TWI586926B - Vapor compression system - Google Patents

Description

Vapor compression system Reference related application

This case claims the US non-provisional application 13/912,634, which was filed on June 7, 2013, and is named as the priority of the vapor compression system.

The present invention is generally directed to a vapor compression system for refrigeration, air conditioning, and chilling liquid systems, and more particularly to a dispensing system and method for a vapor compression system.

Conventional chilled liquid systems are used in heating, ventilation, and air conditioning systems that include an evaporator for generating thermal energy exchange between the coolant of the system and another liquid to be cooled. One form of evaporator includes a housing with a plurality of tubes forming a bundle of tubes for circulating a liquid to be cooled. The coolant is brought into contact with the outer or outer surface of the tube bundle positioned within the housing to form a thermal energy transfer between the liquid to be cooled and the coolant. For example, the coolant can be attached to the outer surface of the tube bundle by spraying or other similar technique commonly referred to as a "falling film" evaporator. In still further examples, the outer surface of the tube bundle may be fully or partially immersed in a liquid coolant commonly referred to as a "filled" evaporator. In yet another example, a portion of the tube bundle can have a coolant attached to the outer surface and another portion of the tube bundle can be immersed in a liquid coolant commonly referred to as a "mixed falling film" evaporator.

As a result of the exchange of heat with the liquid, the coolant is heated and converted to a vapor state, which is then returned to a compressor where it is compressed to begin another coolant cycle. The cooled liquid can be circulated to a plurality of heat exchangers disposed through a building. The warmer gas from the building passes through the heat exchanger where the cooled liquid is warmed and the gas used in the building is cooled. The liquid warmed by the building's gas is returned to the evaporator to repeat this step.

The present invention relates to a dispenser for use in a vapor compression system, comprising a body assembly for placement in a heat exchanger having a plurality of tubular members extending substantially horizontally in the heat exchanger a bundle of tubes. At least one dispensing device is formed at one end of the enclosure to face the bundle of tubes, the at least one dispensing device being configured to apply fluid entering the dispenser to the bundle. The enclosure has an aspect ratio of between about 1/2:1 and about 10:1.

The invention further relates to a dispenser for use in a vapor compression system, comprising a body assembly for placement in a heat exchanger having a plurality of substantially horizontal extensions included in the heat exchanger A bundle of tubes. At least one dispensing device is formed at one end of the enclosure to face the bundle of tubes, the at least one dispensing device being configured to apply fluid entering the dispenser to the bundle. The enclosure has an aspect ratio of between about 1/2:1 and about 10:1. The end of the enclosure includes an end profile and the at least one dispensing device includes at least one opening formed in the end profile. The at least one opening is assembled and disposed to be between about 60 degrees and about 180 degrees The quality encompasses a spray angle dispensing fluid throughout the range of fluid pressures associated with the operation of the dispenser of the system.

More particularly, the present invention relates to a method of dispensing a fluid in a vapor compression system, the method comprising providing a enclosure that is configured to be disposed in a heat exchanger having a bundle of tubes, the bundle being contained in a substantially horizontal level of the heat exchanger Extended multiple fittings. The method includes forming at least one dispensing device disposed in an end of the enclosure to face the bundle of tubes, the at least one dispensing device being configured to apply fluid entering the dispenser to the bundle of tubes. The enclosure has an aspect ratio of between about 1/2:1 and about 10:1. The method includes operating the vapor compression system.

10‧‧‧System

12‧‧‧ buildings

14‧‧‧Vapor Compression System

16‧‧‧Boiler

18‧‧‧ gas return conduit

20‧‧‧ gas supply conduit

22‧‧‧Gas Manager

24‧‧‧ catheter

32‧‧‧Compressor

34‧‧‧Condenser

36‧‧‧Expansion device

38‧‧‧Evaporator

40‧‧‧Control panel

42‧‧‧ Analog Digital (A/D) Converter

44‧‧‧Microprocessor

46‧‧‧Non-volatile memory

48‧‧‧Intermediate panel

50‧‧‧Motor

52‧‧‧ Variable speed drive

54, 78, 140‧‧‧

56‧‧‧Cooling tower

60R‧‧‧Reflow line

60S‧‧‧ supply line

62‧‧‧Cooling load

64‧‧‧Intermediate circuit

66‧‧‧Expansion device

68‧‧‧Entry line

70‧‧‧ middle tube

72, 74, 114‧‧‧ pipeline

76‧‧‧ cylindrical shell

80, 142‧‧‧Distributor

82‧‧‧Liquid coolant

84‧‧‧ pump

86‧‧‧ Cover

92‧‧‧ wall

94‧‧‧Open end

96, 106‧‧‧Vapor coolant

98‧‧‧Extension

100‧‧‧ channel

102‧‧‧Slit hole

104‧‧‧Export

110‧‧‧ coolant

112‧‧‧ adjustment device

116‧‧‧Support

128, 138‧‧ ‧ evaporator

144‧‧‧ enclosure

146‧‧‧Distribution device

End of 148‧‧

150‧‧‧ opposite end

152‧‧‧End

154‧‧‧ opposite ends

156‧‧‧ entrance

158, 258, 358, 458‧‧‧ end morphology

160, 260, 360‧‧‧ openings

162, 178‧‧‧ width

164, 202, 204‧‧ ‧ intervals

166‧‧‧ spray angle

168, 170‧‧‧

172, 174‧‧‧ angular error

176‧‧‧ Height

180‧‧‧symmetric plane

181, 281, 381, 481 ‧ ‧ center point or coincidence point

182, 183, 282, 283, 382, 383, 482, 483‧‧‧ reference lines

184‧‧‧ distal point tangent position/cut point

185, 285, 385, 485 ‧ ‧ reference lines

186, 286, 386, 486 ‧ ‧ distance

187, 287, 387, 487 ‧ ‧ distal end

188, 288, 388, 488 ‧ ‧ distance

189, 289, 389, 489‧‧‧ effective radius or effective radius distance

194, 200‧‧‧ length

196, 198‧ ‧ end

208‧‧‧Distribution fluid

261, 263, 361, 363, 461, 463 ‧ ‧ edge

284, 384, 484 ‧ ‧ cut points

Figure 1 shows an example embodiment for a heating, exhaust and air conditioning system.

