CN105408703A - Distributor for use in a vapor compression system - Google Patents

Abstract

A distributor (142) for use in a vapor compression system (14) includes an enclosure (144) configured to be positioned in a heat exchanger (38) having a tube bundle (78) including a plurality of tubes extending substantially horizontally in the heat exchanger (38). At least one distribution device (146) formed in an end (148) of the enclosure (144) positioned to face the tube bundle (78), the at least one distribution device (146) configured to apply a fluid entering the distributor (142) onto the tube bundle (78). The enclosure (144) has an aspect ratio between about 1/2:1 and about 10:1.

Description

Distributors for use in vapor compression systems

Cross References to Related Applications

This application claims priority to and benefit of US Non-provisional Application No. 13/912634, filed June 7, 2013, entitled "Vapor Compression System."

Background technique

This application relates generally to vapor compression systems in refrigeration, air conditioning and refrigerated liquid systems. The present application relates more particularly to dispensing systems and methods in vapor compression systems.

Conventional refrigerant fluid systems used in HVAC systems include an evaporator to transfer thermal energy between the system's refrigerant and other fluids to be cooled. One type of evaporator comprises a shell with a plurality of tubes forming a tube bundle through which the liquid to be cooled circulates. Refrigerant is brought into contact with the outer or outside surface of the tube bundle inside the shell, resulting in thermal energy transfer between the liquid to be cooled and the refrigerant. For example, in what is commonly referred to as a "falling film" evaporator, the refrigerant may be deposited onto the outside surfaces of the tube bundle by spraying or other similar techniques. In another example, the outside surface of the tube bundle may be fully or partially immersed in the liquid refrigerant in what is commonly called a "flooded" evaporator. In yet another example, a portion of a tube bundle may have refrigerant deposited on the outside surface, and another portion of the tube bundle may be immersed in liquid refrigerant in what is commonly referred to as a "hybrid falling film" evaporator.

Due to thermal energy transfer with the liquid, the refrigerant is heated to convert to a vapor state and then returns to the compressor where the vapor is compressed to start another refrigerant cycle. The cooled liquid can be circulated to multiple heat exchangers throughout the building. The hot air from the building passes through the heat exchanger where the cooled liquid is heated while cooling the building air. The liquid heated by the building's air returns to the evaporator to repeat the process.

Contents of the invention

The present invention relates to a distributor for use in a vapor compression system comprising an enclosure configured to be positioned in a heat exchanger having a tube bundle having a substantially horizontal extension in said heat exchanger of multiple tubes. At least one distribution device is formed in one end of the enclosure positioned facing the tube bundle, the at least one distribution device being configured to apply fluid entering the distributor to the tube bundle. The capsule has an aspect ratio between about 1/2:1 and about 10:1.

The present invention also relates to a distributor for use in a vapor compression system comprising an enclosure configured to be positioned in a heat exchanger having a tube bundle comprising a plurality of substantially horizontally extending tubes in said heat exchanger. root canal. At least one distribution device is formed in one end of the enclosure positioned facing the tube bundle, the at least one distribution device being configured to apply fluid entering the distributor to the tube bundle. The capsule has an aspect ratio between about 1/2:1 and about 10:1. The end of the enclosure includes an end feature, and the at least one distribution device includes at least one opening formed in the end feature. The at least one opening is configured and arranged to distribute fluid at a spray angle of between about 60 degrees and about 180 degrees over substantially the entire range of fluid pressures associated with operation of the dispenser in the system.

The invention additionally relates to a method of distributing fluid in a vapor compression system. The method includes providing an enclosure configured to be positioned in a heat exchanger having a tube bundle including a plurality of tubes extending generally horizontally in the heat exchanger. The method includes forming at least one distribution device in one end of the enclosure positioned to face the tube bundle, the at least one distribution device configured to apply fluid entering the distributor to the above the tube bundle. The capsule has an aspect ratio between about 1/2:1 and about 10:1. The method includes operating the vapor compression system.

Description of drawings

Figure 1 shows an exemplary embodiment for an HVAC system.

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

Figures 3 and 4 schematically illustrate exemplary embodiments of the vapor compression system.

Figure 5A shows an exploded partial cross-sectional view of an exemplary evaporator.

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

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

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

6B and 6C show cross-sectional views of the evaporator taken along line 6-6 in FIG. 6A.

Figure 7 shows an upper perspective view of an exemplary embodiment of a capsule.

FIG. 8 shows a plan view of the enclosure in FIG. 7 .

Figure 9 shows a partial front view of the enclosure taken along line 9-9 in Figure 7 .

FIG. 10 shows a cross-sectional view of the enclosure taken along line 10 - 10 in FIG. 9 .

FIG. 11 shows a cross-sectional view of the enclosure of an exemplary embodiment taken along line 10 - 10 in FIG. 9 .

FIG. 12 shows a cross-sectional view of another exemplary embodiment enclosure taken along line 10 - 10 in FIG. 9 .

FIG. 13 shows a cross-sectional view of another exemplary embodiment enclosure taken along line 10 - 10 in FIG. 9 .

FIG. 14 shows a cross-sectional view of yet another exemplary embodiment enclosure taken along line 10 - 10 in FIG. 9 .

Figure 15 shows an exemplary embodiment of a capsule.

detailed description

FIG. 1 illustrates one exemplary environment for a heating, ventilation and air conditioning (HVAC) system 10 including a chilled liquid system used in a building 12 of a typical commercial facility. System 10 may include a vapor compression system 14 that may supply refrigerated liquid that may be used to cool building 12 . System 10 may include a boiler 16 to supply heated liquid that may be used to heat building 12 , and an air distribution system that circulates air through building 12 . The air distribution system may also include an air return duct 18 , an air supply duct 20 and an air handler 22 . Air handler 22 may include a heat exchanger connected to boiler 16 and vapor compression system 14 by conduit 24 . The heat exchanger in air handler 22 may receive heated liquid from boiler 16 or chilled liquid from vapor compression system 14 depending on the mode of operation of system 10 . The system 10 is shown with separate air handlers on each floor of the building 12, although it is understood that some components may be shared between two or more floors.

