Patent Abstract:
In a parallel flow heat exchanger having an inlet manifold connected to an outlet manifold by a plurality of parallel channels, a spirally shaped insert is disposed within the refrigerant flow path in the inlet manifold such that a swirling motion is imparted to the refrigerant flow in the manifold so as to cause a more uniform distribution of refrigerant to the individual channels. Various embodiments of the spirally shaped inserts are provided, including inserts designed for the internal flow of refrigerant therethrough and/or the external flow of refrigerant thereover.

Full Description:
CROSS REFERENCE TO RELATED APPLICATION 
       [0001]    This application is a divisional of prior U.S. patent application Ser. No. 10/986,680, filed Nov. 12, 2004, now copending, which is incorporated herein by reference. 
     
    
     BACKGROUND OF THE INVENTION 
       [0002]    This invention relates generally to air conditioning and refrigeration systems and, more particularly, to parallel flow evaporators thereof. 
         [0003]    A definition of a so-called parallel flow heat exchanger is widely used in the air conditioning and refrigeration industry now and designates a heat exchanger with a plurality of parallel passages, among which refrigerant is distributed and flown in an orientation generally substantially perpendicular to the refrigerant flow direction in the inlet and outlet manifolds. This definition is well adopted within the technical community and will be used throughout the specification. 
         [0004]    Refrigerant maldistribution in refrigerant system evaporators is a well-known phenomenon. It causes significant evaporator and overall system performance degradation over a wide range of operating conditions. Maldistribution of refrigerant may occur due to differences in flow impedances within evaporator channels, non-uniform airflow distribution over external heat transfer surfaces, improper heat exchanger orientation or poor manifold and distribution system design. Maldistribution is particularly pronounced in parallel flow evaporators due to their specific design with respect to refrigerant routing to each refrigerant circuit. Attempts to eliminate or reduce the effects of this phenomenon on the performance of parallel flow evaporators have been made with little or no success. The primary reasons for such failures have generally been related to complexity and inefficiency of the proposed technique or prohibitively high cost of the solution. 
         [0005]    In recent years, parallel flow heat exchangers, and brazed aluminum heat exchangers in particular, have received much attention and interest, not just in the automotive field but also in the heating, ventilation, air conditioning and refrigeration (HVAC&amp;R) industry. The primary reasons for the employment of the parallel flow technology are related to its superior performance, high degree of compactness and enhanced resistance to corrosion. Parallel flow heat exchangers are now utilized in both condenser and evaporator applications for multiple products and system designs and configurations. The evaporator applications, although promising greater benefits and rewards, are more challenging and problematic. Refrigerant maldistribution is one of the primary concerns and obstacles for the implementation of this technology in the evaporator applications. 
         [0006]    As known, refrigerant maldistribution in parallel flow heat exchangers occurs because of unequal pressure drop inside the channels and in the inlet and outlet manifolds, as well as poor manifold and distribution system design. In the manifolds, the difference in length of refrigerant paths, phase separation, gravity and turbulence are the primary factors responsible for maldistribution. Inside the heat exchanger channels, variations in the heat transfer rate, airflow distribution, manufacturing tolerances, and gravity are the dominant factors. Furthermore, the recent trend of the heat exchanger performance enhancement promoted miniaturization of its channels (so-called minichannels and microchannels), which in turn negatively impacted refrigerant distribution. Since it is extremely difficult to control all these factors, many of the previous attempts to manage refrigerant distribution, especially in parallel flow evaporators, have failed. 
         [0007]    In the refrigerant systems utilizing parallel flow heat exchangers, the inlet and outlet manifolds or headers (these terms will be used interchangeably throughout the text) usually have a conventional cylindrical shape. When the two-phase flow enters the header, the vapor phase is usually separated from the liquid phase. Since both phases flow independently, refrigerant maldistribution tends to occur. 
