Patent Publication Number: US-6904770-B2

Title: Multi-function condenser

Description:
BACKGROUND OF THE INVENTION 
   1. Field of the Invention 
   The subject invention relates to a multi-function condenser for use in an air conditioning system of a motor vehicle. More specifically, the subject invention relates to a multi-function condenser that transfers heat directly between refrigerant flowing from an evaporator and refrigerant flowing from a condenser. 
   2. Description of the Prior Art 
   A condenser for an air conditioning system of a motor vehicle is known in the art. In fact, a condenser having an integral receiver has been documented for use in air conditioning systems, which also include a refrigerant, a refrigerant compressor, an expansion device, and an evaporator. The receiver receives and stores condensed refrigerant from the condenser for flow into the expansion device where the refrigerant is allowed to expand. 
   A suction line of the air conditioning system extends between the evaporator and the compressor to return the refrigerant from the evaporator, where the refrigerant is essentially a gas, through the suction line and to the compressor for re-circulation. It is well known that the refrigerant flowing through the suction line is much cooler than refrigerant in the receiver, which in turn is cooler than refrigerant flowing in the condenser. 
   The refrigerant flowing through the suction line is pressurized by the compressor, which heats the refrigerant, before flowing into the condenser. This is done so that the refrigerant can be condensed into a liquid state by cooling the refrigerant with ambient air, regardless of a temperature of the ambient air. Because of the high pressure of the refrigerant in the condenser, the refrigerant may be condensed even at relatively high temperatures. A differential between energy of the refrigerant flowing into the compressor and a desired energy of the refrigerant flowing out of the compressor dictates an amount of energy the that the compressor must add to the refrigerant. 
   Refrigerant flows through the condenser to be sufficiently cooled and condensed into a liquid state before flowing to the evaporator. A temperature of the refrigerant exiting the condenser correlates to how cool the refrigerant can get when flowing through the expansion device, where the liquid refrigerant vaporizes and absorbs heat. Thus, it is advantageous to remove as much heat as possible from the refrigerant in the condenser to condense the refrigerant and to lower the energy of the refrigerant as much as possible. 
   Consequently, conventional air conditioning systems waste energy by thermodynamically separating the refrigerant flowing through the suction line, which must be energized, and the refrigerant flowing through the receiver and the condenser, which must be de-energized. 
   Furthermore, conventional air conditioning systems are expensive because the systems require the evaporator, the condenser, the compressor, the receiver, and all connecting lines be assembled during production, resulting in a lengthy assembly time, thus presenting a high cost not only for parts but for manpower to assemble the system. With so many components, there is a tendency toward misassembly of the systems. Such assembly also presents plumbing problems, with many points where leaks could develop within the system. 
   In addition, air conditioning systems generally produce pressure pulsations in the refrigerant as the refrigerant vaporizes in the evaporator. The pressure pulsations travel through the refrigerant flowing through the suction line and create noise that may be audible outside of the air conditioning system. The air conditioning systems require a muffler to attenuate the pressure pulsations and reduce noise. The mufflers add cost to production of the air conditioning systems. 
   Due to the inadequacies of the prior art, including those described above, it is desirable to provide a condenser that is multi-functional. More specifically, it is desirable to provide a condenser that, in addition to having an integral receiver, incorporates a conduit disposed in the suction line and passing through the condenser to transfer heat energy between the refrigerant in the condenser and the refrigerant in the suction line. It is also desirable to provide a condenser that is multi-functional to decrease an overall cost of the air conditioning system by eliminating a need for a muffler, while inhibiting misassembly by reducing parts and reducing assembly time for the system. 
   SUMMARY OF THE INVENTION AND ADVANTAGES 
   A condenser for an air conditioning system is disclosed. The condenser includes a first header, a second header, a plurality of tubes, and a conduit. The tubes extend in parallel relationship between the headers for establishing fluid communication between the first header and the second header. The conduit extends into and out of and is surrounded by the second header. A space is defined between the conduit and the second header for transferring heat between refrigerant flowing in the second header and the conduit as refrigerant flows through the conduit independently of refrigerant flowing in the space in the second header surrounding the conduit. 
   Accordingly, the subject invention provides the multi-function condenser that, in addition to condensing the refrigerant, includes the conduit passing through the condenser, specifically the second header, to extract heat energy from refrigerant flowing through the condenser and to add heat energy to the refrigerant flowing through the conduit to a compressor. 