2 and 3 illustrate an exemplary vapor compression system 14 that may be used in an HVAC system, such as HVAC system 10 . Vapor compression system 14 may circulate refrigerant through compressor 32 driven by motor 50 , condenser 34 , expansion device 36 , and liquid refrigerator or evaporator 38 . The vapor compression system 14 may also include a control panel 40 that may include an analog-to-digital (A/D) converter 42 , a microprocessor 44 , non-volatile memory 46 , and an interface board 48 . Some examples of fluids that may be used as refrigerants in the vapor compression system 14 are hydrofluorocarbon (HFC) based refrigerants such as R-410A, R-407, R-134a, hydrofluoroolefins (HFO), such as "Natural" refrigerants of ammonia (NH3), R-717, carbon dioxide (CO2), R-744 or hydrocarbon based refrigerants, water vapor or any other suitable type of refrigerant. In an exemplary embodiment, vapor compression system 14 may utilize one or more of each type of device: VSD 52 , motor 50 , compressor 32 , condenser 34 , and/or evaporator 38 .

The motor 50 used with the compressor 32 can be powered by a variable speed drive (VSD) 52 or can be powered directly from an alternating current (AC) or direct current (DC) power source. If a VSD 52 is used, the VSD 52 receives AC power with a specific fixed line voltage and fixed line frequency from an AC power source and provides power with a variable voltage and frequency to the motor 50 . Motor 50 may comprise any type of electric motor that may be powered by a VSD or directly from an AC or DC power source. For example, motor 50 may be a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor, or any other suitable motor type. In alternative exemplary embodiments, 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 refrigerant vapor and delivers the vapor to condenser 34 through a discharge line. Compressor 32 may be a centrifugal compressor, screw compressor, reciprocating compressor, rotary compressor, rocker compressor, scroll compressor, turbo compressor, or any other suitable compressor. Refrigerant vapor delivered by compressor 32 to condenser 34 transfers heat to a fluid, such as water or air. The refrigerant vapor condenses into a refrigerant liquid in condenser 34 due to heat transfer with the fluid. Liquid refrigerant from condenser 34 flows through expansion device 36 to evaporator 38 . In the exemplary embodiment shown in FIG. 3 , condenser 34 is water cooled and includes a tube bundle 54 connected to a cooling tower 56 .

The liquid refrigerant delivered to the evaporator 38 absorbs heat from another fluid, which may or may not be the same type as the fluid used by the condenser 34 , and undergoes a phase change to a refrigerant vapor. In the exemplary embodiment shown in FIG. 3 , the evaporator 38 comprises a tube bundle having a supply line 60S and a return line 60R connected to a cooling load 62 . Process fluid, such as water, glycol, calcium chloride brine, sodium chloride brine, or any other suitable liquid, enters evaporator 38 via return line 60R and exits evaporator 38 via supply line 60S. The evaporator 38 reduces the temperature of the process fluid in the tube. The tube bundle in evaporator 38 may contain multiple tubes and multiple tube bundles. Vapor refrigerant exits evaporator 38 and returns to compressor 32 through the suction line to complete the cycle.

Figure 4 is similar to Figure 3 and shows a refrigerant circuit with an intermediate circuit 64 that may be placed between the condenser 34 and the expansion device 36 to increase cooling capacity, efficiency and performance. The intermediate circuit 64 has an inlet line 68 which may be directly connected to the condenser 34 or may be in fluid communication with the condenser 34 . As shown, inlet line 68 includes expansion device 66 upstream of intermediate vessel 70 . In an exemplary embodiment, intermediate vessel 70 may be a flash tank, also known as a flash intercooler. In an alternate exemplary embodiment, intermediate vessel 70 may be configured as a heat exchanger or "surface economizer." In a flash intercooler arrangement, the first expansion device 66 is used to reduce the pressure of the liquid received from the condenser 34 . During the expansion process in the flash intercooler, a portion of the liquid evaporates. An intermediate vessel 70 may be used to separate evaporated vapor from liquid received from the condenser. The vaporized liquid can be drawn by the compressor 32 to a port through line 74, either at a pressure between the suction side and the discharge side or at an intermediate stage of compression. The unevaporated liquid is cooled by the expansion process and collected at the bottom of the intermediate vessel 70 , through the line 72 comprising the second expansion device 36 , said liquid at the bottom is recovered and flows to the evaporator 38 .

In a "surface intercooler" arrangement, as known to those skilled in the art, the implementation is slightly different. The intermediate circuit 64 may operate in a manner similar to that described above, except that the intermediate circuit 64 receives only a portion of the refrigerant from the condenser 34 and the remainder of the refrigerant travels directly to the expansion device 36 rather than from the condenser as shown in FIG. 4 . 34 receives the full amount of refrigerant.

5A-5C illustrate an exemplary embodiment of an evaporator configured as a "hybrid falling film" evaporator. As shown in FIGS. 5A-5C , evaporator 138 includes a generally cylindrical shell 76 having a plurality of tubes forming a tube bundle 78 extending generally horizontally along the length of shell 76 . At least one support 116 may be positioned within housing 76 to support the plurality of tubes in tube bundle 78 . A suitable fluid, such as water, ethylene, glycol, or calcium chloride brine flows through the individual tubes of tube bundle 78 . Distributor 80 positioned above tube bundle 78 distributes, deposits or applies refrigerant 110 to the individual tubes in tube bundle 78 from multiple locations. In one exemplary embodiment, the refrigerant deposited by the distributor 80 may be entirely liquid refrigerant, but in another exemplary embodiment, the refrigerant deposited by the distributor 80 may contain liquid refrigerant and vapor refrigerant .