Figure 2 shows an isometric view of an exemplary vapor compression system.

An exemplary embodiment of the vapor compression system is schematically illustrated in Figures 3 and 4.

Figure 5A shows an expanded, partially cutaway view of an example evaporator.

Figure 5B shows a top isometric view of the evaporator of Figure 5A.

Fig. 5C shows a cross-sectional view of the evaporator taken along line 5-5 of Fig. 5B.

Figure 6A shows a top isometric view of an example evaporator.

6B and 6C are cross-sectional views of the evaporator taken along line 6-6 of Fig. 6A.

Figure 7 shows a top perspective view of an exemplary embodiment of a surrounding body.

Figure 8 shows a plan view of the enclosure of Figure 7.

Fig. 9 is a partial front elevational view of the enclosure taken along line 9-9 of Fig. 7.

Figure 10 is a cross-sectional view of the enclosure taken along line 10-10 of Figure 9.

Figure 11 is a cross-sectional view showing an exemplary embodiment of the enclosure taken along line 10-10 of Figure 9.

Figure 12 is a cross-sectional view showing still another exemplary embodiment of the enclosure taken along line 10-10 of Figure 9.

Figure 13 is a cross-sectional view showing still another exemplary embodiment of the enclosure taken along line 10-10 of Figure 9.

Figure 14 is a cross-sectional view showing still another exemplary embodiment of the enclosure taken along line 10-10 of Figure 9.

Figure 15 shows an exemplary embodiment of the enclosure.

1 shows an exemplary environment for a heating, ventilation, air conditioning (HVAC) system 10 for a typical commercial use building 12 and incorporating a coolant system. System 10 can include a vapor compression system 14 that can be utilized to cool the coolant of building 12. System 10 can include a boiler 16 for supplying heated liquid that can be used for heating in building 12, and a gas distribution system for circulating gas in building 12. The gas distribution system can also include a gas return conduit 18, a gas supply conduit 20, and a gas manager 22. Gas manager 22 may include a heat exchanger coupled to boiler 16 and vapor compression system 14 by conduit 24. The heat exchanger located in the gas manager 22 can receive heated liquid from the boiler 16 or from a vapor compression system The cooling liquid of 14 depends on the mode of operation of system 10. System 10 shows that each floor of building 12 has a separate gas manager, but it is also understandable that the components can be shared between floors.

2 and 3 illustrate an example of a vapor compression system 14 that can be used in a heating, ventilation, air conditioning (HVAC) system, such as HVAC system 10. The vapor compression system 14 can circulate a coolant through a compressor 32, a condenser 34, an expansion device 36, and a liquid cooler or evaporator 38 that are driven by a motor 50. The vapor compression system 14 can also include a control panel 40 that can include an analog-to-digital (A/D) converter 42, a microprocessor 44, a non-volatile memory 46, and a mediator 48. Examples of fluids that may be used as a coolant in vapor pressure system 14 may be fluorocarbon (HFC) based coolants, for example, R-410A, R-407, R-134a, hydrofluoroolefin (HFO), natural "refrigerant such as ammonia _{(NH 3), R-717} , carbon dioxide (CO _2), R-744, or a hydrocarbon base coolant, water vapor or any other suitable form of coolant. In an exemplary embodiment, vapor compression system 14 may use one or more variable speed drives 52, motors 50, compressors 32, condensers 34, and/or evaporators 38, each.

Motor 50 for use with compressor 32 can be driven by a variable speed drive (VSD) 52 or can be directly driven by an AC or DC power source. In use, the variable speed drive 52 receives alternating current having a particular line fixed voltage and line fixed frequency from an alternating current source and provides a source of variable voltage and frequency to the motor 50. Motor 50 can include any form of electric motor that can be driven by a variable speed drive or directly by an AC or DC power source. For example, the motor 50 can be a switched reluctance motor, an induction motor, An electronically commutated permanent magnet motor, or any other suitable form of motor. In an alternate exemplary embodiment, other drive mechanisms, such as steam or gas turbines or engines, and associated components may be used to drive compressor 32.

Compressor 32 compresses the coolant vapor and delivers the vapor to condenser 34 through a discharge line. Compressor 32 can be a centrifugal compressor, a screw compressor, a reciprocating compressor, a rotary compressor, a swing arm compressor, a scroll compressor, a turbo compressor, or any other suitable compressor. The coolant vapor delivered by the compressor 32 to the condenser 34 transfers thermal energy to a fluid, such as water or gas. The coolant vapor condenses into a coolant liquid in the condenser 34 due to heat transfer with the fluid. The liquid coolant from the condenser 34 flows through the expansion device 36 to the evaporator 38. In the exemplary embodiment shown in FIG. 3, the condenser 34 is of a water-cooled type and includes a bundle 54 connected to a cooling tower 56.

The liquid coolant delivered to the evaporator 38 absorbs thermal energy from another fluid, which may or may not be in the same form as the fluid used in the condenser 34, and undergoes a phase change to a coolant vapor. In an exemplary embodiment shown in FIG. 3, evaporator 38 includes a tube bundle having a supply line 60S and a return line 60R coupled to a cooling load 62. A working fluid, such as water, ethylene glycol, calcium chloride brine, sodium chloride brine or any other suitable fluid, enters evaporator 38 via return line 60R and exits evaporator 38 via supply line 60S. The evaporator 38 cools the temperature of the working fluid in the line. The tube bundle in evaporator 38 can include a plurality of lines and a plurality of tube bundles that exit evaporator 28 and are returned to compressor 32 by a suction line to complete the cycle.