         [0008]    If the two-phase flow enters the inlet manifold at a relatively high velocity, the liquid phase (droplets of liquid) is carried by the momentum of the flow further away from the manifold entrance to the remote portion of the header. Hence, the channels closest to the manifold entrance receive predominantly the vapor phase and the channels remote from the manifold entrance receive mostly the liquid phase. If, on the other hand, the velocity of the two-phase flow entering the manifold is low, there is not enough momentum to carry the liquid phase along the header. As a result, the liquid phase enters the channels closest to the inlet and the vapor phase proceeds to the most remote ones. Also, the liquid and vapor phases in the inlet manifold can be separated by the gravity forces, causing similar maldistribution consequences. In either case, maldistribution phenomenon quickly surfaces and manifests itself in evaporator and overall system performance degradation. 
       SUMMARY OF THE INVENTION 
       [0009]    Briefly, in accordance with one aspect of the invention, a structure is provided in association with the inlet manifold so as to create a swirling motion of the two-phase refrigerant flow in the evaporator inlet manifold to thereby obtain and uniformly distribute a homogenous two-phase mixture, that consist of liquid and vapor phases, among the parallel channels. At high velocities, the droplets of liquid are driven to the periphery of the manifold by the centrifugal force and some of them pass through the channels closest to the manifold entrance. In the case of low refrigerant velocities, the swirling motion creates the momentum that will carry some of the liquid droplets to the remote channels in the manifold. Additionally, mixing of the refrigerant vapor and liquid phases further promotes homogeneous flow conditions. In each case non-uniform refrigerant distribution is avoided. 
         [0010]    In accordance with another aspect of the invention, the swirling motion is brought about by a spirally wound insert extending longitudinally within the inlet header and having a plurality of perforations for conducting the refrigerant flow into the internal cavity of the inlet header and then to the individual channels adjacent thereto. 
         [0011]    In accordance with another aspect of the invention, the inlet manifold itself is formed in a spirally wound coil that extends along the entrance to the individual channels and is fluidly interconnected thereto by its individual elements. 
         [0012]    By yet another aspect of the invention, a spirally formed, short insert is provided at the entrance to the inlet header and the refrigerant flow passing around the spiral insert prior to entering the inlet header. 
         [0013]    By still another aspect of the invention, a spiral insert is placed within the inlet manifold preferably in a coaxial relationship therewith such that the outer surface of the spiral insert causes a desirable swirling of the refrigerant flow within the inlet manifold such that uniform distribution of refrigerant is provided to the individual channels. 
         [0014]    In the drawings as hereinafter described, preferred and alternate embodiments are depicted; however, various other modifications and alternate constructions can be made thereto without departing from the true spirit and scope of the invention. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0015]      FIG. 1  is a schematic illustration of a parallel flow heat exchanger in accordance with the prior art. 
           [0016]      FIG. 2A  is a schematic illustration of one embodiment of the present invention. 
           [0017]      FIG. 2B  is a variation of the  FIG. 2A  embodiment. 
           [0018]      FIG. 2C  is another variation of the  FIG. 2A  embodiment. 
           [0019]      FIG. 2D  is yet another variation of the  FIG. 2A  embodiment. 
           [0020]      FIG. 3  is an alternative embodiment thereof. 
           [0021]      FIG. 4  is another alternative embodiment thereof. 
           [0022]      FIG. 5A  is yet another alternative embodiment thereof. 
           [0023]      FIG. 5B  is a variation of the  FIG. 5A  embodiment. 
       
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENT 
       [0024]    Referring now to  FIG. 1 , a parallel flow heat exchanger is shown to include an inlet header or manifold  11 , an outlet header or manifold  12  and a plurality of parallel disposed channels  13  fluidly interconnecting the inlet manifold  11  to the outlet manifold  12 . Generally, the inlet and outlet headers  11  and  12  are cylindrical in shape, and the channels  13  are tubes (or extrusions) of flattened or round shape. Channels  13  normally have a plurality of internal and external heat transfer enhancement elements, such as fins. For instance, external fins  15 , disposed therebetween for the enhancement of the heat exchange process and structural rigidity are typically furnace-brazed. Channels  13  may have internal heat transfer enhancements and structural elements as well. 
         [0025]    In operation, two-phase refrigerant flows into the inlet opening  14  and into the internal cavity  16  of the inlet header  11 . From the internal cavity  16 , the refrigerant, typically in the form of a mixture of liquid and vapor, enters the channels openings  17  to pass through the channels  13  to the internal cavity  18  of the outlet header  12 . From there, the refrigerant, which is now usually in the form of a vapor, passes out the outlet opening  19  and then to the compressor (not shown). 
