 91F. However, note that with the test data for the fourth spray water temperature modality, represented by the scrambled solid line, the spray water temperature at the top and bottom of the indirect coil section was 84F and the maximum temperature of spray water was 93F. The improvement of the large spray water cooling zones can be seen when the spray water temperatures are so much colder, exhibiting the ability to absorb more heat from the indirect pipe paths, yet, above all, the spray temperature was colder, as noted by the scrambled lines. The bottom two lines are the inlet and outlet wet bulb temperatures. The bottom dotted line is from the prior art serpentine test showing the wet bulb that entered 78F and left the unit at 89F. The bottom solid line shows the inlet and outlet temperatures of the wet bulb from the test data of the fourth modality. Note that, again, the wet bulb inlet temperature was 78F, yet the wet bulb output is higher than the prior art data dropping out at 94F. This increase in wet bulb output temperature shows the increased performance in identical power consumption of the operation test unit (engines from both tests were both at 30HP). In the test data of the fourth modality, because the spray water temperature profile is pushed up and the wet air bulb line (WB coil & Fill) is also pushed up, this allows the air to have a greater increase in enthalpy . Thus, by adding direct sections to a prior art indirect coil product only, the efficiency gain of having large spray water cooling zones between the pipe paths can be seen as being much more beneficial than a slight one loss in air flow, caused by adding the direct sections. With filling decks sandwiched between the serpentine tubes, the heat rejection efficiency is increased, as the spray water captures more sensitive heat and transfers it to the air both latently and sensitively.
    [0045] With reference now to figure 14, a cooling tower according to a tenth modality is shown in 500. In this modality, the fan motor 510 operates the fan 514 to draw air through the air inlet 503, then through the direct heat exchanger 502, which serves to further cool the spray water by leaving indirect section 508. The spray water is pumped (pump not shown) from the cold water basin 501 upwards through the spray tank tube 513, making it through the spray tank to be uniformly sprayed from the nozzles or holes 512 over the indirect heat exchanger 508. The heated spray water then takes the path of the indirect coil section with optional direct filling installed in the large areas of spray water cooling to the 505 spray tray, which draws all of the spray water and redistributes it evenly from the nozzle or ori holes 504 for the direct filling section 502. The fan motor 516 activates the fan 517 to induce air generally upwards through the air gap 506, upwards through the indirect section 508, through current eliminators 515 and then it is blown for the environment. The air inlet to the indirect section 508 can be of any height, can be on one, two, or three sides and can have air blowing down generally and is not a limitation of the invention. The indirect coil 508 is built with normal or narrow return curves 509, then with larger return curves to create large spray water cooling zones, as in other modalities. In this case, the direct filling sections 507 are installed in the large spray water cooling zones to increase the efficiency of heat transfer within the direct coil section before the spray water leaves the indirect section, to be further cooled. in the direct section 525 below it 502. The indirect heat exchanger coil tank 511 can be the inlet or outlet, depending on the fluid to be used and is not a limitation of the invention. It is important to note that the tenth modality has exactly the indirect coil and the direct filling sections within this serpentine of the fourth modality, installed in a different style unit, to show variations on how users in the art can employ this technology.
    [0046] With reference now to figure 15, a cooling tower according to the eleventh mode is shown in 530. In this mode, the fan motor 540 operates the fan 542 to draw air through the air inlet shutters 533, then through the direct heat exchanger 532, which serves to cool the spray water even further, leaving indirect section 548. Air also enters the upper part of indirect section 548 at 549, generally moves down through indirect section 548, then through stream eliminators 536 and out of fan 542. Spray water is pumped (pump not shown) from cold water bowl 531 up through spray tank 543 into spray tank 547 to be evenly sprayed from the nozzles or holes 541 on the indirect heat exchanger 548. The indirect heat exchanger 548 is constructed with plate coils 535, as shown in the ninth modal age, but it can also be as shown in the tenth modality and is not a limitation of the invention. In this embodiment, there are at least two indirect heat exchanges, separated by a large vertical water cooling zone 538 and the direct fill section 539 is installed in the large spray water cooling zones to increase the efficiency of heat transfer within of the indirect coil section before the spray water leaves the indirect section to be further cooled in the direct section below it 532. The indirect heat exchanger coil deposits 537 and 545 534 and the indirect heat exchanger coil deposits 545 and 546 can be channeled in series or parallel and the input and outputs can be in any position that adapts to the application and is not a limitation of the invention. It is important to note that the eleventh modality has the indirect plate coil and the direct filling sections of the ninth modality, installed without the optional direct section, installed under the lower indirect plate coil section for a different style unit to show variations of how users in the art can employ this technology.