Figure 4 is similar to Figure 3, showing the belt can be fitted to the condenser 34 and expanded A coolant circuit between the devices 36 is provided in an intermediate circuit 64 that provides increased cooling capacity, performance and performance. The intermediate circuit 64 has an inlet line 68 that can be directly or in fluid communication with the condenser 34. As shown, in an exemplary embodiment, the inlet line 68 includes an expansion device 66 located upstream of an intermediate tube 70, and the intermediate tube 70 can be a flash tank, also referred to as a flash intercooler. In another exemplary embodiment, the intermediate tube 70 can be assembled into a heat exchanger or a "surface saving device." In the arrangement of the flash intercooler, a first expansion device 66 operates to reduce the pressure of the liquid received from the condenser 34. During the expansion of the flash intercooler, a portion of the liquid is evaporated. The intermediate tube 70 can be used to separate the vaporized vapor from the liquid received from the condenser. The vaporized liquid can be pumped by compressor 32 through a line 74 to a portion intermediate the suction and discharge or a pressure intermediate the compression. The unvaporized liquid is cooled by the expansion process and concentrated at the bottom of the intermediate tube 70 where it is recovered by a line 72 containing a second expansion device 36 to flow to the evaporator 38.

As is well known to those skilled in the art, in the "surface intercooler" arrangement, the manner of operation is slightly different. The intermediate circuit 64 can operate in a similar manner as previously described, except that as shown in Figure 4, the intermediate circuit 64 receives only a portion of the coolant from the condenser 34 and the remaining coolant is directly processed by the expansion device 36, instead of receiving all The coolant in the condenser 34.

5A-5C illustrate an exemplary embodiment of an evaporator assembled into a "mixed falling film" evaporator. As shown in Figures 5A-5C, an evaporator 138 includes a substantially cylindrical housing 76 with a plurality of The tubular member forms a tube bundle 78 that extends substantially horizontally along the length of the housing 76. At least one support member 116 can be located in the housing The plurality of tubes are supported within the 76 to support the tube bundle 78. A suitable fluid, such as water, ethylene, ethylene glycol or calcium chloride brine, flows through the tube of tube bundle 78. A distributor 80 positioned above the tube bundle 78 distributes, deposits or applies the coolant 110 to the tube of the tube bundle 78 from a number of locations. In an exemplary embodiment, the coolant deposited by the distributor 80 can be a completely liquid coolant, although in another exemplary embodiment, the coolant attached by the dispenser 80 can include a liquid coolant and a vapor coolant. Both.

The liquid coolant flowing around the tube of tube bundle 78 does not change state concentrated at the bottom of housing 76. The concentrated liquid coolant can form a pool or stored liquid coolant 82. The location deposited by the dispenser 80 can include any combination of longitudinal or lateral positions relative to the tube bundle 78. In another exemplary embodiment, the location deposited by the dispenser 80 is not limited to the upper tubular member deposited to the tube bundle 78. The dispenser 80 can include a plurality of nozzles that are supplied by a source of dispersion of the coolant. In one exemplary embodiment, the source of dispersion is a tube connected to a source of coolant, such as a condenser 34. The nozzle includes a spray nozzle but also includes a mechanical opening that can direct or direct coolant to the surface of the tubular member. The nozzle may apply a coolant, such as a spray pattern, in a predetermined pattern such that the upper row of tubes of the tube bundle 78 is covered. The tubes of the tube bundle 78 may be arranged such that the coolant flows around the surface of the tube in the form of a film that is joined to form a drop or, in some cases, a curtain or sheet of liquid coolant located on the surface of the tube bottom. This resulting sheet shape causes the surface of the tube to wet to increase the heat transfer efficiency of fluid flow into the tube of tube bundle 78 and between the surface of the tube of the tube bundle 78.

In the pool of liquid coolant 82, a bundle 140 can be soaked or At least partially immersed to provide additional thermal energy transfer between the coolant and the working fluid to evaporate the pool of liquid coolant 82. In an exemplary embodiment, the tube bundles 78 can be at least partially located above the tube bundle 140 (ie, at least partially overlapping). In an exemplary embodiment, the evaporator 138 cooperates with a dual-round system in which the working fluid to be cooled first flows into the tubular member of the tube bundle 140 and is then directed to flow into the tube bundle 78 in a direction opposite to the flow in the tube bundle 140. Inside the pipe fittings. In the second pass of the dual turn system, the temperature of the fluid flowing in the tube bundle 78 is reduced, thus requiring less heat transfer to the coolant flowing over the surface of the tube bundle 78 to achieve the desired temperature of the working fluid.

It will be appreciated that while a double turn system is described, the first pass cooperates with the tube bundle 140 and the second pass cooperates with the tube bundle 78. Other arrangements are contemplated. For example, evaporator 138 can cooperate with a single-round system in which working fluid flows through both tube bundle 140 and tube bundle 78 in the same direction. Alternatively, the evaporator 138 can be mated to a three-round system in which two passes cooperate with the tube bundle 140 and the remaining one fits with the tube bundle 78, or one round cooperates with the tube bundle 140 and the remaining two passes cooperate with the tube bundle 78. Further, the evaporator 138 can be mated with an alternate two-turn system in which one round cooperates with both the tube bundle 78 and the tube bundle 140, and the second round cooperates with both the tube bundle 78 and the tube bundle 140. In an exemplary embodiment, the tube bundle 78 is at least partially positioned above the tube bundle 140 to separate the tube bundle 78 from the tube bundle 140 with a gap. In yet another exemplary embodiment, the cover 86 covers the tube bundle 78 with an extension toward the gap and abutting the gap. In summary, it is contemplated that any number of rounds per round can be combined with one or both of tube bundle 78 and tube bundle 140.