Liquid refrigerant flowing around the tubes of tube bundle 78 without changing state collects in the lower portion of shell 76 . The collected liquid refrigerant may form a pool or reservoir 82 of liquid refrigerant. The deposition position of the slave distributor 80 may comprise any combination of longitudinal or transverse positions relative to the tube bundle 78 . In another exemplary embodiment, the deposition locations from the distributor 80 are not limited to deposition locations to the upper tubes of the tube bundle 78 . Distributor 80 may comprise a plurality of nozzles fed by a dispersed source of refrigerant. In an exemplary embodiment, the dispersion source is a tube connected to a refrigerant source (eg, condenser 34). Nozzles include spray nozzles, but also machined openings that can direct or direct refrigerant onto the surface of the tube. The nozzles may apply refrigerant in a predetermined pattern, such as a spray pattern, such that the upper row of tubes of the tube bundle 78 is covered. The tubes of tube bundle 78 may be arranged to facilitate the flow of refrigerant in the form of a film around the surface of the tubes, a liquid refrigerant coalescing to form droplets, or, in some examples, located in the tubes. A curtain or curtain of liquid refrigerant at the bottom of a surface. The curtain formed promotes wetting of the tube surfaces, which enhances the efficiency of heat transfer between the fluid flowing within the individual tubes of the tube bundle 78 and the refrigerant flowing around the surfaces of the individual tubes of the tube bundle 78 .

In the pool 82 of liquid refrigerant, the tube bundle 140 may be submerged or at least partially submerged therein to provide additional thermal energy transfer between the refrigerant and the process fluid, thereby evaporating the pool 82 of liquid refrigerant. In an exemplary embodiment, tube bundle 78 may be positioned at least partially above (ie, at least partially overlap) tube bundle 140 . In an exemplary embodiment, evaporator 138 comprises a two-pass system in which the process fluid to be cooled first flows within the tubes of tube bundle 140 and is then directed to flow through tube bundle 78 in a direction opposite to the flow in tube bundle 140. flow in each tube. In the second pass of the two-pass system, the temperature of the fluid flowing in the tube bundle 78 is reduced and therefore a lesser amount of heat transfer needs to occur with the refrigerant flowing on the surface of the tube bundle 78 to obtain the desired temperature of the process fluid.

It should be appreciated that while the foregoing describes a two-pass system in which a first pass is associated with tube bundle 140 and a second pass is associated with tube bundle 78 , other possible arrangements are contemplated. For example, evaporator 138 may comprise a single pass system in which process fluid flows through tube bank 140 and tube bank 78 in the same direction. Alternatively, evaporator 138 may comprise a three-way system in which two passages are associated with tube bundle 140 and the remaining one is associated with tube bundle 78, or in which one passage is associated with tube bundle 140 and the remaining two passages are associated with tube bundle 78 . Additionally, evaporator 138 may include an alternating two-pass system in which one pass is associated with both tube bundle 78 and tube bundle 140 and a second pass is also associated with both tube bundle 78 and tube bundle 140 . In an exemplary embodiment, tube bundle 78 is positioned at least partially above tube bundle 140 such that there is a separation gap between tube bundle 78 and tube bundle 140 . In yet another exemplary embodiment, a shroud 86 overlies the tube bundle 78, wherein the shroud 86 extends toward the gap and terminates adjacent the gap. In general, the present invention contemplates systems having any number of passages, where each passage may be associated with either or both tubes 78 and tube bundles 140 .

Enclosure or shroud 86 is positioned over tube bundle 78 to substantially block cross flow, ie, lateral flow of vapor refrigerant or liquid and vapor refrigerant 106 between the tubes of tube bundle 78 , from occurring. The shroud 86 is positioned over the tubes of the tube bundle 78 and laterally bounds the tubes of the tube bundle 78 . Cover 86 includes an upper end 88 positioned adjacent an upper portion of housing 76 . Distributor 80 may be positioned between shroud 86 and tube bundle 78 . In yet another exemplary embodiment, the distributor 80 may be positioned near the shroud 86 but outside of the shroud 86 such that the distributor 80 is not between the shroud 86 and the tube bundle 78 . However, even though distributor 80 is not between shroud 86 and tube bundle 78, the nozzles of distributor 80 are still configured to direct or apply refrigerant onto the surfaces of the tubes. The upper end 88 of the shroud 86 is configured to substantially prevent the flow of applied refrigerant 110 and partially evaporated refrigerant (ie, liquid and/or vapor refrigerant 106 ) from flowing directly to the outlet 104 . Instead, the applied refrigerant 110 and refrigerant 106 are confined by the shroud 86 and, more specifically, forced to travel downward between the walls 92 before the refrigerant can pass through the open end 94 in the shroud 86 quit. The flow of vapor refrigerant 96 around the shroud 86 also involves the flow of evaporated refrigerant from the pool 82 of liquid refrigerant.

It should be understood that at least the relative terms identified above are non-limiting with respect to the other exemplary embodiments in this disclosure. For example, the shroud 86 may be rotatable relative to the other evaporator components previously discussed, that is, the shroud 86 including the wall 92 is not limited to a vertical orientation. After the shroud 86 has been sufficiently rotated about an axis generally parallel to the tubes of the tube bundle 78, the shroud 86 may be considered to no longer be "positioned over" the tubes of the tube bundle 78 nor to "laterally bound" the tube bundle 78. of each tube. Similarly, the "upper" end 88 of the shroud 86 may no longer be located adjacent the "upper portion" of the housing 76, and other exemplary embodiments are not limited to such an arrangement between the shroud and the housing. In the exemplary embodiment, cover 86 ends after covering tube bundle 78 , but in another exemplary embodiment, cover 86 extends further after covering tube bundle 78 .

