Patent Publication Number: US-2011056664-A1

Title: Vapor compression system

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application claims priority from and the benefit of U.S. Provisional Application No. 61/240,435, entitled VAPOR COMPRESSION SYSTEM, filed Sep. 8, 2009, which is hereby incorporated by reference. 
    
    
     BACKGROUND 
     The application relates generally to vapor compression systems in refrigeration, air conditioning and chilled liquid systems. The application relates more specifically to distribution systems and methods in vapor compression systems. 
     Conventional chilled liquid systems used in heating, ventilation and air conditioning systems include an evaporator to effect a transfer of thermal energy between the refrigerant of the system and another liquid to be cooled. One type of evaporator includes a shell with a plurality of tubes forming a tube bundle(s) through which the liquid to be cooled is circulated. The refrigerant is brought into contact with the outer or exterior surfaces of the tube bundle inside the shell, resulting in a transfer of thermal energy between the liquid to be cooled and the refrigerant. For example, refrigerant can be deposited onto the exterior surfaces of the tube bundle by spraying or other similar techniques in what is commonly referred to as a “falling film” evaporator. In a further example, the exterior surfaces of the tube bundle can be fully or partially immersed in liquid refrigerant in what is commonly referred to as a “flooded” evaporator. In yet another example, a portion of the tube bundle can have refrigerant deposited on the exterior surfaces and another portion of the tube bundle can be immersed in liquid refrigerant in what is commonly referred to as a “hybrid falling film” evaporator. 
     As a result of the thermal energy transfer with the liquid, the refrigerant is heated and converted to a vapor state, which is then returned to a compressor where the vapor is compressed, to begin another refrigerant cycle. The cooled liquid can be circulated to a plurality of heat exchangers located throughout a building. Warmer air from the building is passed over the heat exchangers where the cooled liquid is warmed, while cooling the air for the building. The liquid warmed by the building air is returned to the evaporator to repeat the process. 
     SUMMARY 
     The present invention relates to a distributor for use in a vapor compression system including an enclosure configured to be positioned in a heat exchanger having a tube bundle comprising a plurality of tubes extending substantially horizontally in the heat exchanger. A plurality of distribution devices are formed in the enclosure, the plurality of distribution devices configured to apply a fluid entering the distributor onto the tube bundle. The enclosure is formed of unitary construction. 
     The present invention further relates to a heat exchanger for use in a vapor compression system including a shell, a tube bundle, a hood, and a distributor. The tube bundle includes a plurality of tubes extending substantially horizontally in the shell. The hood covers and substantially laterally surrounds the tube bundle. The distributor includes an enclosure configured to be positioned in the heat exchanger. A plurality of distribution devices are formed in the enclosure. The plurality of distribution devices is configured to apply a fluid entering the distributor onto the tube bundle. The enclosure is formed of unitary construction. 
    
    
     
       BRIEF DESCRIPTION OF THE FIGURES 
         FIG. 1  shows an exemplary embodiment for a heating, ventilation and air conditioning system. 
         FIG. 2  shows an isometric view of an exemplary vapor compression system. 
         FIGS. 3 and 4  schematically illustrate exemplary embodiments of the vapor compression system. 
         FIG. 5A  shows an exploded, partial cutaway view of an exemplary evaporator. 
         FIG. 5B  shows a top isometric view of the evaporator of  FIG. 5A . 
         FIG. 5C  shows a cross section of the evaporator taken along line  5 - 5  of  FIG. 5B . 
         FIG. 6A  shows a top isometric view of an exemplary evaporator. 
         FIGS. 6B and 6C  show a cross section of the evaporator taken along line  6 - 6  of  FIG. 6A . 
         FIG. 7  shows an exemplary embodiment of an inverted enclosure of a distribution device. 
         FIG. 8  shows a cross section of the enclosure taken along line  8 - 8  of  FIG. 7 . 
         FIG. 9  shows an exemplary embodiment of an inverted enclosure of a distribution device. 
         FIG. 10  shows a cross section of the enclosure taken along line  10 - 10  of  FIG. 9 . 
         FIG. 11  shows an exemplary embodiment of an inverted enclosure with a distribution device. 
         FIG. 12  shows another exemplary embodiment of an inverted enclosure with a distribution device. 
         FIG. 13  shows another exemplary embodiment of an inverted enclosure with a distribution device. 
         FIG. 14  shows yet another exemplary embodiment of an inverted enclosure with a distribution device. 