   The subject invention further provides the multi-functional condenser that incorporates multiple parts of the air conditioning system, such as the receiver and an expansion device, to decrease an overall cost of the system. By including the multiple parts in the condenser, assembly time is reduced, a tendency toward misassembly is inhibited, a number of points where leaks could develop are decreased, and accessibility to the parts is improved. 
   The subject invention further attenuates pressure pulsations in the refrigerant flowing through the conduit to eliminate a need for a separate muffler, thus further reducing cost for the system. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     Other advantages of the present invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein: 
       FIG. 1  is a schematic view of an air conditioning system illustrating a compressor, an evaporator, and a multi-function condenser; 
       FIG. 2  is a front view of the multi-function condenser of  FIG. 1 ; 
       FIG. 3  is a partially cross-sectional side view of the multi-function condenser of  FIG. 1 ; 
       FIG. 4  is a schematic view of an air conditioning system illustrating a compressor, an evaporator, and an alternative embodiment of the multi-function condenser; 
       FIG. 5  is a front view of the alternative multi-function condenser of  FIG. 4 ; 
       FIG. 6  is a partially cross-sectional side view of the alternative multi-function condenser of  FIG. 4 ; and 
       FIG. 7  is a cross-sectional top view of a second header of the multi-function condenser. 
   

   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
   Referring to the Figures, wherein like numerals indicate like or corresponding parts throughout the several views, a multi-function condenser is generally disclosed at  10 . For descriptive purposes only, the multi-function condenser  10  is hereinafter referred to as “the condenser”. 
   Referring specifically to  FIG. 1 , the condenser  10  is used in an air conditioning system, which is shown generally at  12 . The air conditioning system  12  includes an evaporator  14  for vaporizing a refrigerant flowing into the evaporator  14  to cool air that is flowing around an exterior of the evaporator  14 . A compressor  16  pressurizes the refrigerant flowing into the compressor  16 , which heats the refrigerant to a temperature that is much higher than ambient air temperatures, even on relatively hot days. This allows the condenser  10  to condense the refrigerant into a liquid state by removing heat from the refrigerant with the ambient air. Because of the increased pressure of the refrigerant in the condenser  10 , the refrigerant may be condensed even at relatively high temperatures. A suction line  18  is disposed between the evaporator  14  and the compressor  16 . The refrigerant flows through the suction line  18  from the evaporator  14  to the compressor  16 . A pressurized refrigerant line  20  is disposed between the compressor  16  and the condenser  10 . The refrigerant flows from the compressor  16  through the pressurized refrigerant line  20  to the condenser  10 , where a phase of the refrigerant changes from a vapor to a liquid due to the removal of heat by the condenser  10 . An evaporator inlet line  22  is disposed between the condenser  10  and the evaporator  14 . The refrigerant flows from the condenser  10  through the evaporator inlet line  22  to the evaporator  14  to allow for a repetitious cycle of heating and cooling of the refrigerant flowing through the system  12 . 
   The condenser  10  includes a first header  24 , a second header  26 , and a plurality of tubes  28  extending in parallel relationship between the headers  24 ,  26  for establishing fluid communication between the first header  24  and the second header  26 . A plurality of dividers  30  are disposed in the first header  24  and the second header  26 . The dividers  30  divide the tubes  28  into groups and direct refrigerant flow in a serpentine path through the tubes  28  between the headers  24 ,  26 . The dividers  30  thus prevent the refrigerant from flowing into the first header  24  and exiting through the second header  26  after making only one pass through the tubes  28 . By flowing the refrigerant in a serpentine path through the tubes  28 , the refrigerant is substantially cooled before exiting the condenser  10 . 
