Abstract:
An improved heat exchanger includes a first tube ( 10 ) of generally circular cross section having a relatively large inside diameter and being U-shaped with opposite ends ( 12,14 ) adjacent one another. A second tube having a cross section that is relatively small in relation to the cross section of the first tube ( 10 ) and helical shaped section ( 36 ) intermediate its ends ( 32,34 ) is located within the first tube ( 10 ) and extends through caps ( 44 ) at the ends ( 12,14 ) of the first tube ( 10 ) to be received in headers ( 38,40 ). The first tube ( 10 ) impales headers ( 26,28 ) and includes apertures ( 22,24 ) aligned with the headers ( 26,28 ) and in fluid communication with the interiors thereof.

Description:
FIELD OF THE INVENTION  
         [0001]    This invention relates to heat exchangers generally, and more particularly, to a heat exchanger that may serve as a water heater and a gas cooler.  
         BACKGROUND OF THE INVENTION  
         [0002]    Ozone layer and/or global warming problems have focused considerable attention on the nature of refrigerants employed in refrigeration systems of various sorts. Some such systems, particularly those that do not have sealed compressor units as are commonly found in vehicular air conditioning systems, are prone to refrigerant leakage. Older refrigerants, HFC 12, for example, are thought to cause depletion of the ozone layer while many of the replacements, HCFC 134a, for example, are believed to contribute to the so-called “greenhouse effect” and thus global warming.  
           [0003]    As a consequence, a considerable effort is underway to develop refrigeration systems employing transcritical refrigerants such as carbon dioxide. Carbon dioxide is plentiful in the atmosphere and may be obtained therefrom by conventional techniques and employed as a refrigerant in such systems. Should the systems leak the CO 2  refrigerant, because it was originally obtained from the atmosphere, there is no net increase of the refrigerant in the atmosphere, and thus no increase in environmental damage as a result of the leak.  
           [0004]    Transcritical refrigeration systems, such as CO 2  systems, operate at relatively high pressures and require, in lieu of a condenser in a conventional vapor compression refrigeration system, a gas cooler for the refrigerant.  
           [0005]    The heat rejected by a gas cooler can be employed for various useful purposes and one such use is for heating potable water for residential, commercial, or industrial usages. The present invention is primarily directed at providing a combination water heater and gas cooler.  
         SUMMARY OF THE INVENTION  
         [0006]    It is the principal object of the invention to provide a new and improved heat exchanger. More specifically, it is an object of the invention to provide a new and improved heat exchanger that is particularly suited for use as a gas cooler in a refrigeration system and utilizes the rejected heat from the gas stream being cooled to heat a liquid, such as potable water.  
           [0007]    An exemplary embodiment of the invention achieves the foregoing object in a heat exchanger that includes a first tube of generally circular cross section and which has a relatively large internal diameter. The first tube is generally U-shaped with opposite ends adjacent to one another. A second tube having a circular cross section that is relatively small in relation to the relatively large cross section of the first tube is provided and has opposite ends. Intermediate the opposite ends the second tube is a helical configuration having an external diameter about that of the relatively large diameter of the first tube. Convolutions of the helical configuration can be spaced from one another, or could be touching, and the second tube is located within the first tube with the opposed ends of the second tubes extending out of the opposite ends of the first tube. Hollow headers are impaled by the first tube adjacent each of the opposite ends and are sealed thereto and a port in the first tube is adjacent each opposite end and aligned with and in fluid communication with a corresponding one of the headers. A cap is disposed on each of the opposite ends of the first tube and sealed thereto and an aperture in each cap is sized to receive a corresponding one of the opposed ends of the second tube to allow the corresponding one of the opposed ends to extend past the cap. The caps, and each corresponding one of the opposed ends of the second tube are sealed to each other at the corresponding aperture.  
           [0008]    In one form, the first tube has opposite ends and at least one U-shaped bend between the opposite ends. In a further form, the first tube has at least two U-shaped bends between the opposite ends.  
           [0009]    In a preferred embodiment, the helical configuration of the second tube has an external diameter such that it is in contact with the internal diameter of the first tube.  
           [0010]    Preferably, each of the headers is a tube of larger internal diameter than the external diameter of the first tube.  
           [0011]    In a preferred embodiment, each of the caps has a flat circular wall surrounded by a peripheral cylindrical flange and sealed to the associate opposite end of the first tube and the aperture is located in the flat circular wall.  
           [0012]    In one embodiment of the invention, each of the flanges on the caps abuts and seals against the interior wall of the first tube while in another embodiment, each such flange abuts and seals against the exterior wall of the first tube.  