         [0026]    As discussed hereinabove, it is desirable that the two-phase refrigerant passing from the inlet header  11  to the individual channels  13  do so in a uniform manner (or in other words, with equal vapor quality) such that the full heat exchange benefit of the individual channels can be obtained and flooding conditions are not created and observed at the compressor suction (this may damage the compressor). However, because of various phenomena as discussed hereinabove, a non-uniform flow of refrigerant to the individual channels  13  (so-called maldistribution) occurs. In order to address this problem, the applicants have introduced design features that will create a swirling motion of the two-phase refrigerant flow in the inlet manifold  11  to thereby bring about a more uniform flow to the channels  13 . Also, the increased velocity typically associated with the swirling motion will further promote the mixing process of the liquid and vapor phases. 
         [0027]    In the  FIG. 2A  embodiment, an insert  21  is located within the internal cavity  16  of the inlet manifold  11  as shown. The insert  21  is a tubular structure that is formed in a spiral coil with individual coil elements  22  as shown. The insert  21  is preferably suspended within the cavity by appropriate attachment, such as brazing or the like, at the side or end of the inlet manifold  11 . Obviously, the support structure should not block or obstruct the entrance to the individual channels  13 . As shown, the axis A of the spirally formed coil insert  21  is preferably coaxial with the axis of the inlet manifold  11 . 
         [0028]    The inlet opening  14  is fluidly connected by a tube  23  to one end of the insert  21  so as to cause the refrigerant to pass into the insert  21 . A plurality of openings  24  in each of the coil elements  22  provides for fluid communication of the refrigerant from the internal portion of the insert  21  to the internal cavity  16  of the inlet manifold  11 . The refrigerant exiting the openings  24  thus will have a swirling motion at increased velocity imparted thereto prior to entering the internal cavity  16 , thus providing the mixing effect as it moves to the individual channels  13  in a uniform fashion. Additionally, relatively small openings  24  provide uniform dispersement of both phases (liquid and vapor) of refrigerant along the cavity  16  of the manifold  11 . It should be noted that the openings  24  may have various shapes and be of different sizes, preferably with the diminishing sizes as the refrigerant flows from the inlet  14  of the manifold  11  to the remote end of the spirally formed insert  21 . Furthermore, a spirally formed insert  21  may itself have enhancement elements to further promote mixing process. For instance, the insert  21  can be manufactured from a twisted tube, have surface indentations, etc. 
         [0029]    In  FIG. 2B  there is shown a variation of this design wherein, rather than the refrigerant being directed to flow only into the insert  21 , the flow is directed to flow from the inlet  14  to the cavity  16  where it can flow into the insert  21  and over its outer surface, both of which will tend to impart a swirl to the flow. Of course, relevant hydraulic impedances have to be managed, by the insert dimensions, insert relative location inside the manifold and insert opening sizes, to ensure a proper refrigerant flow split into and over the insert  21 . 
         [0030]    In the  FIG. 2C  embodiment the insert  21 C is also designed to give a swirling motion to the fluid flow. However, rather than a coiled tube  21  as shown in  FIG. 2A , the tube  21 C is twisted as shown to provide a swirling motion to the fluid as it exists the openings  24  and enters the internal cavity  16 . 
         [0031]    The  FIG. 2D  embodiment combines the features of the  FIGS. 2A and 2C  embodiments such that the tube  21 D is both twisted and coiled. 
         [0032]    In the  FIG. 3  embodiment, the inlet header  11  of the previously described embodiment is replaced by an inlet header  26  that is, itself, formed in a spirally twisted tube. An inlet opening  14  is fluidly connected at one end of the inlet header  26  so as to introduce the flow of refrigerant thereto. As the refrigerant enters the inlet header  26 , it flows through the internal cavities of the inlet header  26  to thereby have a swirling motion (typically at increased velocity and more homogeneous conditions) imparted thereto. 