   Referring to  FIG. 3 , the second header  26  includes a header portion  32  and a receiver portion  34 . The receiver portion  34  has a first end  36  and a second end  38  and preferably extends in parallel relationship along the header portion  32 . A receiver inlet  40  extends between the second header  26  and the receiver portion  34  and is proximal to the first end  36  of the receiver portion  34 . The receiver inlet  40  conveys refrigerant from the second header  26  into the receiver portion  34 . The receiver inlet  40  is positioned adjacent to an end of the serpentine path of the refrigerant flow in the condenser  10 . By including the receiver inlet  40  within the second header  26 , a potential for leaks is avoided where the refrigerant flows from the condenser  10  to the receiver portion  34 . The receiver portion  34  defines a receiver cavity  42  for receiving and storing the refrigerant from the header portion  32  for flowing into the evaporator  14  through the evaporator inlet line  22 . Although it is not required, the condenser  10  is preferably positioned with the headers  24 ,  26  vertically disposed. The receiver inlet  40  is positioned at a top of the receiver portion  34  to fill the receiver cavity  42  and maintain a constant supply of refrigerant in the receiver cavity  42 . A condenser inlet  44  is disposed in the first header  24 . The condenser inlet  44  receives a flow of refrigerant from the compressor  16 . The refrigerant flowing into the condenser  10  from the compressor  16  is superheated and would cause the refrigerant flowing in the receiver cavity  42  to boil if the condenser inlet  44  was positioned in the second header  26 . Thus, the condenser inlet  44  must be positioned in the first header  24  to allow the refrigerant to make at least one pass through the tubes  28  before reaching the second header  26  such that the refrigerant is de-superheated. One pass through the tubes  28  is sufficient to cool the refrigerant flowing into the condenser  10  from the compressor  16  such that it will not boil the refrigerant flowing in the receiver cavity  42 . 
   As shown in  FIG. 3 , the condenser  10  further includes a conduit  46 . More specifically, the conduit  46  is a component of the suction line. The conduit  46  extends into and out of and is surrounded by the second header  26 . A space  48  is defined between the conduit  46  and the second header  26  for receiving the refrigerant flowing into the receiver cavity  42  from the condenser  10 . More specifically, the conduit  46  extends into and out of the receiver cavity  42 . That is, in the subject invention, the vaporized refrigerant flowing through the suction line  18  is re-routed from the evaporator  14  through the receiver cavity  42  before flowing to the compressor  16 . Preferably, as shown in  FIG. 7 , the receiver portion  34  defines a circular cross-sectional shape. Preferably, the conduit  46  also defines a circular cross-sectional shape and is concentric within the receiver cavity  42  to define the space  48  between the conduit  46  and the receiver portion  34 . The conduit  46  is surrounded by the receiver portion  34 . Refrigerant flows through the conduit  46  independently of refrigerant flowing in the space  48 . 
   During operation of the air conditioning system  12 , as the refrigerant vaporizes in the evaporator  14 , pressure pulsations are generated in the refrigerant. The pressure pulsations travel through the refrigerant flowing through the suction line  18  and the conduit  46 . The pressure pulsations create noise that may be audible outside of the air conditioning system  12 . The conduit  46  attenuates the pressure pulsations in the refrigerant flowing through the conduit  46  to eliminate a need for a separate muffler, thus reducing cost for the air conditioning system  12 . 
   The purpose of the conduit  46  passing through the receiver portion  34  is to transfer heat between the refrigerant flowing in the space  48  and the conduit  46 . Refrigerant flowing from the evaporator  14  through the conduit  46 , although vaporized, is at a much lower temperature than the refrigerant flowing through the space  48 , which is in a liquid state, due to pressure differences between the refrigerant flowing in the conduit  46  and the refrigerant flowing in the space  48 . In addition, with the receiver portion  34  extending in parallel to the header portion  32  of the second header  26 , refrigerant flowing through the header portion  32  is also cooled, through the refrigerant in the space  48 , by the refrigerant flowing in the conduit  46 . The refrigerant flowing into the condenser  10  is super heated. The super heated refrigerant is cooled to de-superheat the refrigerant in a first pass through the tubes  28  before the refrigerant reaches the header portion  32  of the second header  26  to prevent the refrigerant from boiling the refrigerant flowing through the receiver portion  34 . The refrigerant flowing through the header portion  32  of the second header  26  is not much hotter than the refrigerant flowing in the space  48 . Thus, additional heat removal from the refrigerant flowing through the header portion  32  of the second header  26  increases an overall efficiency for the air conditioning system  12  and does not drastically raise a temperature of the refrigerant flowing through the space  48 . 
   Referring to  FIGS. 3 and 6 , the conduit  46  includes a plurality of fins  50  spaced along and disposed transversely about an exterior of the conduit  46 . The fins  50  aid in the transfer of heat in a heat exchanger by increasing a heat transfer surface area between fluid flows. Referring to  FIG. 7 , the fins  50  are generally annular in shape. Preferably the fins  50  define holes  52  to permit the refrigerant flowing in the space  48  to flow less hindered through the space  48 , however, the holes  52  are not specifically required, and slots (not shown) may be defined by the fins  50  in place of the holes  52 . Furthermore, an annular gap is defined between each fin  50  and the receiver portion  34  to allow the refrigerant to flow around the fin  50  and through the space  48 . 