A surrounding body or cover 86 is disposed on the tube bundle 78 to substantially avoid intersection The cross flow, that is, the vapor coolant or the cross flow of the liquid and vapor coolant 106 between the tubes of the tube bundle 78. The cover 86 is located above the tubular member of the tube bundle 78 and laterally frames the tubular member of the tube bundle 78. The cover 86 includes an upper end 88 located adjacent the upper portion of the housing 76 and the dispenser 80 can be positioned between the cover 86 and the tube bundle 78. In yet another exemplary embodiment, the dispenser 80 can be positioned adjacent to but outside of the cover 86 such that the dispenser 80 is not positioned between the cover 86 and the tube bundle 78. However, although the dispenser 80 is not between the cover 86 and the tube bundle 78, the nozzles of the dispenser 80 are still configured to direct or apply coolant to the surface of the tubular member. The upper end 88 of the cover 86 is configured to substantially avoid the flow of the applied coolant 110 and the partially evaporated coolant, i.e., the liquid and/or vapor coolant 106 flows directly to the outlet 104, instead, the applied coolant 110, 106 It is limited by the cover 86, and more specifically, between the walls 92 before the coolant can exit the open end 94 of the cover 86. The flow of vapor coolant 96 around the cover 86 also includes a coolant that is vaporized by the pool of liquid coolant 82.

It should be understood that at least the foregoing defined and related terms are not to be construed as limiting. For example, the cover 86 can be rotated relative to the other evaporator assemblies previously described, i.e., the cover 86 includes the wall 92 and is not limited to the upright orientation. Based on sufficient rotation of the cover 86 along the axis of the tubular member of a substantially parallel bundle 78, the cover 86 can no longer be considered "above the tubular member of the bundle 78" or "the tubular member that laterally frames the bundle 78". Similarly, the "upper" end 88 of the cover 86 is no longer adjacent an "upper" portion of the housing 76, and other exemplary embodiments between the cover and the housing are not limited to such an arrangement. In an exemplary embodiment, the cover 86 terminates after covering the tube bundle 78, although in another example In the embodiment, the cover 86 extends further after covering the tube bundle 78.

After the cover 86 forces the coolant 106 down between the walls 92 and through the open end 94, the vapor coolant flows through the space between the housing 76 and the wall 92 from the bottom of the housing 76 to the upper portion of the housing 76. Previously, there was a sudden change in direction. In conjunction with the effect of gravity, this sudden change in flow direction causes any water droplets entrained by a proportion of coolant to cool with the liquid coolant 82 or housing 76, thereby removing these water droplets from the flow of vapor coolant 96. In addition, the coolant mist flowing between the walls 92 along the length of the cover 86 combines into larger water droplets to be more easily separated by gravity or to maintain sufficient proximity to or contact with the tube bundle 78 to allow The coolant mist evaporates by heat transfer with the tube bundle. As a result of the increased size of the water droplets, the effectiveness of the liquid by gravity separation improves, allowing the vapor coolant 96 to have an increased upward velocity through the evaporator in the space between the wall 92 and the housing 76. Vapor coolant 96, whether flowing from the open end 94 or the pool of liquid coolant 82, flows through wall 92 to a pair of extensions 98 projecting from upper end 88 and into a passage 100. The vapor coolant 96 enters the passage 100 through a slot 102 in the space between the end of the extension 98 and the housing 76 before exiting an outlet 104 of the evaporator 138. In another exemplary embodiment, vapor coolant 96 may enter passage 100 via an opening or hole formed in extension 98 instead of slot 102. In yet another exemplary embodiment, the slot 102 may be formed by a space between the cover 86 and the housing 76, that is, the cover 86 does not include the extension 98.

In other words, once the coolant 106 is expelled from the cover 86, the vapor coolant 96 then flows from the bottom of the housing 76 along the aforementioned passage path to the top of the housing 76. In an exemplary embodiment, the channel path is at the exit 104 Previously, it may be substantially symmetrical between the surface of the cover 86 and the housing 76. In an exemplary embodiment, a baffle, such as extension 98, is disposed adjacent the evaporator outlet to prevent direct path of vapor coolant 96 to the compressor inlet.

In an exemplary embodiment, the cover 86 includes opposing substantially parallel walls 92. In another exemplary embodiment, the wall 92 can extend substantially longitudinally and terminate at an open end 94 that is substantially opposite the upper end 88. The upper end 88 and the wall 92 are relatively close to the tubular member of the tube bundle 78, while the wall 92 extends toward the bottom of the housing 76 such that the tubular member of the tube bundle 78 is substantially laterally framed. In an exemplary embodiment, wall 92 may be spaced between about 0.02 inches (0.5 mm) and about 0.8 inches (20 mm) of tubing of tube bundle 78. In yet another exemplary embodiment, the wall 92 can be spaced between about 0.1 inches (3 mm) and about 0.2 inches (5 mm) of the tubular member of the tube bundle 78. However, in order to provide sufficient space to provide the dispenser 80 between the tubular member and the upper end of the cover, the spacing between the upper end 88 and the tubular member of the tube bundle 78 can be much greater than 0.2 inches (5 mm). In an exemplary embodiment, the walls 92 of the cover 86 are substantially parallel and the housing 76 is cylindrical, and the wall 92 may symmetry the space along a symmetrical housing to align a central longitudinal plane separating the walls 92. In other exemplary embodiments, the wall 92 does not need to extend longitudinally beyond the bottom tubular member of the tube bundle 78, and the wall 92 need not be planar, i.e., the wall 92 can be curved or have other non-planar shapes. Regardless of its specific configuration, the cover 86 is configured to direct the coolant 106 through the open end 94 of the cover 86 within the extent of the wall 92.