         [0033]    Fluidly connected to the inlet header  26 , is the plurality of parallel channels  13  for receiving the refrigerant flow from the inlet header  26 . Because of the swirling motion imparted to the flow of refrigerant within the inlet header  26 , the refrigerant flowing to the individual microchannels  13  is uniformly distributed so as to obtain maximum efficiency from the heat exchanger. It should be noted that the inlet header  26  may be of a progressively diminishing size to reflect a reduction in the refrigerant mass flow rate toward a remote end of the inlet header  26 . Once again, the inlet header  26  may have enhancement elements, such as surface indentations or internal fins, to further promote the mixing process. 
         [0034]    Referring now to  FIG. 4 , an alternative embodiment is shown wherein an insert  28  is placed within the inlet opening  14  as shown rather than within the internal cavity  16  of the inlet manifold  11 . The insert  21  is preferably suspended in a coaxial relationship with the inlet opening  14  by way of brazing or the like to the sides of the inlet opening  14 . The insert  28  may be closed so as to allow the refrigerant to flow around the outer surfaces thereof so as to impart a swirling motion to the refrigerant entering the internal cavity  16  of the inlet manifold  11 . Alternatively, the spiral insert  28  may be opened at its ends such that the refrigerant may pass through the internal confines thereof as it flows through the length of the insert  28  and enters the internal cavity  16 . It may also be so constructed as to pass the refrigerant both through the internal structure and the outer surface of the insert  28  as it enters the internal cavity  16 . In all cases, the swirling motion imparted to the refrigerant as it enters the internal cavity  16  provides a uniform, homogenous refrigerant mixture as it flows along the manifold  11  and enters the individual channels  13 . 
         [0035]    Another embodiment of the present invention is shown in  FIG. 5A  wherein an insert  29  is preferably coaxially disposed within the internal cavity  16  of the inlet manifold  11 , in a manner similar to that of the  FIG. 2A  embodiment. However, rather than the refrigerant being routed through the insert  29 , it is designed to have the refrigerant pass over the spirally formed outer surface of the insert  29  similar to the manner in which this occurs in the  FIG. 4  embodiment. Again, the insert  29  is mounted to the inlet manifold by brazing or the like to the sides or end of the inlet manifold  11 . The swirling high velocity motion that is imparted by the flow of refrigerant over the outer surfaces of the insert again brings about the delivery of a uniform mixture of refrigerant to the individual channels  13 . 
         [0036]    A variation of this design is shown in  FIG. 5B  wherein there is provided a variable diameter (and subsequently a cross-section area) of the insert  29  along its length. Preferably, the diameter of the insert  29  increases toward the downstream end of the inlet manifold  11  so as to reflect a reduction in the refrigerant mass flow rate and accordingly impede the flow to the downstream channels  13 . Obviously, other geometric characteristics may be varied in a similar fashion to cause an identical overall effect on a hydraulic resistance change along the insert  29  axis. 
         [0037]    In each of the embodiments of the present invention as shown in  FIGS. 2-5 , the swirling high velocity motion that is imparted to the refrigerant flow tends to solve the problem of maldistribution of refrigerant, create homogeneous conditions and bring uniform refrigerant mixture to the entrance of the individual channels. At high refrigerant flow velocities, the droplets of the liquid refrigerant phase are driven to the periphery of the manifold by the centrifugal force so as to allow some of them to enter the channels closest to the header entrance. In cases of low refrigerant flow velocities, the swirling motion creates a momentum and jetting effect that tend to carry some of the liquid droplets to the remote channels in the manifold. Additionally, the swirling motion promotes mixing of liquid and vapor phases of refrigerant creating a homogeneous substance. Thus, the swirling motion tends to overcome the previous problems of maldistribution of refrigerant to the individual channels. 
         [0038]    It is well understood to a person ordinarily skilled in the art that any of the embodiments can be combined in a singled design if desired. Also, the teachings of the invention can benefit any heat exchanger orientation and configuration. 
         [0039]    While the present invention has been particularly shown and described with reference to preferred and alternate embodiments as illustrated in the drawings, it will be understood by one skilled in the art that various changes in detail may be effected therein without departing from the true spirit and scope of the invention as defined by the claims.

Technology Classification (CPC): 8