         FIG. 15  shows another exemplary embodiment of an inverted enclosure with a distribution device. 
         FIG. 16  shows yet another exemplary embodiment of an inverted enclosure with a distribution device. 
     
    
    
     DETAILED DESCRIPTION OF THE EXEMPLARY EMBODIMENTS 
       FIG. 1  shows an exemplary environment for a heating, ventilation and air conditioning (HVAC) system  10  incorporating a chilled liquid system in a building  12  for a typical commercial setting. System  10  can include a vapor compression system  14  that can supply a chilled liquid which may be used to cool building  12 . System  10  can include a boiler  16  to supply heated liquid that may be used to heat building  12 , and an air distribution system which circulates air through building  12 . The air distribution system can also include an air return duct  18 , an air supply duct  20  and an air handler  22 . Air handler  22  can include a heat exchanger that is connected to boiler  16  and vapor compression system  14  by conduits  24 . The heat exchanger in air handler  22  may receive either heated liquid from boiler  16  or chilled liquid from vapor compression system  14 , depending on the mode of operation of system  10 . System  10  is shown with a separate air handler on each floor of building  12 , but it is appreciated that the components may be shared between or among floors. 
       FIGS. 2 and 3  show an exemplary vapor compression system  14  that can be used in an HVAC system, such as HVAC system  10 . Vapor compression system  14  can circulate a refrigerant through a compressor  32  driven by a motor  50 , a condenser  34 , expansion device(s)  36 , and a liquid chiller or evaporator  38 . Vapor compression system  14  can also include a control panel  40  that can include an analog to digital (ND) converter  42 , a microprocessor  44 , a non-volatile memory  46 , and an interface board  48 . Some examples of fluids that may be used as refrigerants in vapor compression system  14  are hydrofluorocarbon (HFC) based refrigerants, for example, R-410A, R-407, R-134a, hydrofluoro olefin (HFO), “natural” refrigerants like 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 use one or more of each of VSDs  52 , motors  50 , compressors  32 , condensers  34  and/or evaporators  38 . 
     Motor  50  used with 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. VSD  52 , if used, receives AC power having a particular fixed line voltage and fixed line frequency from the AC power source and provides power having a variable voltage and frequency to motor  50 . Motor  50  can include any type of electric motor that can be powered by a VSD or directly from an AC or DC power source. For example, motor  50  can be a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor or any other suitable motor type. In an alternate exemplary embodiment, other drive mechanisms such as steam or gas turbines or engines and associated components can be used to drive compressor  32 . 
     Compressor  32  compresses a refrigerant vapor and delivers the vapor to condenser  34  through a discharge line. Compressor  32  can be a centrifugal compressor, screw compressor, reciprocating compressor, rotary compressor, swing link compressor, scroll compressor, turbine compressor, or any other suitable compressor. The refrigerant vapor delivered by compressor  32  to condenser  34  transfers heat to a fluid, for example, water or air. The refrigerant vapor condenses to a refrigerant liquid in condenser  34  as a result of the heat transfer with the fluid. The 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 evaporator  38  absorbs heat from another fluid, which may or may not be the same type of fluid used for condenser  34 , and undergoes a phase change to a refrigerant vapor. In the exemplary embodiment shown in  FIG. 3 , evaporator  38  includes a tube bundle having a supply line  60 S and a return line  60 R connected to a cooling load  62 . A process fluid, for example, water, ethylene glycol, calcium chloride brine, sodium chloride brine, or any other suitable liquid, enters evaporator  38  via return line  60 R and exits evaporator  38  via supply line  60 S. Evaporator  38  chills the temperature of the process fluid in the tubes. The tube bundle in evaporator  38  can include a plurality of tubes and a plurality of tube bundles. The vapor refrigerant exits evaporator  38  and returns to compressor  32  by a suction line to complete the cycle. 
       FIG. 4 , which is similar to  FIG. 3 , shows the refrigerant circuit with an intermediate circuit  64  that may be incorporated between condenser  34  and expansion device  36  to provide increased cooling capacity, efficiency and performance. Intermediate circuit  64  has an inlet line  68  that can be either connected directly to or can be in fluid communication with condenser  34 . As shown, inlet line  68  includes an expansion device  66  positioned upstream of an intermediate vessel  70 . Intermediate vessel  70  can be a flash tank, also referred to as a flash intercooler, in an exemplary embodiment. In an alternate exemplary embodiment, intermediate vessel  70  can be configured as a heat exchanger or a “surface economizer.” In the flash intercooler arrangement, a first expansion device  66  operates to lower the pressure of the liquid received from condenser  34 . During the expansion process in a flash intercooler, a portion of the liquid is evaporated. Intermediate vessel  70  may be used to separate the evaporated vapor from the liquid received from the condenser. The evaporated liquid may be drawn by compressor  32  to a port at a pressure intermediate between suction and discharge or at an intermediate stage of compression, through a line  74 . The liquid that is not evaporated is cooled by the expansion process, and collects at the bottom of intermediate vessel  70 , where the liquid is recovered to flow to the evaporator  38 , through a line  72  comprising a second expansion device  36 . 