After the cover 86 forces the refrigerant 106 to travel down between the walls 92 through the open end 94, the direction of flow of the vapor refrigerant changes abruptly, and then in the space between the housing 76 and the wall 92 from the The lower portion goes to the upper portion of the housing 76 . Combined with gravitational effects, the sudden change in flow direction causes some of all entrained refrigerant droplets to collide with liquid refrigerant 82 or shell 76 , causing these droplets to be removed from the flow of vapor refrigerant 96 . Also, the refrigerant mist traveling along the length of the shroud 86 between the walls 92 coalesces into larger droplets that are more easily separated by gravity or maintained in close proximity to the tube bundle 78 Or in contact with the tube bundle 78 to allow evaporation of the refrigerant mist by heat transfer with the tube bundle. The efficiency of liquid separation by gravity improves due to the increased droplet size, allowing vapor refrigerant 96 to flow with an increased upward velocity through the evaporator in the space between wall 92 and housing 76 . Vapor refrigerant 96 , whether flowing from open end 94 or from pool 82 of liquid refrigerant, flows through a pair of extensions 98 that protrude from wall 92 near upper end 88 and enter channel 100 . Vapor refrigerant 96 enters channel 100 through slot 102 , which is the space between the end of extension 98 and housing 76 , before vapor refrigerant 96 exits evaporator 138 at outlet 104 . In another exemplary embodiment, vapor refrigerant 96 may enter channel 100 through an opening or hole formed in extension 98 instead of slot 102 . In yet another exemplary embodiment, slot 102 may be formed by the space between cover 86 and housing 76 , that is, cover 86 does not include extension 98 .

In other words, once the refrigerant 106 exits the cover 86 , the vapor refrigerant 96 flows along a prescribed path from the lower portion of the housing 76 to the upper portion of the housing 76 . In an exemplary embodiment, the passageway may be substantially symmetrical between the cover 86 and the surface of the housing 76 before reaching the outlet 104 . In the exemplary embodiment, a plurality of baffles, such as extensions 98 , are positioned near the evaporator outlet to block the direct path of vapor refrigerant 96 to the compressor inlet.

In an exemplary embodiment, the shroud 86 includes generally parallel opposing walls 92 . In another exemplary embodiment, each wall 92 may extend generally vertically and terminate in an open end 94 located generally opposite the upper end 88 . Upper end 88 and wall 92 are positioned proximately adjacent the tubes of tube bundle 78 , with wall 92 extending toward the lower portion of housing 76 to generally laterally bound the tubes of tube bundle 78 . In an exemplary embodiment, wall 92 may be spaced from each tube in tube bundle 78 by between about 0.02 inches (0.5 mm) and about 0.8 inches (20 mm). In yet another exemplary embodiment, wall 92 may be spaced from each tube in tube bundle 78 by between about 0.1 inches (3 mm) and about 0.2 inches (5 mm). However, the spacing between upper end 88 and the tubes of tube bundle 78 may be significantly greater than 0.2 inches (5 mm) in order to provide sufficient spacing to position distributor 80 between the tubes and the upper end of the shroud. In an exemplary embodiment in which the walls 92 of the cover 86 are generally parallel and the housing 76 is cylindrical, the walls 92 may also be arranged symmetrically about a central vertical symmetry plane of the housing that separates the spatially separated walls 92. bisect. In other exemplary embodiments, wall 92 need not extend perpendicularly through the lower tubes of tube bundle 78, nor need wall 92 be planar, as wall 92 may be curved or have other non-planar shapes. Regardless of the specific configuration, the shroud 86 is configured to flow refrigerant 106 through the open end 94 of the shroud 86 within the confines of the walls 92 .

An exemplary embodiment of an evaporator configured as a "falling film" evaporator 128 is shown in FIGS. 6A-6C . As shown in FIGS. 6A-6C , the evaporator 128 is similar to the evaporator 138 shown in FIGS. 5A-5C except that the evaporator 128 does not contain a tube bundle 140 in the refrigerant sump 82 collected in the lower portion of the shell. . In the exemplary embodiment, the shroud 86 ends after covering the tube bundle 78 , but in another exemplary embodiment, the shroud 86 extends further toward the refrigerant sump 82 after covering the tube bundle 78 . In yet another exemplary embodiment, the cover 86 ends when the cover does not completely cover the tube bundle, ie substantially covers the tube bundle.

As shown in FIGS. 6B and 6C , pump 84 may be used to recirculate liquid refrigerant pool 82 from the lower portion of housing 76 to distributor 80 via line 114 . As further shown in FIG. 6B , line 114 may include regulating device 112 which may be in fluid communication with a condenser (not shown). In another exemplary embodiment, an ejector (not shown) may be employed to draw liquid refrigerant 82 from the lower portion of shell 76 using pressurized refrigerant from condenser 34 which is The effort effect operates. The injector combines the functions of the regulating device 112 and the pump 84 .

In an exemplary embodiment, an arrangement of tubes or tube bundles may be defined by a plurality of evenly spaced tubes aligned vertically and horizontally, forming an outline that may be generally rectangular. However, it is also possible to use tube bundles in a stacked arrangement, in which the individual tubes are aligned neither vertically nor horizontally, and also in a non-uniformly spaced arrangement.

In another exemplary embodiment, different tube bundle configurations are also contemplated. For example, finned tubes (not shown) may be used in a tube bundle, such as along the uppermost horizontal row or uppermost portion of the tube bundle. In addition to the possibility of using finned tubes, tubes developed for more efficient operation in pool boiling applications, such as in "flooded" evaporators, can also be used. Additionally or in combination with finned tubes, a porous coating may also be applied to the outer surfaces of the individual tubes of the tube bundle.