    权利要求:
    Claims (20)
    [0001]
    1. Heat exchange method, characterized by the fact that it comprises the steps of: providing a section of indirect evaporation heat exchange, the section of indirect heat exchange conducting a fluid stream within a plurality of paths, the section indirect heat exchange system comprising a top and a base, move air through the indirect section, air moving through the indirect heat exchange section exchanging heat with the fluid stream within the plurality of paths in the indirect heat exchange section , in which the indirect heat exchange section is composed of a series of serpentine tubes comprising sections of path and return curve sections of normal and increased height, the series of serpentine tubes including at least one area having a vertical spacing increased between vertically adjacent path sections of the serpentine tubes, such increased vertical spacing formed by the height height return curve sections, which have a height larger than normal return curve sections, an inlet tank and an outlet tank, operatively connected to the series of serpentine tubes so that the fluid stream can pass into the series of serpentine tubes and out of the series of serpentine tubes.
    [0002]
    2. Heat exchange method according to claim 1, characterized in that a distribution system is provided to distribute an evaporative liquid to a portion of the indirect heat exchange section from a position below the top of the section of indirect heat exchange in the area of the indirect heat exchange section having an increased vertical spacing between vertically adjacent path sections of the serpentine tubes.
    [0003]
    3. Heat exchange method according to claim 1, characterized by the fact that a direct heat exchange section is provided below the distribution system, the direct heat exchange section comprising a filling assembly located in one of the areas in the indirect heat exchange section having increased vertical spacing between vertically adjacent path sections of the serpentine tubes.
    [0004]
    4. Heat exchange method according to claim 1, characterized by the fact that air moves upwards through the indirect heat exchange section.
    [0005]
    5. Heat exchange method according to claim 1, characterized by the fact that air moves through the indirect heat exchange section.
    [0006]
    6. Heat exchange method according to claim 1, characterized in that the increased height of the return curve sections is at least 2.54 cm (one inch).
    [0007]
    7. Heat exchange method according to claim 2, characterized in that it additionally comprises a current eliminator located above the distribution system that distributes liquid over the indirect heat exchange section.
    [0008]
    8. Heat exchange method, characterized by the fact that it comprises the steps of: providing an indirect heat exchange section, the indirect heat exchange section conducting a fluid stream within a plurality of paths, the exchange section of indirect heat comprising a top and a base, distribute an evaporative liquid to the section of indirect heat exchange so that the indirect heat exchange takes place between the fluid stream within the plurality of paths and the evaporative liquid, moving air through the indirect heat exchange section, the air moving through the indirect heat exchange section exchanging heat and mass with the evaporative liquid moving through the indirect heat exchange section and therefore exchanging heat indirectly with the fluid stream within the plurality of paths in the indirect section, in which the indirect heat exchange section is composed of a series of serpentine tubes comprising sections of path and sections of return curve d and normal height and at least one increased return curve section, the increased return curve section providing increased vertical spacing between vertically adjacent sections of the coil coil, an inlet and an outlet tank, operably connected to the series of serpentine tubes so that the fluid stream can pass into the series of serpentine tubes and out of the series of serpentine tubes.
    [0009]
    Heat exchange method according to claim 8, characterized in that air moves upwards through the indirect heat exchange section.
    [0010]
    10. Heat exchange method according to claim 8, characterized by the fact that a section of direct heat exchange is provided in one or more of the areas in the indirect heat exchange sections having increased vertical spacing between path sections vertically adjacent to the series of serpentine tubes.