     In the “surface intercooler” arrangement, the implementation is slightly different, as known to those skilled in the art. Intermediate circuit  64  can operate in a similar matter to that described above, except that instead of receiving the entire amount of refrigerant from condenser  34 , as shown in  FIG. 4 , intermediate circuit  64  receives only a portion of the refrigerant from condenser  34  and the remaining refrigerant proceeds directly to expansion device  36 . 
       FIGS. 5A-5C  show an exemplary embodiment of an evaporator configured as a “hybrid falling film” evaporator. As shown in  FIGS. 5A-5C , an evaporator  138  includes a substantially cylindrical shell  76  with a plurality of tubes forming a tube bundle  78  extending substantially horizontally along the length of shell  76 . At least one support  116  may be positioned inside shell  76  to support the plurality of tubes in tube bundle  78 . A suitable fluid, such as water, ethylene, ethylene glycol, or calcium chloride brine flows through the tubes of tube bundle  78 . A distributor  80  positioned above tube bundle  78  distributes, deposits or applies refrigerant  110  from a plurality of positions onto the tubes in tube bundle  78 . In one exemplary embodiment, the refrigerant deposited by distributor  80  can be entirely liquid refrigerant, although in another exemplary embodiment, the refrigerant deposited by distributor  80  can include both liquid refrigerant and vapor refrigerant. 
     Liquid refrigerant that flows around the tubes of tube bundle  78  without changing state collects in the lower portion of shell  76 . The collected liquid refrigerant can form a pool or reservoir of liquid refrigerant  82 . The deposition positions from distributor  80  can include any combination of longitudinal or lateral positions with respect to tube bundle  78 . In another exemplary embodiment, deposition positions from distributor  80  are not limited to ones that deposit onto the upper tubes of tube bundle  78 . Distributor  80  may include a plurality of nozzles supplied by a dispersion source of the refrigerant. In an exemplary embodiment, the dispersion source is a tube connecting a source of refrigerant, such as condenser  34 . Nozzles include spraying nozzles, but also include machined openings that can guide or direct refrigerant onto the surfaces of the tubes. The nozzles may apply refrigerant in a predetermined pattern, such as a jet pattern, so that the upper row of tubes of tube bundle  78  are covered. The tubes of tube bundle  78  can be arranged to promote the flow of refrigerant in the form of a film around the tube surfaces, the liquid refrigerant coalescing to form droplets or in some instances, a curtain or sheet of liquid refrigerant at the bottom of the tube surfaces. The resulting sheeting promotes wetting of the tube surfaces which enhances the heat transfer efficiency between the fluid flowing inside the tubes of tube bundle  78  and the refrigerant flowing around the surfaces of the tubes of tube bundle  78 . 
     In the pool of liquid refrigerant  82 , a tube bundle  140  can be immersed or at least partially immersed, to provide additional thermal energy transfer between the refrigerant and the process fluid to evaporate the pool of liquid refrigerant  82 . In an exemplary embodiment, tube bundle  78  can be positioned at least partially above (that is, at least partially overlying) tube bundle  140 . In one exemplary embodiment, evaporator  138  incorporates a two pass system, in which the process fluid that is to be cooled first flows inside the tubes of tube bundle  140  and then is directed to flow inside the tubes of tube bundle  78  in the opposite direction to the flow in tube bundle  140 . In the second pass of the two pass system, the temperature of the fluid flowing in tube bundle  78  is reduced, thus requiring a lesser amount of heat transfer with the refrigerant flowing over the surfaces of tube bundle  78  to obtain a desired temperature of the process fluid. 