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

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

Additionally, the expansion functionality of the expansion device of system 14 may be incorporated into distributor 80 . In an exemplary embodiment, two expansion devices may be employed. An expansion device is shown in the spray nozzle of the dispenser 80 . Another expansion device, such as expansion device 36, may provide an initial partial expansion to the refrigerant prior to expansion provided by injection nozzles positioned within the evaporator. In an exemplary embodiment, another expansion device, a non-injection nozzle expansion device, may be controlled by the level of liquid refrigerant 82 in the evaporator to account for changes in operating conditions such as evaporating and condensing pressures and partial cooling load . In an alternative exemplary embodiment, the expansion device may be controlled by the level of liquid refrigerant in the condenser, or in yet another exemplary embodiment, by the level of liquid refrigerant in a "flash economizer" vessel. Liquid level to control the expansion device. In an exemplary embodiment, most of the expansion can occur in the nozzle, providing a larger pressure differential while allowing the nozzle to have a reduced size, thereby reducing nozzle size and cost.

This application refers to other publications including, for example, the dispenser contained in applicant's U.S. Nonprovisional Patent Application No. 12/875,748, filed September 3, 2010, entitled "VAPOR COMPRESSION SYSTEM," which is incorporated by reference method is incorporated into this paper as a whole.

FIG. 7 illustrates an exemplary embodiment of a distributor 142 configured to apply fluid entering the distributor 142 to a tube bundle in a manner similar to that previously shown, for example, in FIG. 6B . The distributor 142 includes an enclosure 144 having one end 148 positioned facing the tube bundle (eg, FIG. 6B ) and an opposite end 150 facing away from the tube bundle. The dispenser 142 also includes an inlet 156 formed in the end 150 and extending between a terminus 152 and an opposite end 154 . End 148 includes an end feature 158 to which at least one dispensing device 146 or a plurality of dispensing devices 146 are operatively associated. In one embodiment, dispensing device 146 includes an opening 160 formed in end feature 158 of end 148 (FIG. 9). Due to this arrangement, the fluid 206 entering the inlet 156 of the enclosure 144 , which may comprise a two-phase mixture of vapor and liquid, is distributed along the length of the enclosure 144 and exits through the distribution device 146 as distribution fluid 208 Encapsulation 144 . Due to the novel configuration of the capsule 144, the flow of the dispensing fluid 208 along the length of the capsule 144 is improved, ie directed to flow more evenly along the length of said capsule.

It should be understood that one, two or more distributors 142 may be used in a single bundle. In one embodiment, two or more dispensers may have overlapping spray angles 166 ( FIG. 11 ) for the dispensed fluid 208 . In one embodiment, the tube bundle may be divided into multiple zones with individual distributors, for example vertically separated zones. For example, for a large tube bundle divided into vertically separated regions, one or more distributors may be provided between each region to provide improved, multi-layer wetting of the tubes of the bundle.

Although the enclosure 144 is shown in FIGS. 7-10 as a multi-piece assembled structure constructed, for example, by welding, it may be extruded, having a unitary or single-piece construction.

10 shows a section through opening 160 formed in end feature 158 of end 148 taken along line 10 - 10 in FIG. 9 . End portion 148 extends to opposing enclosure portions 168 , 170 . As shown in FIG. 10, the enclosure portions 168, 170 are parallel to each other and have a plane of symmetry 180 relative to each other. As further shown in FIG. 10 , the enclosure has a height 176 and a width 178 . The term "aspect ratio of the enclosure" refers to the height 176 divided by its width 178 . The aspect ratio of the capsule may be between about 1/2:1 and about 10:1, between about 1/2:1 and about 8:1, between about 2:1 and about 6:1, about 2:1 and about Between 4:1, between about 2:1 and about 3:1, between about 3:1 and about 8:1, between about 4:1 and about 6:1, about 2:1, about 3:1, about 4:1 or any subcombination thereof. By appropriately sizing the aspect ratio, in combination with the size and spacing of the openings 160, the fluid flow through the openings 160 of the enclosure can be optimized such that the length of the enclosure is comparable to that of the present disclosure. The operation of the dispenser is associated with greater uniformity over substantially the entire fluid pressure range.

For example, as shown collectively in FIGS. 8-10 , the inlet 156 has a length 194 that is between about 1/6 and 1/3 of the length 200 . The inlet 156 is located generally intermediate the opposing end portions 196 , 198 . In one embodiment, adjacent openings 160 formed in end feature 158 of end 148 are spaced apart from one another by substantially the same interval 164 along length 200 . In another embodiment, the spacing 164 between at least some of the adjacent openings 160 connected to the inlet 156 may be greater than the spacing 202 between at least some of the adjacent openings 160 connected to the end portion 196, and/or may be greater than The spacing 204 between at least a portion of adjacent openings 160 connected to the end portion 198 serves to facilitate more uniform flow of fluid through the collective openings 160 along the length 200 of the enclosure 144 . In one embodiment, the spacing 202 between at least some of the adjacent openings 160 connected to the end portion 196 can be substantially evenly spaced relative to the spacing 204 between at least some of the adjacent openings 160 connected to the end portion 198. open. In one embodiment, opening 160 includes a generally uniform width 162 . In one embodiment, the cutout end of opening 160 may be "square" or generally rectangular, although in other embodiments the cutout end may be curved or a combination of curved and straight, having the same shape as End features 158 , 258 , 358 , 458 respectively shown in FIGS. 11-14 are similar in manner, as will be discussed in further detail below. In other embodiments, the opening 160 may have a varying width. Accordingly, it should be understood that the size of the opening 160 corresponds to a combination of the distance 186 (also referred to as the height) from the cutout end of the opening 160 to the point of distal tangency 184 ( FIG. 11 ) of the end feature 158 of the enclosure, and the width 162 (Figure 10). That is, if the widths 162 of the openings 160 are substantially equal to one another, and if the heights or distances 186 of the openings are also substantially equal, the sizes of the openings 160 will be considered substantially equal. In one embodiment, where the widths 162 of the openings 160 differ from one another, the heights or distances 186 of the openings may not be equal to one another, but the dimensions of the openings 160 may be substantially equal to one another as long as the resulting length 200 ( Figure 8) has a substantially uniform fluid flow. In one embodiment, at least two of the openings 160 are substantially equal to each other or substantially equal in size.