6A-6C illustrate an exemplary embodiment of an evaporator assembly as a "falling film" evaporator 128, as shown in Figures 6A-6C, the evaporator 128 is similar to the evaporator shown in Figures 5A through 5C. 138, except that the evaporator 128 does not include a tube bundle 140 positioned within a pool of coolant 82 concentrated at the bottom of the housing. In a van In an exemplary embodiment, the cover 86 terminates after being disposed within the tube bundle 78, although in another exemplary embodiment, the cover 86 extends further toward the pool of coolant 82 after covering the tube bundle 78. In yet another exemplary embodiment, the cover 86 terminates such that the cover does not completely cover the bundle, i.e., substantially covers the bundle.

As shown in FIGS. 6B and 6C, a pump 84 can be used to recirculate the pool of liquid coolant 82 from the bottom of the housing 76 via line 114 to the distributor 80. As shown in Figure 6B, line 114 can include an adjustment device 112 that can be in fluid communication with a condenser (not shown). In another exemplary embodiment, an injector (not shown) can be applied to draw liquid coolant 82 from the bottom of housing 76 using pressurized coolant from condenser 34 operating with the Celan effect. This injector combines the functions of the adjustment device 112 with the pump 84.

In an exemplary embodiment, an arrangement of tubes or bundles of tubes may be defined by a plurality of equally spaced tubes longitudinally and horizontally aligned to form a substantially rectangular contour. However, the tubular members are not aligned longitudinally or horizontally, and tube bundle stacking arrangements that are not equally spaced may be used.

In another exemplary embodiment, different tube bundle structures are contemplated, for example, a tube with fins (not shown) may be used in the tube bundle, such as along the topmost horizontal column or the top of the tube bundle. In addition to the possibility of using finned tubulars, the tubular components are more efficient in pool boiling applications, such as in "full liquid" evaporators. In addition, or in combination with a tubular member having fins, a porous coating may also be applied to the outer surface of the tubular member of the bundle.

In still another exemplary embodiment, the cross-sectional profile of the evaporator housing may be non-circular.

In an exemplary embodiment, a portion of the cover may extend partially into the outlet of the housing.

Moreover, it is possible to incorporate the dispenser 80 into the expansion function of the expansion device of the system 14. In an exemplary embodiment, two expansion devices are applicable. An expansion device is a spray nozzle embodied in the dispenser 80. Another expansion device, such as expansion device 36, provides an initial partial expansion of the coolant prior to delivery of the spray nozzle located within the evaporator. In an exemplary embodiment, the other expansion device, that is, the non-spray nozzle expansion device, can be controlled by different levels of liquid coolant 82 located in the evaporator for different operating environments, such as evaporation and condensation pressure, and Partially cooled load. In an alternate exemplary embodiment, the expansion device can be controlled by the height of the liquid coolant located in the condenser, or in another exemplary embodiment, a "flash economizer" conduit. In an exemplary embodiment, the primary expansion can be created at the nozzle, providing a greater pressure differential while allowing the nozzle to be downsized, thereby reducing the size and cost of the nozzle.

Other disclosures, including dispensers, are disclosed in the U.S. Non-Provisional Application Serial No. 12/875,748, entitled "Vapor Compression System", filed on September 3, 2010, which is incorporated herein by reference.

Figure 7 illustrates an exemplary embodiment of a dispenser 142 that is configured to apply fluid entering the dispenser 142 to a bundle of tubes as described above, as shown in Figure 6B. The dispenser 142 includes a perimeter 144 having a distal end 148 disposed to face a bundle of tubes (Fig. 6B) and an opposite end 150 facing away from the bundle of tubes. The dispenser 142 also includes an inlet 156 formed at the end 150 and extending between the end 152 and the opposite end 154. End 148 includes at least one The end device 158 is operatively mated by the dispensing device 146 or the plurality of dispensing devices 146. In one embodiment, the dispensing device 146 includes an opening 160 (FIG. 9) formed at the end 148 of the end profile 158. The effect of this arrangement is that the fluid 206, which may include a vapor-liquid two-phase mixture, enters the inlet 156 of the enclosure 144, distributes along the length of the enclosure 144 and exits the enclosure 144 via the dispensing device 146 to form the distribution fluid 208. Due to the novel structure of the enclosure 144, the flow of the distribution fluid 208 is improved along the length of the enclosure 144, i.e., forms a more uniform flow along the length of the enclosure.

It will be appreciated that one, two or more dispensers 142 can be used with a single bundle of tubes. In one embodiment, two or more dispensers may have an overlapping spray angle 166 for dispensing fluid 208 (FIG. 11). In one embodiment, a bundle of tubes can be divided into zones, such as longitudinal separation zones, with a plurality of separate distributors. For example, for a plurality of tube bundles divided into a plurality of longitudinal separation zones, one or more dispensers can be placed between each zone to provide improved, multi-stage wetting of the tubular bundle.

As shown in Figures 7-10, the enclosure 144 can be extended to form a unitary or one-piece structure from a plurality of combinations, such as by welding.

10 shows a cross-sectional view along line 10-10 of an opening 160 extending through end profile 158 formed at end 148 along FIG. The end 148 extends to the opposing body portions 168, 170. As shown in Figure 10, the body portions 168, 170 are parallel to each other and have a plane of symmetry 180 relative to each other. As shown in FIG. 10, the enclosure has a height 176 and a width 178. The term "aspect ratio" refers to the height 176 divided by the width 178. The aspect ratio of the enclosure may be between about 1/2:1 and about 10:1, about 1/2:1 and about 8:1, about 2:1 and about 6:1. About 2:1 and about 4:1, about 2:1 and about 3:1, about 3:1 and about 8:1, about 4:1 and about 6:1, about 2:1, about 3:1 Approximately 4:1 or any combination thereof. With an appropriately sized aspect ratio result, in combination with the size and space of the opening 160, the fluid flow through the opening 160 of the enclosure can be optimized, i.e., substantially covering the entire fluid pressure range associated with the operation of the dispenser of the present invention. The length of the body is more uniform.