     It is to be understood that although a two pass system is described in which the first pass is associated with tube bundle  140  and the second pass is associated with tube bundle  78 , other arrangements are contemplated. For example, evaporator  138  can incorporate a one pass system where the process fluid flows through both tube bundle  140  and tube bundle  78  in the same direction. Alternatively, evaporator  138  can incorporate a three pass system in which two passes are associated with tube bundle  140  and the remaining pass associated with tube bundle  78 , or in which one pass is associated with tube bundle  140  and the remaining two passes are associated with tube bundle  78 . Further, evaporator  138  can incorporate an alternate two pass system in which one pass is associated with both tube bundle  78  and tube bundle  140 , and the second pass is associated with both tube bundle  78  and tube bundle  140 . In one exemplary embodiment, tube bundle  78  is positioned at least partially above tube bundle  140 , with a gap separating tube bundle  78  from tube bundle  140 . In a further exemplary embodiment, hood  86  overlies tube bundle  78 , with hood  86  extending toward and terminating near the gap. In summary, any number of passes in which each pass can be associated with one or both of tube bundle  78  and tube bundle  140  is contemplated. 
     An enclosure or hood  86  is positioned over tube bundle  78  to substantially prevent cross flow, that is, a lateral flow of vapor refrigerant or liquid and vapor refrigerant  106  between the tubes of tube bundle  78 . Hood  86  is positioned over and laterally borders tubes of tube bundle  78 . Hood  86  includes an upper end  88  positioned near the upper portion of shell  76 . Distributor  80  can be positioned between hood  86  and tube bundle  78 . In yet a further exemplary embodiment, distributor  80  may be positioned near, but exterior of, hood  86 , so that distributor  80  is not positioned between hood  86  and tube bundle  78 . However, even though distributor  80  is not positioned between hood  86  and tube bundle  78 , the nozzles of distributor  80  are still configured to direct or apply refrigerant onto surfaces of the tubes. Upper end  88  of hood  86  is configured to substantially prevent the flow of applied refrigerant  110  and partially evaporated refrigerant, that is, liquid and/or vapor refrigerant  106  from flowing directly to outlet  104 . Instead, applied refrigerant  110  and refrigerant  106  are constrained by hood  86 , and, more specifically, are forced to travel downward between walls  92  before the refrigerant can exit through an open end  94  in the hood  86 . Flow of vapor refrigerant  96  around hood  86  also includes evaporated refrigerant flowing away from the pool of liquid refrigerant  82 . 
     It is to be understood that at least the above-identified, relative terms are non-limiting as to other exemplary embodiments in the disclosure. For example, hood  86  may be rotated with respect to the other evaporator components previously discussed, that is, hood  86 , including walls  92 , is not limited to a vertical orientation. Upon sufficient rotation of hood  86  about an axis substantially parallel to the tubes of tube bundle  78 , hood  86  may no longer be considered “positioned over” nor to “laterally border” tubes of tube bundle  78 . Similarly, “upper” end  88  of hood  86  may no longer be near “an upper portion” of shell  76 , and other exemplary embodiments are not limited to such an arrangement between the hood and the shell. In an exemplary embodiment, hood  86  terminates after covering tube bundle  78 , although in another exemplary embodiment, hood  86  further extends after covering tube bundle  78 . 
     After hood  86  forces refrigerant  106  downward between walls  92  and through open end  94 , the vapor refrigerant undergoes an abrupt change in direction before traveling in the space between shell  76  and walls  92  from the lower portion of shell  76  to the upper portion of shell  76 . Combined with the effect of gravity, the abrupt directional change in flow results in a proportion of any entrained droplets of refrigerant colliding with either liquid refrigerant  82  or shell  76 , thereby removing those droplets from the flow of vapor refrigerant  96 . Also, refrigerant mist traveling along the length of hood  86  between walls  92  is coalesced into larger drops that are more easily separated by gravity, or maintained sufficiently near or in contact with tube bundle  78 , to permit evaporation of the refrigerant mist by heat transfer with the tube bundle. As a result of the increased drop size, the efficiency of liquid separation by gravity is improved, permitting an increased upward velocity of vapor refrigerant  96  flowing through the evaporator in the space between walls  92  and shell  76 . Vapor refrigerant  96 , whether flowing from open end  94  or from the pool of liquid refrigerant  82 , flows over a pair of extensions  98  protruding from walls  92  near upper end  88  and into a channel  100 . Vapor refrigerant  96  enters into channel  100  through slots  102 , which is the space between the ends of extensions  98  and shell  76 , before exiting evaporator  138  at an outlet  104 . In another exemplary embodiment, vapor refrigerant  96  can enter into channel  100  through openings or apertures formed in extensions  98 , instead of slots  102 . In yet another exemplary embodiment, slots  102  can be formed by the space between hood  86  and shell  76 , that is, hood  86  does not include extensions  98 . 