Although enclosure portions 168 , 170 are shown generally parallel in FIG. 10 , enclosure portion 168 may include an angular offset 172 and/or enclosure portion 170 may include an angular offset 174 . Accordingly, the enclosure portions 168, 170 may each be offset from parallel by between 0 and about 45 degrees, or any subcombination thereof, forming a "V" shape. In one embodiment, angular offset 172 and/or angular offset 174 may vary along the length of the enclosure, if desired.

FIG. 11 is an enlarged view of area 11 in FIG. 10 showing further details of exemplary end features 158 of enclosure 144 . As further shown in FIG. 11 , feature 158 defines a curvilinear or hemispherical profile having a radius or effective radius or radial distance 189 and extending to opposing enclosure portions 168 , 170 . In one embodiment, the radius or effective radius or radial distance 189 may comprise one or more curves having different radii of curvature. An effective radius or radius or radial distance 189 extends outwardly from a central point or coincident point 181 coincident with a reference line 182 generally perpendicular to the opposing enclosure portions 168 , 170 . As shown in FIG. 10 , capsule portions 168 , 170 are parallel to each other and have a plane of symmetry 180 that is symmetric to each other and, in one embodiment, plane of symmetry 180 coincides with reference line 182 . In one embodiment, coincidence point 181 is not located in the center of enclosure 144 . In one embodiment, the capsule has no plane of symmetry. The opening 160 includes edges 161 , 163 associated with the cutout ends of the opening 160 , the edge 161 being associated with and abutting the enclosure portion 168 , and the edge 163 being associated with and abutting the enclosure portion 170 . As further shown in FIG. 11 , reference line 183 is generally perpendicular to opposing enclosure portions 168 , 170 and extends past edges 161 , 163 . Reference line 182 is parallel to reference line 183 . A distal portion 187 of the end feature 158 of the end 148 relative to the capsule portions 168, 170 includes a distal tangent point 184 coincident with a reference line 185, which is mutually parallel to the reference lines 182, 183. The spacing or effective spacing between edges 161 , 163 of opening 160 to point of tangency 184 of distal portion 187 of end feature 158 , as measured along reference line 185 , yields distance 186 . The spacing between the reference line 182 extending through the coincident point 181 and the point of tangency 184 , as measured along said reference line 185 , yields a distance 188 . Distance 188 is greater than distance 186 . That is, the radius or effective radius or radial distance 189 associated with the distal tangent (e.g., tangent point 184 (distance 188) of end feature 158) is greater than that associated with the distal tangent (e.g., distal tangent point 184). (distance 186 )) the effective spacing or spacing between the associated edges 161 , 163 . Accordingly, the spray angle 166 of 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 180 degrees, between about 160 and about 180 degrees, between about 160 and about 170 degrees, between about 160 and about 165 degrees, about 160 degrees, about 165 degrees and about 170 degrees, the spray Angle 166 remains relatively constant over substantially the entire range of fluid pressures associated with operation of the distributor of the vapor compression system.

FIG. 12 is an enlarged view of an area similar to area 11 of FIG. 10 showing more detail of an exemplary end feature 258 of enclosure 144 . As further shown in FIG. 12 , feature 258 defines a rectangular or rectangular profile formed of linear segments of the enclosure having an effective radius or effective radial distance 289 and extending to opposing enclosure portions 168 , 170 . An effective radius or effective radial distance 289 extends outwardly from a central point or coincident point 281 coincident with a reference line 282 generally perpendicular to the opposing enclosure portions 168 , 170 . In one embodiment, coincidence point 281 is not located in the center of enclosure 144 . In one embodiment, the capsule has no plane of symmetry. The opening 260 includes edges 261 , 263 associated with the cutout ends of the opening 260 , the edge 261 being associated with and abutting against the enclosure portion 168 , and the edge 263 being associated with and abutting against the enclosure portion 170 . As further shown in FIG. 12 , reference line 283 is generally perpendicular to opposing enclosure portions 168 , 170 and extends past edges 261 , 263 . Reference line 282 is parallel to reference line 283 . A distal portion 287 of end feature 258 of end 148 relative to capsule portions 168, 170 includes a distal tangent point 284 coincident with reference line 285, which is mutually parallel to reference lines 282, 283. The spacing or effective spacing between edges 261 , 263 of opening 260 to point of tangency 284 of distal portion 287 of end feature 258 , as measured along reference line 285 , yields distance 286 . The spacing between the reference line 282 extending through the coincidence point 281 and the point of tangency 284 , as measured along said reference line 285 , yields a distance 288 . Distance 288 is greater than distance 286 . That is, the effective radius or effective radial distance 289 associated with the distal tangent (e.g., tangent 284 (distance 288) of end feature 258) is greater than the effective radius or effective radial distance 289 associated with the distal tangent (e.g., tangent 284 (distance 288)). 286)) the effective distance or distance between the relevant edges 161, 163. Accordingly, the spray angle 166 (FIG. 11) of the dispensing fluid flowing through the 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, About 150 degrees to about 180 degrees, about 160 degrees to about 180 degrees, about 160 degrees to about 170 degrees, about 160 degrees to about 165 degrees, about 160 degrees, about 165 degrees and about 170 degrees , the injection angle 166 remains relatively constant over substantially the entire range of fluid pressures associated with operation of the distributor of the vapor compression system.