           [0013]    Other objects and advantages will become apparent from the following specification taken in connection with the accompanying drawings. 
       
    
    
     DESCRIPTION OF THE DRAWINGS  
       [0014]    [0014]FIG. 1 is a plan view of a heat exchanger made according to the invention;  
         [0015]    [0015]FIG. 2 is a fragmentary, side elevation of the heat exchanger;  
         [0016]    [0016]FIG. 3 is a perspective view of a cap employed in the heat exchanger;  
         [0017]    [0017]FIG. 4 is a fragmentary sectional view of part of the heat exchanger;  
         [0018]    [0018]FIG. 5 is a fragmentary view showing an optional construction for the heat exchanger of FIG. 1; and  
         [0019]    [0019]FIG. 6 is a somewhat diagrammatic plan view of another embodiment of the heat exchanger made according to the invention. 
     
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS  
       [0020]    The present invention will be described as being useful in the environment of a refrigeration system employing a transcritical refrigerant such as CO 2 . However, it is to be understood that the heat exchanger may be used in other heat exchange applications that do not involve refrigeration and/or water heating and may find use in refrigeration systems using conventional, and/or nontranscritical refrigerants. Accordingly, no limitation to a water heater/gas cooler in a transcritical refrigeration system is intended except insofar as expressly stated in the appended claims.  
         [0021]    With the foregoing in mind, the exemplary embodiments of a heat exchanger made according to the invention and particularly suited for use as a gas cooler/water heater will be described. Referring to FIG. 1, an elongated, U-shaped tube, generally designated  10 , has opposed ends  12  and  14  which are brought into adjacency with each other as a result of a bent or curved section  16  located approximately midway between the ends  12  and  14  of the tube  10 . The tube  10  is generally circular in cross section and, if made without the bend  16 , cylindrical in shape. Preferably, the tube  10  will be made of metal such as copper or stainless steel but other materials, including nonmetallic ones, could be used in forming the tube  10  in some instances.  
         [0022]    The tube  10  has an interior wall  18  of a relatively large diameter as well as an exterior wall  20 .  
         [0023]    Adjacent the ends  12  and  14 , inlet and outlet apertures  22 , 24 , respectively, are provided in the tube  10 . Tubular headers  26  and  28  are impaled by respective ones of the ends  12  and  14  such that they are aligned with the apertures  22 , 24  and are sealed to the exterior wall  20  of tube  10 . It will be observed that the headers  26 , 28  are preferably tubes of generally circular cross section and of a larger diameter than the outer diameter of the wall  20  of the tube  10 .  
         [0024]    Contained within the tube  10  is a second tube, generally designated  30 , of circular cross section and having a diameter that is relatively small compared to the diameter of the first tube  10 . The second tube  30  has opposed ends  32 , 34  and intermediate its ends, the tube  30  has helical convolutions  36 . In some applications it may be advantageous for the convolutions  36  to be spaced from each other as shown in FIG. 1, while in other applications it may be advantageous for the convolutions to be abutted against each other as shown in FIG. 5. In a preferred embodiment, the diameter of the helix forming the convolutions  36  is essentially the same as the inner diameter of the tube  10  so that the convolutions  36  of the tube  30  may be in contact with the inner wall  18  of the tube  10 . However, it is not necessary that such be the case and in many instances, the outer diameter of the convolutions  36  could be considerably less than the diameter of the inner wall  18  of the tube  10 .  
         [0025]    The ends  32 , 34  of the second tube  30  are relatively straight as can be seen in the left-hand side of FIG. 1 and extend beyond the ends  12 , 14  of the first tube  10  to terminate within tubular headers  38 , 40 .  
         [0026]    To this end, the headers  38  and  40  are apertured as at  42 , that is, provided with a circular hole  42  of approximately the same diameter as the outer diameter of the ends  32 , 34  of the second tube  30 . The interfaces of the headers  38 , 40  and the ends  32 , 34  at the apertures  42  are sealed.  
         [0027]    In the usual case, the second tube  30  will be made of a metal such as copper or stainless steel and will have a wall thickness sufficient, when considering the material of which it is made, to withstand the operating pressures which, in a refrigeration system, particularly a transcritical one, can be substantial. The use of a metal as a material for forming the tube  30  is preferred because its greater thermal conductivity than other materials such as plastics.  
         [0028]    Returning to the first tube  10 , the same has its ends  12  and  14  capped with caps  44 . The caps  44  include a central aperture  46  through which the ends  32 , 34  of the second tube  30  pass and are sealed.  