     Stated another way, once refrigerant  106  exits from hood  86 , vapor refrigerant  96  then flows from the lower portion of shell  76  to the upper portion of shell  76  along the prescribed passageway. In an exemplary embodiment, the passageways can be substantially symmetric between the surfaces of hood  86  and shell  76  prior to reaching outlet  104 . In an exemplary embodiment, baffles, such as extensions  98  are provided near the evaporator outlet to prevent a direct path of vapor refrigerant  96  to the compressor inlet. 
     In one exemplary embodiment, hood  86  includes opposed substantially parallel walls  92 . In another exemplary embodiment, walls  92  can extend substantially vertically and terminate at open end  94 , that is located substantially opposite upper end  88 . Upper end  88  and walls  92  are closely positioned near the tubes of tube bundle  78 , with walls  92  extending toward the lower portion of shell  76  so as to substantially laterally border the tubes of tube bundle  78 . In an exemplary embodiment, walls  92  may be spaced between about 0.02 inch (0.5 mm) and about 0.8 inch (20 mm) from the tubes in tube bundle  78 . In a further exemplary embodiment, walls  92  may be spaced between about 0.1 inch (3 mm) and about 0.2 inch (5 mm) from the tubes in tube bundle  78 . However, spacing between upper end  88  and the tubes of tube bundle  78  may be significantly greater than 0.2 inch (5 mm), in order to provide sufficient spacing to position distributor  80  between the tubes and the upper end of the hood. In an exemplary embodiment in which walls  92  of hood  86  are substantially parallel and shell  76  is cylindrical, walls  92  may also be symmetric about a central vertical plane of symmetry of the shell bisecting the space separating walls  92 . In other exemplary embodiments, walls  92  need not extend vertically past the lower tubes of tube bundle  78 , nor do walls  92  need to be planar, as walls  92  may be curved or have other non-planar shapes. Regardless of the specific construction, hood  86  is configured to channel refrigerant  106  within the confines of walls  92  through open end  94  of hood  86 . 
       FIGS. 6A-6C  show an exemplary embodiment of an evaporator configured as a “falling film” evaporator  128 . As shown in  FIGS. 6A-6C , evaporator  128  is similar to evaporator  138  shown in  FIGS. 5A-5C , except that evaporator  128  does not include tube bundle  140  in the pool of refrigerant  82  that collects in the lower portion of the shell. In an exemplary embodiment, hood  86  terminates after covering tube bundle  78 , although in another exemplary embodiment, hood  86  further extends toward pool of refrigerant  82  after covering tube bundle  78 . In yet a further exemplary embodiment, hood  86  terminates so that the hood does not totally cover the tube bundle, that is, substantially covers the tube bundle. 
     As shown in  FIGS. 6B and 6C , a pump  84  can be used to recirculate the pool of liquid refrigerant  82  from the lower portion of the shell  76  via line  114  to distributor  80 . As further shown in  FIG. 6B , line  114  can include a regulating device  112  that can be in fluid communication with a condenser (not shown). In another exemplary embodiment, an ejector (not shown) can be employed to draw liquid refrigerant  82  from the lower portion of shell  76  using the pressurized refrigerant from condenser  34 , which operates by virtue of the Bernoulli effect. The ejector combines the functions of a regulating device  112  and a pump  84 . 
     In an exemplary embodiment, one arrangement of tubes or tube bundles may be defined by a plurality of uniformly spaced tubes that are aligned vertically and horizontally, forming an outline that can be substantially rectangular. However, a stacking arrangement of tube bundles can be used where the tubes are neither vertically or horizontally aligned, as well as arrangements that are not uniformly spaced. 
     In another exemplary embodiment, different tube bundle constructions are contemplated. For example, finned tubes (not shown) can be used in a tube bundle, such as along the uppermost horizontal row or uppermost portion of the tube bundle. Besides the possibility of using finned tubes, tubes developed for more efficient operation for pool boiling applications, such as in “flooded” evaporators, may also be employed. Additionally, or in combination with the finned tubes, porous coatings can also be applied to the outer surface of the tubes of the tube bundles. 
     In a further exemplary embodiment, the cross-sectional profile of the evaporator shell may be non-circular. 
     In an exemplary embodiment, a portion of the hood may partially extend into the shell outlet. 