    [0011]
    11. Heat exchange method according to claim 8, characterized in that a distribution system is provided to distribute an evaporation liquid through the indirect heat exchange section from a position above the heat exchange section. indirect heat.
    [0012]
    12. Heat exchange method according to claim 8, characterized in that air moves through the indirect heat exchange section.
    [0013]
    13. Heat exchange method according to claim 8, characterized in that the increased height of the return curve sections is at least 2.54 cm (one inch).
    [0014]
    14. Heat exchange method, characterized by the fact that it comprises the steps of: providing an indirect heat exchange section, the indirect heat exchange section conducting a fluid stream within a plurality of paths, the exchange section of indirect heat comprising a top and a base, distribute an evaporative liquid to the section of indirect heat exchange so that the indirect heat exchange takes place between the fluid stream within the plurality of paths and the evaporative liquid, moving air through the indirect heat exchange section, the air moving through the indirect heat exchange section exchanging heat with the evaporative liquid moving through the indirect heat exchange section and therefore exchanging heat indirectly with the fluid stream within the plurality of paths in the indirect section, where the indirect heat exchange section is composed of a series of serpentine tubes comprising sections of path and height return curve sections the normal and increased, the series of serpentine tubes including at least one area having an increased vertical spacing between vertically adjacent path sections of the serpentine coil, the increased vertical spacing formed by the height-height return curve sections, which have a height greater than the normal return curve sections.
    [0015]
    15. Heat exchange method according to claim 14, characterized by the fact that it additionally comprises: collecting all the evaporative liquid that leaves the indirect heat exchange section, and pumping the collected evaporation liquid upwards so that it can be distributed to the indirect heat exchange section.
    [0016]
    16. Heat exchange method according to claim 14, characterized by the fact that a direct heat exchange section is provided in one or more of the areas in the indirect heat exchange sections having increased vertical spacing between vertical travel sections adjacent to the series of serpentine tubes.
    [0017]
    17. Heat exchange method according to claim 14, characterized in that a distribution system is provided to distribute an evaporating liquid through the indirect heat exchange section from a position above the heat exchange section indirect heat.
    [0018]
    18. Heat exchange method according to claim 14, characterized in that a direct heat exchange section is provided, the direct heat exchange section comprising a filling assembly located in one of the areas in the exchange section of indirect heat having an increased vertical spacing between vertically adjacent path sections of the series of serpentine tubes.
    [0019]
    19. Heat exchange method according to claim 14, characterized in that a direct heat exchange section is provided, the direct heat exchange section comprising a filling assembly located below the indirect heat exchange section , and moving air through the direct heat exchange section.
    [0020]
    20. Heat exchange method according to claim 14, characterized by the fact that a current eliminator is provided above the distribution system that distributes liquid over the indirect heat exchange section.
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    同族专利:
    公开号 | 公开日
    AU2016244222A1|2016-11-03|
    AU2016244222B2|2018-03-01|
    KR20150130548A|2015-11-23|
    EP2972038A4|2016-12-07|
    CN105283729B|2018-03-20|
    MX2015013268A|2016-04-04|
    AU2014237750B2|2016-07-14|
    JP2016510869A|2016-04-11|
    US20140264973A1|2014-09-18|
    BR112015023123A2|2017-07-18|
    CA2907121A1|2014-09-25|
    US10443942B2|2019-10-15|
    CN105283729A|2016-01-27|
    US20170284742A1|2017-10-05|
    WO2014149873A1|2014-09-25|
    EP2972038A1|2016-01-20|
    CA2907121C|2019-06-18|
    US9255739B2|2016-02-09|
    AU2014237750A1|2015-11-05|
    JP6270983B2|2018-01-31|
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    法律状态:
    2018-11-13| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|
    2019-12-10| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|
    2020-09-29| B09A| Decision: intention to grant|
    2020-12-22| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 06/03/2014, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US13/833,788|US9255739B2|2013-03-15|2013-03-15|Cooling tower with indirect heat exchanger|
    US13/833,788|2013-03-15|
    PCT/US2014/021300|WO2014149873A1|2013-03-15|2014-03-06|Cooling tower with indirect heat exchanger|
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