         [0029]    A typical cap  44  is shown in perspective in FIG. 3 and it will be seen that the same has a flat, circular base  48  in which the central aperture is located and which is surrounded by a peripheral, cylindrical flange  50 . In one embodiment, the caps  44  are adapted to fit onto and seal against the outer surface  20  of the first tube  10 . In that case, the inner surface  52  of each cap  54  will have a diameter equal to the outer diameter of the tube  10 , that is, the diameter of the outer surface  20  of the wall of the tube  10 . This type of arrangement is shown in FIGS. 1 and 2.  
         [0030]    In an alternate form of the invention shown in FIG. 4, each cap  44  is again provided with a flat circular central base  48  including the aperture  46  therein through which an end  32 , 34  of the second tube  30  passes. In this case, the cap  44  is introduced into the end  12 , 14  of the first tube  10  and the outer surface  56  of the flange  50  will have a diameter that is approximately the same as the diameter of the inner surface  18  of the tube  10  so that the cap  44  and first tube  10  may be sealed to one another.  
         [0031]    The various interfaces of the components requiring sealing, including the interface between the caps  44  and ends  12 , 14 , of the first tube  10  and the tube ends  32 , 34 , may be sealed by known bonding techniques. For example, where the components are metal, metallurgical bonds are preferred such as those achieved by soldering, brazing or even welding.  
         [0032]    In some instances, it may be desirable to employ more than one of the heat exchangers thus described in a single structure. In this case, the form of the invention fragmentarily illustrated in FIG. 2 may be employed. In this embodiment, two or more of the just described structures are utilized with a single pair of the headers  26 , 28  and a single pair of the headers  38 , 40 . The number of units employed with a given set of headers will, of course, depend upon the heat exchange capacity desired.  
         [0033]    As illustrated, the header  40  serves as an inlet header through the second tube  30  while the header  38  serves as an outlet tube therefore. The header  26  serves as an inlet header for the first tube  10  while the header  28  serves as an outlet header therefore. Thus, flows will be in the direction of arrows illustrated in FIG. 1 and it will be seen that countercurrent flow for maximum efficiency is achieved. However, if desired, the inlet and outlet positions of the headers  38 , 40  or the headers  26 , 28  could be reversed to achieve concurrent flow. Baffles, not shown, could be placed in the headers to achieve multipass flow in a conventional fashion if desired.  
         [0034]    Advantageously, heat transfer is maximized in the structure by reason of the helical convolutions  36  and the spacing thereof of the second tube  30  within the first tube  10 . This configuration promotes turbulence in the fluid entering the header  26  and leaving the header  28  as it passes through the first tube  10 . The increased turbulence increases the rate of heat transfer.  
         [0035]    By manufacturing the convolutions  36  so that they at least nominally engage the inner surface  18  of the tube  10 , the length of the tube  30  within the tube  10  is maximized, thereby maximizing the surface area available for heat transfer and further improve heat transfer efficiency.  
         [0036]    The use of caps such as the caps  44 , whether in the configuration shown in FIGS. 1 and 2 or in the configuration shown in FIG. 4 provides a simple, but effective way of sealing the ends  12 , 1   3  of the first tube  10  as well as the point of entry and exit of the second tube  30  from the first tube  10  with simply an economically manufactured structure, thereby reducing the cost of the heat exchanger.  
         [0037]    The apertures such as those shown at  22 , 24 , 42 , 46  as well as the unnumbered apertures in the headers  26 , 28  through which the first tube  10  passes may be punched, as opposed to machined, thereby lowering the cost of manufacture in this regard as well.  
         [0038]    [0038]FIG. 6 is diagrammatic representation of an alternate embodiment of a heat exchanger made according to the invention. Other than the exceptions discussed below, all of the components of the embodiment of FIG. 6, and options therefor, are the same as those previously described, with like reference numbers representing like components. The embodiment of FIG. 6 differs from that previously described in that the tube  10  has multiple U-shaped bends  16  rather than the single bend  18  shown in FIG. 1. While the embodiment of FIG. 6 is shown with two U-shaped bends  16 , in some applications more than two bends may be desirable or less than two bends may be desirable, depending upon the requirements of the particular application. The use of multiple bends  16  allows for a greater length of the tubes  10  and  30  without increasing the width of the heat exchanger. As seen in FIG. 6, if an even number of bends  16  are provided, the ends  12  and  14  and the ends  32  and  34  are located at opposite sides of the heat exchanger, as are the associated headers  26 , 28  and headers  38 , 40 , as opposed to being located on the same side of the heat exchanger when an odd number of bends  16  are used as in FIG. 1.  
         [0039]    The ability to employ several of the heat exchange structure with a single set of headers provides a great deal of flexibility in designing for a given heat exchange capacity, thereby providing maximum design flexibility.