   Referring again to  FIGS. 3 and 6 , a desiccant  56  is disposed about the conduit  46  along a portion of a length of the conduit  46  in the space  48 . The desiccant  56  dehydrates the refrigerant. Preferably, for the conduit  46  and the receiver portion  34  having circular cross-sectional shapes, the desiccant  56  is an annular desiccant cartridge, as is well known in the art. 
   A first end cap  58  is disposed at the first end  36  of the receiver portion  34  for closing the receiver portion  34  about the conduit  46  at the first end  36 . The first end cap  58  provides an inlet into the conduit  46  for communication with the evaporator  14 . The first end cap  58  includes a first male member  62  extending from the first end cap  58 . The first male member  62  inserts into the first end  36  of the receiver portion  34  and extends into the receiver cavity  42  for sealing the receiver cavity  42  at the first end  36 . 
   The first end cap  58  defines a first axial bore  64  through the first end cap  58 . The conduit  46  partially extends into the first axial bore  64 . The first axial bore  64  centers the conduit  46  in the receiver cavity  42  to ensure that the refrigerant flows uniformly around the conduit  46 . The first end cap  58  further includes a first inner ledge  66  disposed within the first axial bore  64 . The first inner ledge  66  abuts the conduit  46  when the conduit  46  extends into the first axial bore  64 . The first inner ledge  66  defines an opening for conveying refrigerant into the conduit  46 . The first end cap  58  further includes a first outer peripheral ledge  68  disposed about the first male member  62  for abutting the first end  36  of the receiver portion  34 . The first inner ledge  66 , the first outer peripheral ledge  68 , and the first male member  62  simplify assembly of the condenser  10  by preventing the conduit  46  from being inserted too far into the first end cap  58  and by preventing the first end cap  58  from being inserted too far into the receiver cavity  42 . Thus, the first inner ledge  66 , the first outer peripheral ledge  68 , and the first male member  62  inhibit a tendency toward misassembly of the condenser  10  by providing reference points for correct assembly. 
   A second end cap  70  is disposed at the second end  38  of the receiver portion  34 . The second end cap  70  closes the receiver portion  34  about the conduit  46  at the second end  38 . The second end cap  70  also provides outlets for communication with a compressor  16  and the evaporator  14 . The second end cap  70  includes a second male member  72  extending from the second end cap  70 . The second male member  72  inserts into the second end  38  of the receiver portion  34  and extends into the receiver cavity  42  for sealing the receiver cavity  42  at the second end  38 . The second male member  72  defines a concentric groove  74  for allowing refrigerant to flow from the receiver cavity  42  to the evaporator  14 . 
   The second end cap  70  defines a second axial bore  76  through the second end cap  70 . The conduit  46  partially extends into the second axial bore  76 . The second axial bore  76  centers the conduit  46  in the receiver cavity  42 . The second end cap  70  further includes a second inner ledge  78  disposed within the second axial bore  76 . The second inner ledge  78  abuts the conduit  46  when the conduit  46  extends into the second axial bore  76 . The second inner ledge  78  defines an opening for conveying refrigerant out of the conduit  46 . The second end cap  70  further includes a second outer peripheral ledge  80  disposed about the second male member  72  for abutting the second end  38  of the receiver portion  34 . Like the first inner ledge  66 , the first outer peripheral ledge  68 , and the first male member  62  of the first end cap  58 , the second inner ledge  78 , the second outer peripheral ledge  80 , and the second male member  72  aid in assembly of the condenser  10  by providing reference points for correct assembly. 
   Referring again to  FIG. 3 , the second end cap  70  defines a chamber  82  separate from the second axial bore  76 . The chamber  82  receives refrigerant flowing from the concentric groove  74 . The second end cap  70  further defines a third bore  84  transverse to and intersecting the second axial bore  76 . The third bore  84 , as described below, is designed to receive an expansion device  86 . 