For example, as shown in Figures 8-10, the inlet 156 has a length 194 between 1/6 and 1/3 of the length 200. The inlet 156 is located substantially centrally between the opposite end portions 196, 198. In one embodiment, adjacent openings 160 formed in the end profile 158 of the tip 148 have an interval 164 that is substantially equal to each other along the length 200. In another embodiment, the spacing 164 between at least a portion of the adjacent opening 160 associated with the inlet 156 can be greater than the spacing 202 between at least a portion of the adjacent opening 160 associated with the tip portion 196, and / or greater than the spacing 204 between at least a portion of the adjacent opening 160 associated with the tip portion 198 to promote a more consistent fluid flow through the concentrated opening 160 along the length 200 of the enclosure 144. In one embodiment, the spacing 202 between at least a portion of the adjacent opening 160 associated with the tip portion 196 can be substantially spaced relative to the spacing 204 between at least a portion of the adjacent opening 160 associated with the tip portion 198. . In one embodiment, the opening 160 includes a substantially uniform width 162. In one embodiment, the slit end of the opening 160 may be "square" or substantially rectangular, although in another embodiment, the end of the slit may be curved or curved and linearly combined, as shown in Figures 11-14, respectively. The similarly shaped end topography bodies 158, 258, 358, 458 are shown further below. In another embodiment, the opening 160 Can have different widths. Thus, it can be appreciated that the size of the opening 160 corresponds to the combination of the end of the slit of the opening 160 to the distance 186 of the distal end tangent position 184 (FIG. 11) of the end profile body 158 of the enclosure, ie, the height and Width 162 (Figure 10). That is, if the widths 162 of the openings 160 are substantially equal to one another, the dimensions of the openings 160 are considered to be substantially equal if the height of the openings or the distance 186 are also substantially equal. In one embodiment, the widths 162 of the openings 160 are different from each other, and the heights or distances 186 of the openings may be different from each other, but the dimensions of the openings 160 may be substantially equal to each other as long as the result is 200 along the length of the enclosure (Fig. 8). The fluid flow is substantially uniform. In one embodiment, at least two of the openings 160 are substantially equal or substantially equal in size to each other.

Although the body portions 168, 170 shown in FIG. 10 are generally parallel, the body portion 168 can include an angular error 172 and/or the body portion 170 can include an angular error 174. That is, each of the body portions 168, 170 can be reciprocally shaped into a V shape by being offset parallel to each other between 0 and about 45 degrees or other sub-combinations. In one embodiment, the angular error 172 and/or the angular error 174 may vary along the length of the enclosure if desired.

11 is a partial enlarged view of the area 11 of FIG. 10 showing further details of an example of the end topography 158 of the enclosure 144. As shown in FIG. 11, the topography 158 defines a curved or hemispherical profile having an effective radius or effective radius distance 189 and extending to the opposing enclosure portions 168, 170. In one embodiment, the radius or effective radius or radius distance 189 may include one or more curves having different radii of curvature. The effective radius or effective radiation distance 189 extends outwardly from a center point or coincident point 181 of a reference line 182 that coincides with substantially perpendicularly opposite body portions 168, 170. As shown in Figure 10 The body portions 168, 170 are shown to be parallel to one another and have a plane of symmetry 180 relative to each other, and in one embodiment, the plane of symmetry 180 coincides with the reference line 182. In one embodiment, the coincident point 181 is not located at the center of the enclosure 144. In one embodiment, the enclosure does not have a plane of symmetry. The opening 160 includes edges 161, 163 associated with the end of the slit associated with the opening 160, the edge 161 being adjacent and associated with the body portion 168, the edge 163 being adjacent and associated with the body portion 170. As further shown in FIG. 11, a reference line 183 is substantially perpendicular to the opposing body portions 168, 170 and extends through the edges 161, 163. Reference line 182 is parallel to reference line 183. A distal end portion 187 of the distal end portion 148 relative to the end shaped body 158 of the body portions 168, 170 includes a distal end point 184 that coincides with a reference line 185 that is generally parallel to the reference lines 182, 183. The spacing 161, 163 of the opening 160 forms a distance 186 from the spacing or effective spacing between the tangent points 184 of the distal end portion 187 of the end topography 158 measured along the reference line 185. A distance 188 is formed between the reference line 182 extending through the coincident point 181 and the distal tangent point 184 measured along the reference line 185. The distance 188 is greater than the distance 186. That is, the effective radius or effective radiation distance 189 associated with a distal tangential portion, such as the tangent point 184 (distance 188) of the end topography 158, is greater than the edge 161 associated with the distal tangent portion, such as the tangent point 184 (distance 186). Effective interval or interval between 163. As a result, the dispensing fluid flowing through the opening 160 is limited to between about 60 degrees and about 180 degrees, between about 90 degrees and about 180 degrees, between about 120 degrees and about 180 degrees, Between about 150 degrees and about 180 degrees, between about 160 degrees and about 180 degrees, between about 160 degrees and about 170 degrees, between about 160 degrees and about 165 degrees, about 160 degrees a spray angle 166 of about 165 degrees and about 170 degrees, the spray angle 166 being in operation with the dispenser of the vapor compression system The fluid pressure of the shutoff remains relatively constant under the substantial overall range.