     In addition, it is possible to incorporate the expansion functionality of the expansion devices of system  14  into distributor  80 . In one exemplary embodiment, two expansion devices may be employed. One expansion device is exhibited in the spraying nozzles of distributor  80 . The other expansion device, for example, expansion device  36 , can provide a preliminary partial expansion of refrigerant, before that provided by the spraying nozzles positioned inside the evaporator. In an exemplary embodiment, the other expansion device, that is, the non-spraying nozzle expansion device, can be controlled by the level of liquid refrigerant  82  in the evaporator to account for variations in operating conditions, such as evaporating and condensing pressures, as well as partial cooling loads. In an alternative exemplary embodiment, expansion device can be controlled by the level of liquid refrigerant in the condenser, or in a further exemplary embodiment, a “flash economizer” vessel. In one exemplary embodiment, the majority of the expansion can occur in the nozzles, providing a greater pressure difference, while simultaneously permitting the nozzles to be of reduced size, therefore reducing the size and cost of the nozzles. 
       FIGS. 7-16  show respective enclosures or housings  148 ,  150 ,  152 ,  154 ,  156 ,  158 ,  160 ,  162  for a distributor. For simplicity, the term “the enclosures” may refer at least to any of the exemplary embodiments shown in  FIGS. 7-16  or described in the present disclosure. The enclosures can have a predetermined shape, such as, but not limited to, a rectangular, diamond, circular, cylindrical and/or square shape for improving refrigerant flow to tube bundle  78 . Any suitable shape may be used for the enclosures, so long as refrigerant flow  106  can be maintained through the enclosure. Inlets (not shown) may be located at an upper portion of enclosure or at the ends of enclosure. Distribution devices  130 , such as nozzles, holes, or openings, including slotted openings sometimes referred to as slits, can be formed or located on a bottom portion, side portion, or other suitable location of the enclosure to allow refrigerant  110  to flow onto tube bundles  78 . Distribution devices  130  may also be formed or located close together, if multiple distribution devices  130  are formed or located in the enclosure. Distribution devices  130  may be arranged in a strategic organized pattern or distribution devices  130  may be arranged in a varying or scattered pattern along the enclosure. In one embodiment, a scattered pattern of distribution devices  130  includes a random pattern of distribution devices. 
     Distribution devices  130  may be formed at an angle in relation to the sides of the enclosure, such as a V-shaped notch formed in a flat surface, in which the V-shaped notch may be oriented perpendicular to the surface. In one embodiment, the V-shaped notch may be formed in a flat surface in which the centerline of the notch is not oriented perpendicular to the surface. Alternately, for shapes having arguably one continuous surface, such as a circular shape, such as a circular cylinder, the V-shaped notch may be radially oriented in the circular shape, in which the center line of the V-shaped notch may extend in a direction that is parallel to a line directed through the center axis of the cylinder, although in other embodiments, the centerline of the V-shaped notch may not align with the center axis. In a further alternate arrangement, the V-shaped notch may be oriented in a direction that is perpendicular to the center axis of the cylinder, such as shown in  FIG. 11 . It is to be understood that in a further embodiment, the V-shaped notch may be oriented in a direction that is between a radially oriented position and a perpendicularly oriented position with respect to the center axis of the cylinder, or the sides of enclosure that is non-circular or non-cylindrical. It is to be understood that notches may define profiles that are not V-shaped. 
     As shown in  FIGS. 7-8 , distribution devices  130  may be arranged substantially perpendicular to the length of enclosure  148 . In one embodiment, distribution devices  130  may be formed by a blade of a cutting tool, such as a cutting tool having a rotating blade, in which the orientation of the distribution device (openings formed by the cutting tool) may be aligned with a linear arrangement of openings formed in the enclosure. However, in another embodiment, distribution devices  130  may be arranged in substantial alignment with respect to the length of the enclosure. In a further embodiment (not shown), distribution devices  130  may be positioned in a non-linear arrangement, and in yet another embodiment (not shown), in addition to distribution devices  130  being positioned in a nonlinear arrangement, the shape of the enclosure may extend nonlinearly, such as a curve. 