FIG. 13 is an enlarged view of an area similar to area 11 of FIG. 10 showing more detail of an exemplary end feature 358 of enclosure 144 . As further shown in FIG. 13 , end feature 358 defines a "V"-shaped profile formed by linear segments of the enclosure having an effective radius or effective radial distance 389 and extending to opposing enclosure portions 168, 170. An effective radius or effective radial distance 389 extends outwardly from a central point or coincident point 381 coincident with a reference line 382 generally perpendicular to the opposing enclosure portions 168 , 170 . In one embodiment, coincidence point 381 is not located in the center of enclosure 144 . In one embodiment, the capsule has no plane of symmetry. The opening 360 includes edges 361 , 363 associated with the cutout ends of the opening 360 , the edge 361 being associated with and abutting against the enclosure portion 168 , and the edge 363 being associated with and abutting against the enclosure portion 170 . As further shown in FIG. 13 , reference line 383 is generally perpendicular to opposing enclosure portions 168 , 170 and extends past edges 361 , 363 . Reference line 382 is parallel to reference line 383 . A distal portion 387 of the end feature 358 of the end 148 with respect to the capsule portions 168, 170 includes a distal tangent point 384 coincident with a reference line 385 that is mutually parallel to the reference lines 382, 383. The spacing or effective spacing between edges 361 , 363 of opening 360 to point of tangency 384 of distal portion 387 of end feature 358 , as measured along reference line 385 , yields distance 386 . The spacing between the reference line 382 extending through the coincident point 381 and the point of tangency 384 , as measured along said reference line 385 , yields a distance 388 . Distance 388 is greater than distance 386 . That is, the effective radius or effective radial distance 389 associated with a distal tangency (e.g., tangent point 384 (distance 388) of end feature 358) is greater than that associated with a distal tangency (e.g., distal tangency point 384 (distance 388)). The distance 386)) is the effective distance or distance between the associated edges 361, 363. Accordingly, the spray angle 166 (FIG. 11) of the dispensing fluid flowing through the 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, About 150 degrees to about 180 degrees, about 160 degrees to about 180 degrees, about 160 degrees to about 170 degrees, about 160 degrees to about 165 degrees, about 160 degrees, about 165 degrees and about 170 degrees , the injection angle 166 remains relatively constant over substantially the entire range of fluid pressures associated with operation of the distributor of the vapor compression system.

FIG. 14 is an enlarged view of an area similar to area 11 of FIG. 10 showing more detail of exemplary end features 458 of enclosure 144 . As further shown in FIG. 14, end feature 458 defines a lower "D"-shaped profile formed from a combination of linear and curved sections of the enclosure, having an effective radius or effective radial distance 489, and Extends to opposing enclosure portions 168 , 170 . In one embodiment, different arrangements or profiles of curvilinear and linear segments may be used. An effective radius or effective radial distance 489 extends outwardly from a central point or coincident point 481 coincident with a reference line 482 generally perpendicular to the opposing enclosure portions 168 , 170 . In one embodiment, coincidence point 481 is not located at the center point of enclosure 144 . In one embodiment, the capsule has no plane of symmetry. The opening 460 includes edges 461 , 463 associated with the cutout ends of the opening 460 , the edge 461 being associated with and abutting against the enclosure portion 168 , and the edge 463 being associated with and abutting against the enclosure portion 170 . As further shown in FIG. 13 , reference line 483 is generally perpendicular to opposing enclosure portions 168 , 170 and extends past edges 461 , 463 . Reference line 482 is parallel to reference line 483 . The end feature 458 of the end portion 148 includes a distal tangent point 484 with respect to the distal portion 487 of the capsule portions 168, 170, which coincides with a reference line 485, which is parallel to the reference lines 482, 483. . The spacing or effective spacing between edges 461 , 463 of opening 460 to point of tangency 484 of distal portion 487 of end feature 458 , as measured along reference line 485 , yields distance 486 . The spacing between the reference line 482 extending through the coincident point 481 and the point of abstangent 484 , as measured along said reference line 485 , yields a distance 488 . Distance 488 is greater than distance 486 . That is, the effective radius or effective radial distance 489 associated with a distal tangency (e.g., tangent point 484 (distance 488) of end feature 458) is greater than that associated with a distal tangency (e.g., distal tangency point 484 (distance 488)). The distance 486)) is the effective distance or distance between the associated edges 461, 463. Accordingly, the spray angle 166 (FIG. 11) of 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, About 150 degrees to about 180 degrees, about 160 degrees to about 180 degrees, about 160 degrees to about 170 degrees, about 160 degrees to about 165 degrees, about 160 degrees, about 165 degrees and about 170 degrees , the injection angle 166 remains relatively constant over substantially the entire range of fluid pressures associated with the operation of the distributor of the vapor compression system.

It should be understood that the lines 183 , 283 , 383 , 483 associated with the respective distances 186 , 286 , 386 , 486 are not limited to extending through each respective edge 161 and 163 , 261 and 263 of the respective opening 160 , 260 , 360 , 460 , 361 and 363, 461 and 463. For example, in one embodiment, edges 161 and 163 of opening 160 may be offset relative to line 183 such that line 183 represents an average distance 186 between corresponding edges 161 , 163 . However, the lines 183, 283, 383, 483 and the corresponding respective distances 186, 286, 386, 486 to the respective points of tangency 184, 284, 384, 484 are smaller than the corresponding respective distances between the lines 182, 282, 382, 482 188, 288, 388, 488 and corresponding respective distances 188, 288, 388, 488 to respective tangent points 184, 284, 384, 484 to ensure a consistent controlled spray angle 166 of the dispensed fluid stream (FIG. 11) , for the purposes already described above.