12 is a partial enlarged view similar to zone 11 of FIG. 10 showing further details of an example of end profile 258 of enclosure 144. As shown in FIG. 12, the topography 258 defines a square or rectangular profile that is comprised of linear segments having an effective radius or effective radius distance 289 and extending to the perimeter of the opposing enclosure portions 168, 170. The effective radius or effective radiation distance 289 extends outwardly from a center point or coincident point 281 of a reference line 282 that coincides with substantially perpendicularly opposite body portions 168, 170. In one embodiment, the coincident point 281 is not centered on the enclosure 144. In one embodiment, the enclosure does not have a plane of symmetry. The opening 260 includes edges 261, 263 associated with the end of the slit associated with the opening 260, the edge 261 being adjacent and associated with the body portion 168, the edge 263 being adjacent and associated with the body portion 170. As further shown in FIG. 12, a reference line 283 is substantially perpendicular to the opposing body portions 168, 170 and extends through the edges 261, 263. Reference line 282 is parallel to reference line 283. A distal end portion 287 of the distal end portion 148 relative to the end shaped body 258 of the body portions 168, 170 includes a distal tangent point 284 that coincides with a reference line 285 that is generally parallel to the reference lines 282, 283. The distance or effective spacing between the edges 261, 263 of the opening 260 and the tangent point 284 of the distal end portion 287 of the end topography 258 measured along the reference line 285 forms a distance 286. A distance 288 is formed between the reference line 282 extending through the coincident point 281 and the distal tangent point 284 measured along the reference line 285. The distance 288 is greater than the distance 286. That is, the effective radius or effective radiation distance 289 associated with a distal tangential portion, such as the tangent point 284 (distance 288) of the end topography 258, is greater than the edge 161 associated with the distal tangential portion, such as the tangent point 284 (distance 286). Effective interval or interval between 163. As a result, the fluid flow is distributed The through opening 260 is limited to between about 60 degrees and about 180 degrees, between about 90 degrees and about 180 degrees, between about 120 degrees and about 180 degrees, between about 150 degrees and about 180 degrees. Between degrees, between about 160 degrees and about 180 degrees, between about 160 degrees and about 170 degrees, between about 160 degrees and about 165 degrees, about 160 degrees, about 165 degrees, and about At a spray angle 166 of 170 degrees (Fig. 11), the spray angle 166 remains relatively fixed below the substantial overall range of fluid pressure associated with operation of the dispenser of the vapor compression system.

13 is a partial enlarged view similar to zone 11 of FIG. 10 showing further details of an example of end profile 358 of enclosure 144. As shown in FIG. 13, end profile body 358 defines a V-shaped profile that is comprised of a linear segment having an effective radius or effective radial distance 389 and extending to the perimeter of opposing body portions 168, 170. The effective radius or effective radiation distance 389 extends outwardly from a center point or coincident point 381 of a reference line 382 that coincides with substantially perpendicularly opposite body portions 168, 170. In one embodiment, the coincident point 381 is not located at the center of the enclosure 144. In one embodiment, the enclosure does not have a plane of symmetry. The opening 360 includes edges 361, 363 associated with the end of the slit associated with the opening 360, the edge 361 being adjacent and associated with the body portion 168, the edge 363 being adjacent and associated with the body portion 170. As further shown in FIG. 13, a reference line 383 is substantially perpendicular to the opposing body portions 168, 170 and extends through the edges 361, 363. Reference line 382 is parallel to reference line 383. A distal end portion 387 of the distal end portion 148 relative to the end shaped body 358 of the body portions 168, 170 includes a distal tangent point 384 that coincides with a reference line 385 that is generally parallel to the reference lines 382, 383. The edges 361, 363 of the opening 360 form a distance from the spacing or effective spacing between the tangent points 384 of the distal end portion 387 of the end topography 358 measured along the reference line 385. 386. A distance 388 is formed between the reference line 382 extending through the coincident point 381 and the distal tangent point 384 measured along the reference line 385. The distance 388 is greater than the distance 386. That is, the effective radius or effective radiation distance 389 associated with a distal tangent portion, such as tangent point 384 (distance 388) of end topography 358, is greater than edge 361 associated with the distal tangent portion, such as tangent point 384 (distance 386). Effective interval or interval between 363. As a result, the dispensing fluid flow through opening 360 is limited to between about 60 degrees and about 180 degrees, between about 90 degrees and about 180 degrees, between about 120 degrees and about 180 degrees, between Between about 150 degrees and about 180 degrees, between about 160 degrees and about 180 degrees, between about 160 degrees and about 170 degrees, between about 160 degrees and about 165 degrees, about 160 degrees, At a spray angle 166 (Fig. 11) of about 165 degrees, and about 170 degrees, the spray angle 166 remains relatively fixed below the substantial overall range of fluid pressure associated with operation of the dispenser of the vapor compression system.

14 is a partial enlarged view similar to zone 11 of FIG. 10 showing further details of an example of end profile 458 of enclosure 144. As shown in FIG. 14, the bottom of the topography 458 defining a "D" profile is formed by combining a linear and curved section of a body having an effective radius or effective radius distance 489 and extending to the opposing body portions 168, 170. . In one embodiment, a different arrangement or profile of curved segments than linear segments can be used. The effective radius or effective radiation distance 489 extends outwardly from a center point or coincident point 481 of a reference line 482 that coincides with substantially perpendicularly opposite body portions 168, 170. In one embodiment, the coincident point 481 is not centered on the enclosure 144. In one embodiment, the enclosure does not have a plane of symmetry. The opening 460 includes edges 461, 463 associated with the end of the slit associated with the opening 460, the edge 461 being adjacent and surrounding the body portion 168 Relatedly, the edge 463 is adjacent and associated with the body portion 170. As further shown in FIG. 13, a reference line 483 is substantially perpendicular to the opposing body portions 168, 170 and extends through the edges 461, 463. Reference line 482 is parallel to reference line 483. A distal end portion 487 of the distal end portion 148 relative to the end shaped body 458 of the body portions 168, 170 includes a distal end point 484 that coincides with a reference line 485 that is generally parallel to the reference lines 482, 483. The spacing 461, 463 of the opening 460 forms a distance 486 from the spacing or effective spacing between the tangent points 484 of the distal end portion 487 of the end topography 458 as measured along the reference line 485. A distance 488 is formed between the reference line 482 extending through the coincident point 481 and the distal tangent point 484 measured along the reference line 485. The distance 488 is greater than the distance 486. That is, the effective radius or effective radiation distance 489 associated with a distal tangential portion, such as the tangent point 484 (distance 488) of the end topography 458, is greater than the edge 461 associated with the distal tangential portion, such as the tangent point 484 (distance 486). Effective interval or interval between 463. As a result, the dispensing fluid flowing through the opening 460 is limited to between about 60 degrees and about 180 degrees, between about 90 degrees and about 180 degrees, between about 120 degrees and about 180 degrees, between Between about 150 degrees and about 180 degrees, between about 160 degrees and about 180 degrees, between about 160 degrees and about 170 degrees, between about 160 degrees and about 165 degrees, about 160 degrees, At a spray angle 166 (Fig. 11) of about 165 degrees, and about 170 degrees, the spray angle 166 remains relatively fixed below the substantial overall range of fluid pressure associated with operation of the dispenser of the vapor compression system.