     The enclosures shown in  FIGS. 7-16  may contain a variety of distribution devices  130 , if desired, to provide refrigerant flow to tube bundle  78 . The enclosure may include at least one distribution device  130  that is a nozzle, at least one distribution device  130  that is formed in the enclosure, at least one distribution device  130  being arranged in a strategic pattern with another distribution device  130 , another distribution device  130  being arranged in a varying pattern or non-pattern with another distribution device  130  and/or another distribution device  130  that is formed or disposed at an angle in relation to another distribution device  130  or in relation to the sides of enclosure, and any combination thereof. In other words, distribution devices  130  can be located and formed in enclosure in such a manner to provide a uniform distribution of applied refrigerant  110  to tube bundles  78 , even if the arrangement of distribution devices  130  includes a variety of nozzles, formations, and patterns on the enclosure. A uniform distribution of applied refrigerant  110  on tube bundles  78  provides improved heat transfer and cooling to tube bundles  78 . 
     Relative spacial terms such as upper, lower, horizontal, inverted and the like, are not intended to be limiting, but are provided to assist with providing an understanding of the disclosure. 
     Other exemplary embodiments of the enclosures may include openings (not shown) in the upper portion of the enclosure to allow for the flow of vapor refrigerant from the enclosure. In an exemplary embodiment, distribution devices  130  may be formed by a cutting tool, such as a cutting tool with a rotating blade or reciprocating blade, or may be formed by other methods, such as a press. For example, an axial internal hole or opening may be drilled in the enclosure using a drill bit or other device with a rounded or tapered end. From the outside of the enclosure, the rounded or tapered end of the internal hole may be intersected with a notch that has a V-shape. In a further exemplary embodiment, distribution devices  130  may be formed in the enclosure prior to the enclosure being formed into a final shape. In each of these distribution device embodiments, the enclosure is formed of unitary construction. That is, such as in these embodiments, the enclosure contains a single part. 
     Referring specifically to  FIGS. 7 and 8 , enclosure  148  is shown in an inverted position, having a diamond shaped cross-section.  FIGS. 9 and 10  show enclosure  150  in an inverted position, having an irregular hexagon shaped cross section. The irregular hexagon cross section shape may be similar to a rectangular shape, having the bottom corners angled, forming a hexagon, rather than a rectangle, as shown in  FIG. 10 . Enclosures  148  and  150  are located above tube bundles (not shown) such that refrigerant  110  can be applied to tube bundles  78  to provide heat transfer to tube bundles (not shown). When located above tube bundles  78 , distribution devices  130  may be positioned on the bottom surface, or in other words, distribution devices  130  provide a flow path for refrigerant  106  such that refrigerant  106  flows from enclosures  148  and  150  downward onto tube bundles. Distribution devices  130  are shown as being formed in enclosures  148  and  150 . Distribution devices  130  may be a separate device such as a nozzle and placed in enclosures  148  and  150  during or after manufacture of enclosures  148  and  150 . Distribution devices  130  are shown as having substantially parallel walls to provide a flow path for refrigerant  106 . Distribution devices  130  may have non-parallel walls, or any other suitable shape for providing a flow path for refrigerant  106  from enclosures  148  and  150  are to tube bundles  78 . In a further embodiment, the enclosure may extend nonlinearly.  FIGS. 7 ,  8 ,  9 , and  10  show three sets of distribution devices  130  formed on each bottom surface  144  of enclosure  148  and enclosure  150 , however any suitable number of distribution devices  130  may be formed or located in enclosures  148  and  150  to provide a flow path for refrigerant  106  to tube bundles  78 . For example, enclosure  150  may include distribution devices  130  formed along the bottom corners of enclosure  150 . Enclosures  148  and  150  may also include openings (not shown) on the top surface or surfaces  146  to provide ventilation of vapor refrigerant from enclosures  148  and  150 . 
     Referring specifically to  FIG. 11 , enclosure  152  is shown in an inverted position.  FIG. 11  shows enclosure  152  having a cylindrical shape with a circular cross section, however enclosure  152  may have any suitable shape, with any suitable cross section, such as the shape and cross section of any other embodiment disclosed herein. Enclosure  152  is located above tube bundles (not shown) such that refrigerant  110  can be applied to tube bundles  78  to provide heat transfer to tube bundles (not shown). When located above tube bundles  78 , distribution device(s) may be positioned on the bottom surface, or in other words, distribution devices  130  provide a flow path for refrigerant  106  such that refrigerant  106  flows from enclosure  152  downward onto tube bundles  78 . Distribution devices  130  may be located on any suitable location on enclosure  152 , for example, the side surfaces. Alternately, for shapes having arguably one continuous surface, such as a circular shape, distribution devices  130  may be positioned at different locations along the periphery of the enclosure. Refrigerant  106  flows through enclosure  152 , and at least a portion of refrigerant  106  passes through distribution devices  130  and onto tube bundles  78 . 