   Preferably, the first end cap  58  and the second end cap  70  are brazed onto the first end  36  and the second end  38 , respectively. The first end cap  58  and the second end cap  70  are brazed adjacent the first male member  62  and second male member  72 , respectively. The brazing process creates a durable seal that inhibits leakage from the receiver cavity  42  at the first end cap  58  and the second end cap  70 . It is to be appreciated that alternative methods of attaching the first end cap  58  and the second end cap  70  are also possible. 
   The expansion device  86  is any device capable of expanding the refrigerant. Preferably, the expansion device  86  is a thermostatic expansion valve assembly (TXV)  86 , although a fixed or variable orifice (not shown) may also be used. Although the TXV  86  is not required at the condenser  10 , the particular embodiment disclosed in  FIG. 3  includes the TXV  86  disposed within the third bore  84  of the second end cap  70 . Alternatively, the TXV may be positioned in the evaporator inlet line  22 , adjacent to the evaporator  14 . The TXV  86  maintains separation between the refrigerant flowing in the second axial bore  76  and the refrigerant flowing in the chamber  82 . If the TXV  86  is not disposed in the second end cap  70 , a barrier, which is not shown, must be disposed in the third bore  84  between the second axial bore  76  and the chamber  82  to separate the refrigerant flowing through the second axial bore  76  and the refrigerant flowing through the chamber  82 . The TXV  86  is in fluid communication with the chamber  82  to control the refrigerant flowing from the receiver cavity  42  to the evaporator  14 . 
   Alternatively, as shown in  FIGS. 4-6 , the TXV  86  is mounted to the second end cap  70 . The TXV  86  defines a first channel  88  and a second channel  90 . The first channel  88  and second channel  90  complement the chamber  82  and the second axial bore  76 , respectively, for separately receiving the refrigerant flowing from the chamber  82  and the second axial bore  76 . The TXV  86  is in fluid communication with the chamber  82  to control the refrigerant flowing from the receiver cavity  42  to the evaporator  14 . 
   As is understood by those skilled in the art, the TXV  86  controls the refrigerant flowing from the receiver cavity  42  to the evaporator  14  by sensing or monitoring a superheat of the refrigerant that exits the evaporator  14  through the suction line  18 , i.e., the conduit  46 . Because the refrigerant from the evaporator  14  is returned back through the receiver portion  34 , the TXV  86  can sense or monitor the superheat in the receiver cavity  42  and an external superheat sensing bulb is not required in the air conditioning system  12  to sense heat elsewhere. 
   A first end cap adapter  92  is coupled to the suction line  18 . The first end cap adapter  92  engages the first end cap  58  for mounting the suction line  18  to the conduit  46  at the first end  36 . Preferably, the first end cap  58  and the first end cap adapter  92  include complementary first end flanges  94  extending transverse to the first axial bore  64 . Preferably, the first end flanges  94  define complementary holes for receiving a fastener  96  and for mounting the first end cap adapter  92  to the first end cap  58 , however, it is to be appreciated that other fastening means are possible. 
   Referring to  FIG. 3 , a second end cap adapter  98  is coupled to the suction line  18 . The second end cap adapter  98  engages the second end cap  70  for mounting the suction line  18  to the conduit  46  at the second end  38 . A third end cap adapter  100  is coupled to the evaporator inlet line  22 . The third end cap adapter  100  engages the second end cap  70  for mounting the evaporator inlet line  22  to the conduit  46  at the second end  38 . More specifically, the second end cap adapter  98  and the third end cap adapter  100  are mounted to the second end cap  70  at the third bore  84  on opposite ends of the third bore  84 . Preferably, the second end cap  70  and the second end cap adapter  98  include complementary second end flanges  102  extending transverse to the third bore  84 . Preferably, the second end cap  70  and the third end cap adapter  100  include complementary second end flanges  102  extending transverse to the second axial bore  76 . Preferably, the second end flanges  102  define complementary holes for receiving a fastener  96  and for mounting the second end cap adapter  98  to the second end cap  70  and for mounting the third end cap adapter  100  to the second end cap  70 , however, it is to be appreciated that other fastening means are possible. 
   Alternatively, as shown in  FIG. 6 , a fourth end cap adapter  104  is coupled to the suction line  18  and to the evaporator inlet line  22 . The fourth end cap adapter  104  engages the second end cap  70  for mounting the suction line  18  and the evaporator inlet line  22  to the conduit  46  at the second end  38 . Preferably, the second end cap  70  and the fourth end cap adapter  104  define complementary holes for receiving a fastener  96  and for mounting the fourth end cap adapter  104  to the second end cap  70 , however, it is to be appreciated that other fastening means are possible. 