It can be appreciated that the lines 183, 283, 383, 483 associated with the respective distances 186, 286, 386, 486 are not limited to extending through respective corresponding edges 161 and 163 of the corresponding openings 160, 260, 360, 460. , 261 and 263, 361 and 363, 461 and 463. For example, in one embodiment, the opening Edges 161 and 163 of 160 may be offset relative to line 183 such that line 183 presents an average distance 186 between edges 161 and 163. However, the lines 183, 283, 383, 483 and the respective distances 186, 286, 386, 486 corresponding to the respective tangent points 184, 284, 384, 484 are less than the lines 182, 282, 382, 482 and to the respective tangent points 184. The respective corresponding distances 188, 288, 388, 488 between the respective distances 188, 288, 388, 488 of 284, 384, 484, in order to ensure consistency, the controlled spray angle 166 of the dispensed fluid flow (Fig. 11), the reason described above.

Figure 15 illustrates an exemplary embodiment of a dispenser 142 having a linear axis 190 having a curved axis 192 compared to a dispenser having a straight or linear axis, such as in combination with different configurations of openings 160 (Figure 8 ), providing improved fluid distribution on partial tube bundles.

While only the specific features and embodiments of the present invention have been shown and described, without departing from the scope of the invention, Variations may result (eg, size, size, structure, appearance and proportion of different components, parameter values (eg, temperature, pressure, etc.), arrangement of arrangements, materials used, color, orientation, etc.). The order of any process or method steps may be changed or reordered according to various embodiments. Therefore, it is to be understood that the scope of the appended claims is intended to cover all modifications and changes in the spirit of the invention. Furthermore, in order to provide a precise description of the exemplary embodiments, not all features are described in the actual aspects (e.g., not related to the presently preferred embodiments of the present invention, or the meaning of the patent application scope of the present invention. related). What needs to be understood is that in any such In the development of the actual situation, as in any engineering or design case, several specific implementation decisions may be made. Such developments can be complex and time consuming, but would be a routine practice for design, manufacture, and production without undue experimentation for those skilled in the art having the benefit of this disclosure.

14‧‧‧Vapor Compression System

32‧‧‧Compressor

34‧‧‧Condenser

36‧‧‧Expansion device

38‧‧‧Evaporator

40‧‧‧Control panel

42‧‧‧ Analog Digital (A/D) Converter

44‧‧‧Microprocessor

46‧‧‧Non-volatile memory

48‧‧‧Intermediate panel

50‧‧‧Motor

52‧‧‧ Variable speed drive

54‧‧‧ tube bundle

56‧‧‧Cooling tower

60R‧‧‧Reflow line

60S‧‧‧ supply line

62‧‧‧Cooling load

64‧‧‧Intermediate circuit

66‧‧‧Expansion device

68‧‧‧Entry line

70‧‧‧ middle tube

72, 74‧‧‧ pipeline

Claims (10)

A dispenser for use in a vapor compression system, comprising: a surrounding body assembled to be disposed in a heat exchanger having a plurality of substantial horizontal extensions included in the heat exchanger a bundle of tubes; and at least one dispensing device formed in one end of the enclosure to face the bundle of tubes, the at least one dispensing device being assembled to apply fluid entering the dispenser to the bundle Upper; wherein the enclosure has an aspect ratio of between about 2:1 and about 6:1. The dispenser of claim 1, wherein the end of the enclosure comprises a tip topography and the at least one dispensing device comprises at least one opening formed in the tip topography; wherein the at least one opening is A spray angle dispensing fluid is provided and arranged to substantially cover an entire range of fluid pressures associated with operation of the dispenser of the system between about 60 degrees and about 180 degrees. The dispenser of claim 2, wherein the tip topography comprises at least one of a curved profile, a linear profile, or a combination thereof. The dispenser of claim 2, comprising a substantially parallel opposite portion extending away from the end of the enclosure. The dispenser of claim 4, wherein the opposing portions are offset from each other by between 0 degrees and about 45 degrees. The dispenser of claim 4, wherein the end profile is associated with And a reference line that is substantially perpendicular to the opposite portions of the end shaped body is disposed at a first distance from a distal tangent portion of the end topography body, and a second distance is formed on the at least one An effective spacing of the edge of the opening and the distal tangential portion of the end topography body, the first distance being greater than the second distance. The dispenser of claim 6 wherein the reference line coincides with a center point of an effective radius of the end topography body. The dispenser of claim 7, wherein a plane of symmetry of the enclosure coincides with the center point. The dispenser of claim 1 wherein the aspect ratio is between about 2:1 and about 4:1. A method for dispensing a fluid in a vapor compression system, comprising: providing a surrounding body that is assembled to be disposed in a heat exchanger having a bundle of tubes, the bundle of tubes being substantially horizontally contained in the heat exchanger An extended plurality of tubular members; and at least one dispensing device formed in one end of the surrounding body disposed to face the bundle of tubes, the at least one dispensing device being assembled to apply fluid entering the dispenser to the bundle of tubes, Wherein the enclosure has an aspect ratio of between about 2:1 and about 6:1; and operating the vapor compression system.