Fig. 15 shows an exemplary embodiment of a distributor 142 having a curved axis 192 as opposed to a linear axis 190, which is different from a distributor having a straight or linear axis (for example, having a differently configured opening 160 (Fig. 8) in combination), the distributor 142 may provide improved liquid distribution for some tube bundle arrangements.

While only some features and embodiments of the present invention have been shown and described, many modifications and changes (for example, in size, dimension, structure, shape and proportion of various elements, and parameter values ( such as temperature, pressure, etc.), mounting arrangement, material usage, color, orientation, etc.), without materially departing from the novel teachings and advantages of the claimed subject matter. The order or sequence of any process or method steps may be varied or rearranged according to alternative embodiments. It is, therefore, to be understood that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the invention. Furthermore, in an effort to provide a concise description of exemplary embodiments, all features of an actual embodiment (i.e., those not related to the best mode presently contemplated for carrying out the invention, or those not related to adequate disclosure of the claimed invention) may not be described. features irrelevant to the invention). It should be appreciated that in the development of any actual implementation, as in any engineering or design project, numerous implementation-specific decisions may be made. Such a development effort might be complex and time consuming, but would nonetheless be a routine task of design, fabrication, and manufacture without undue experimentation for those of ordinary skill having the benefit of this disclosure.

Claims (20)

1., for the distributor in steam compression system, comprising:

Capsule, is configured to be positioned to have in the heat exchanger of tube bank, and described tube bank is included in many pipes of the less horizontal extension in described heat exchanger; And

At least one distributor, be formed at the end be oriented in the face of described tube bank of described capsule, at least one distributor described is configured to the fluid entered in described distributor to be applied in described tube bank;

Wherein said capsule has about 1/2:1 to the length-width ratio about between 10:1.

2. distributor as claimed in claim 1, the described end of wherein said capsule comprises an end features, and at least one distributor described comprises at least one opening be formed in described end features,

With the jet angle distributing fluids between about 60 degree to about 180 degree in the substantially whole fluid pressure range that the operation that at least one opening wherein said was configured and was set to the distributor in described system is relevant.

3. distributor as claimed in claim 2, wherein said end features comprises at least one in curved profile, linear profile or its combination.

4. distributor as claimed in claim 2, comprises the substantial parallel opposite segments extended away from the described end of described capsule.

5. distributor as claimed in claim 4, wherein said opposite segments can from the skew 0 degree that is parallel to each other to about 45 degree.

6. distributor as claimed in claim 4, wherein relevant to described end features and the reference line being essentially perpendicular to the opposite segments of described end features is oriented to the distally tangent portion of first distance from described end features, to the effective spacing relevant existence second distance between the edge be formed at least one opening described and the tangent portion, distally of end features, described first distance is greater than described second distance.

7. distributor as claimed in claim 6, the central point of the effective radius of wherein said reference line and described end features coincides.

8. distributor as claimed in claim 7, the plane of symmetry and the described central point of wherein said capsule coincide.

9. distributor as claimed in claim 1, wherein said length-width ratio at about 2:1 to about between 4:1.

10. distributor as claimed in claim 1, wherein said length-width ratio is about 2:1.

11. distributors as claimed in claim 1, wherein said length-width ratio is about 4:1.

12. distributors as claimed in claim 2, wherein said jet angle is between about 160 degree to about 170 degree.

13. distributors as claimed in claim 2, wherein said jet angle is about 165 degree.

14. distributors as claimed in claim 2, one of them entrance is formed in the end being oriented to away from described tube bank of described capsule, described entrance is configured to receive fluid and enters in described capsule, described entrance is located substantially between two parties relative to the length of described capsule, and described entrance is about 1/6 of the length of described capsule to about 1/3.

15. distributors as claimed in claim 14, at least one distributor wherein said length comprised along described capsule is formed at the multiple openings in described end features.

16. distributors as claimed in claim 15, are wherein formed at the described multiple opening size equalization substantially in described end features.

17. distributors as claimed in claim 14, are wherein formed at the described multiple opening uniform intervals substantially in described end features.

18. distributors as claimed in claim 14, at least one distributor wherein said comprises the multiple openings be formed in described end features, first spacing at least partially with the centre portion of the length corresponding to described capsule of described multiple opening, and second spacing had at least partially corresponding at least one end section in paired end section of the residue opening of described multiple opening, described first spacing is less than described second spacing.

19. 1 kinds, for the distributor in steam compression system, comprising:

Capsule, is configured to be positioned to have in the heat exchanger of tube bank, and described tube bank is included in many pipes of the less horizontal extension in described heat exchanger; And

At least one distributor, be formed in the end being oriented in the face of described tube bank of described capsule, at least one distributor described is configured to the fluid entered in described distributor to be applied in described tube bank;

Wherein said capsule has about 1/2:1 to the length-width ratio about between 10:1;

The described end of wherein said capsule comprises an end features, and at least one distributor described comprises at least one opening be formed in described end features;

With the jet angle distributing fluids between about 60 degree to about 180 degree in the substantially whole fluid pressure range that the operation that at least one opening wherein said was configured and was set to the distributor in described system is relevant.

The method of 20. 1 kinds of distributing fluids in steam compression system, comprising:

There is provided the capsule being configured to be positioned to have in the heat exchanger of tube bank, described tube bank is included in many pipes of the less horizontal extension in described heat exchanger; And

At least one distributor is formed in the end being oriented in the face of described tube bank of described capsule, at least one distributor described is configured to the fluid entered in described distributor to be applied in described tube bank, and wherein said capsule has about 1/2:1 to the length-width ratio about between 10:1; And

Operate described steam compression system.