   By including the first end cap adapter  92  and fourth end cap adapter  104  instead of fusing the suction line  18  to the first end cap  58  and the second end cap  70 , respectively, the system  12  of the subject invention provides an accessibility advantage. The first end cap adapter  92  and the fourth end cap adapter  104  may be easily removed to access the receiver portion  34  and to remove and repair the condenser  10 . 
   A method of assembling the condenser  10  is also proposed. In an optional fabricating step, the second header  26  is cut from a header tube preferably having a circular cross-sectional shape. More preferably, the second header  26  is cut from the header tube having the header portion  32  and the receiver portion  34  defining the receiver cavity  42 . 
   In a mounting step, the second header  26  is mounted onto the condenser  10  having the first header  24  and the plurality of tubes  28 . The second header  26  may be welded, snapped, brazed, or otherwise fused onto the condenser  10  to ensure that the second header  26  will not leak when receiving refrigerant under high pressure. 
   In a first end cap fusing step, the first end cap  58  is pressed and fused onto the second header  26  at the first end  36  of the receiver portion  34 . The first male member  62  is inserted into the space  48  to correctly position the first end cap  58  on the first end  36 . Preferably, the first end cap  58  is brazed onto the second header  26 . Preferably, the first end cap fusing step is performed subsequent to the step of mounting the second header  26  onto the condenser  10 . However, it is to be appreciated that the first end cap fusing step may be performed prior to the step of mounting the second header  26  onto the condenser  10 . 
   In an optional cutting step, the conduit  46  is cut from a conduit tube preferably having a circular cross-sectional shape smaller than the receiver portion  34 . In a fin fusing step that is also optional, a plurality of fins  50  are fused onto the conduit  46  in spaced relationship along and transversely about an exterior of the conduit  46 . More specifically, the conduit  46  is inserted through the fins  50 , which are annular in shape. The fins  50  are mounted to the conduit  46  through mechanical expansion of the conduit  46 . The fins  50  may be mounted to the conduit  46  through other methods, such as welding, brazing, etc. 
   In an inserting step, the conduit  46  is inserted into the first axial bore  64  to center the conduit  46  in the receiver cavity  42 . Preferably, the conduit  46  is inserted into the first axial bore  64  prior to the step of fusing the first end cap  58  onto the second header  26 . The conduit  46  is pressed into the first axial bore  64  until the conduit  46  abuts the first inner ledge  66  disposed in the first end cap  58 . 
   In a second end cap fusing step, the second end cap  70  is fused onto the second header  26  at the second end  38  of the receiver portion  34 . Preferably, the second end cap  70  is brazed onto the second header  26 . Preferably, the step of fusing the second end cap  70  onto the second header  26  occurs before the step of fusing the first end cap  58  onto the second header  26 . Regardless of which end cap fusing step occurs first, only one of the first end cap fusing step and the second end cap fusing step can be performed before the step of inserting the conduit  46  through the second header  26 . 
   In a desiccant inserting step, the desiccant  56  is placed in the receiver cavity  42 . Preferably, the desiccant inserting step is performed prior to the step of inserting the conduit  46  into the second header  26 , but may also be performed after the step of inserting the conduit  46  into the second header  26 , in which case the desiccant inserting step is placed in the space  48  between the conduit  46  and the receiver portion  34 . 
   For assembly of the embodiment as shown in  FIG. 3 , the TXV  86  is inserted into the second end cap  70  subsequent to the step of fusing the second end cap  70  onto the second end  38 . The second end cap adapter  98 , and the third end cap adapter  100  are mounted to the second end cap  70  and the first end cap adapter  92  is mounted to the first end cap  58  to connect the condenser  10  to the air conditioning system  12 . 
   Alternatively, for the embodiment of  FIG. 6 , the TXV  86  is mounted to the second end cap  70 , preferably after the step of fusing the second end cap  70  to the second end  38 . The fourth end cap adapter  104  is mounted to the second end cap  70  and the first end cap adapter  92  is mounted to the first end cap  58  to connect the condenser  10  to the air conditioning system  12 . 
   Obviously, many modifications and variations of the present invention are possible in light of the above teachings. The invention may be practiced otherwise than as specifically described within the scope of the appended claims.