     Distribution devices  130  are shown as being formed in enclosure  152 , however distribution devices  130  may be a separate device such as a nozzle, and placed in enclosure  152  during or after manufacture. Distribution devices  130  are shown as having been formed with a V-shaped cut or V-notch, or vertical rounded end mill cut or notch, however distribution devices  130  may have any other suitable shape for providing a flow path for refrigerant  106  from enclosure  130  to tube bundles  78 , such as the distribution devices shown in  FIGS. 12 and 13 .  FIG. 12  shows a distribution device  130  having being formed with a horizontal V-shaped cut or V-notch in enclosure  154  with a narrower opening than distribution device  130  shown in  FIG. 11 . Referring specifically to  FIG. 13 , enclosure  156  is shown having a distribution device  130  having been formed with a horizontal saw cut with substantially parallel sides. Enclosures  152 ,  154 , and  156  shown in  FIGS. 11 ,  12  and  13  may have any other suitably shaped formation of distribution devices  130  to provide a flow path for refrigerant  106  from enclosures  152 ,  154 , and  156  to tube bundles  78 . 
     Referring specifically to  FIG. 14 ,  FIG. 14  shows an inverted enclosure  158  similar to the enclosures  152 ,  154 , and  156  shown in  FIGS. 11 ,  12 , and  13 . However,  FIG. 14  shows enclosure  158  having a rectangular or square shaped cross section. Enclosure  158  may have any suitable shape with any suitable cross section, such as the shape and cross section of any other embodiment disclosed herein.  FIG. 14  shows a distribution device  130  formed with a V-shaped cut or V-notch on each of the lower corners of the square, although distribution devices  130  may have substantially parallel walls, as shown as formed in enclosure  160  in  FIG. 15 . Enclosures  158  and  160  shown in  FIGS. 14 and 15  may have any other suitably shaped formation of distribution devices  130  to provide a flow path for refrigerant  106  from enclosures  158  and  160  to tube bundles  78 . Distribution devices  130  may also be formed or located on other areas of enclosures  158  and  160  and not on only the lower corners as shown in  FIGS. 14 and 15 . 
     Referring specifically to  FIG. 16 , enclosure  162  is similar to enclosures shown in  FIGS. 7 ,  11 ,  12 ,  13 ,  14 , and  15 . Enclosure  162  is in an inverted position having a diamond shaped cross section. Distribution devices are shown as being formed in enclosure  162  on the bottom angle surface of the diamond shape, or in other words, distribution devices  130  provide a flow path for refrigerant  106  such that refrigerant  106  flows from enclosure  162  downward onto tube bundles  78 . Distribution devices  130  may also be located on any suitable location on enclosure  162 , for example, the sides. Refrigerant  106  flows through enclosure  162 , and at least a portion of refrigerant  106  passes through distribution devices  130  and onto tube bundles  78 . Distribution devices  130  are shown as being formed in enclosure  162 , however, distribution devices  130  may be a separate device such as a nozzle, and placed in enclosure  162 . Distribution devices  130  are shown as having being formed with a horizontal V-shaped cut or V-notch, however distribution devices  130  may have substantially parallel walls or any other suitable shaped formation to provide a flow path for refrigerant  106  from enclosure  162  to tube bundles  78 .  FIG. 16  may include any number of distribution devices  130  formed in enclosure  162  to provide a flow path for refrigerant  106  to tube bundles  78 . 
     Although distribution devices  130  may be formed at substantially forty five degrees to a horizontal axis of the enclosures, distribution devices  130  may be formed at any angle other than forty five degrees to the horizontal axis to provide liquid distribution to tube bundles. Stated another way, one side of the distribution device may be formed at any angle between zero and ninety degrees to a surface of the enclosure or with respect to the direction (or length) of the enclosure. 
     While only certain features and embodiments of the invention have been shown and described, many modifications and changes may occur to those skilled in the art (e.g., variations in sizes, dimensions, structures, shapes and proportions of the various elements, values of parameters (e.g., temperatures, pressures, etc.), mounting arrangements, use of materials, colors, orientations, etc.) without materially departing from the novel teachings and advantages of the subject matter recited in the claims. The order or sequence of any process or method steps may be varied or re-sequenced 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 the exemplary embodiments, all features of an actual implementation may not have been described (i.e., those unrelated to the presently contemplated best mode of carrying out the invention, or those unrelated to enabling the claimed invention). It should be appreciated that in the development of any such 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 nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure, without undue experimentation.