Abstract:
A kit for producing heat exchangers includes at least two types of heat exchanger cores in order to produce more than two different heat exchangers. The kit has a first type of heat exchanger core with a plurality of pairs of plates in order to produce a plurality of parallel flow paths between the plate pairs and a second type of heat exchanger core with a plurality of groups of three plates in order to produce a plurality of second parallel flow paths, one flow path being produced between two of each three plates.

Description:
[0001]    This nonprovisional application is a continuation of International Application No. PCT/EP2012/076859, which was filed on Dec. 21, 2012, and which claims priority to German Patent Application No. 10 2011 090 182.5, which was filed in Germany on Dec. 30, 2011, and which are both herein incorporated by reference. 
     
    
     BACKGROUND OF THE INVENTION 
       [0002]    1. Field of the Invention 
         [0003]    The invention relates to a kit for producing a heat exchanger in a plate design, particularly for motor vehicles, with a plurality of plate pairs and/or plate groups for forming flow paths, a heat exchanger core for forming heat exchangers, and a corresponding heat exchanger. 
         [0004]    2. Description of the Background Art 
         [0005]    Heat exchangers for motor vehicles are known in the conventional art. Thus, heat exchangers are already being used in many configurations and for many specific purposes in vehicles, for example, as evaporators, storage evaporators, oil coolers, condensers, charge air cooler, or coolant coolers. All of these heat exchangers have different configurations and types of construction, so that a different design is also often used for each type. 
         [0006]    DE 102006028017, which corresponds to U.S. Pat. No. 8,495,894, which is incorporated herein by reference, and which discloses an evaporator with a cold store, a so-called storage evaporator, in which an evaporator part is formed with double-row flat tubes, whereby a storage part, which is formed as a single row, is provided adjacent to said evaporator part of the heat exchanger and through an arrangement of double tubes, on the one hand, a refrigerant can flow through an inner flat tube and, on the other, a cold store medium can be disposed in a space between the inner flat tube and the outer flat tube or can flow through this region. 
         [0007]    In the conventional art, the production of a storage evaporator is a highly complex process, because a plurality of tubes and a plurality of parts must be fabricated and connected together. The evaporator part is typically a variation of a standard refrigerant evaporator, so that this structural element as well cannot be used as a standard version, but requires modification at least in regard to some structural elements. The storage evaporator therefore represents a special solution that cannot fall back on mass-produced parts. 
         [0008]    EP 1817534 B1, which corresponds to U.S. Pat. No. 8,122,943, discloses a storage evaporator, whereby in a first exemplary embodiment flat tubes are again inserted into one another that can be connected by means of connecting members to different refrigerant or cold storage material-media circuits. The production of such a storage evaporator again has a high parts complexity, which results in considerable additional costs. 
         [0009]    The embodiment of a storage evaporator in a plate design according to the second exemplary embodiment of EP 1817534 B1 also shows that a unique solution was again developed, which is of limited suitability for other applications. 
         [0010]    The heat exchangers in the conventional art are therefore adapted very particularly to the requirements of the specific medium in the circuit, so that wide use for different applications is more likely to be ruled out. 
       SUMMARY OF THE INVENTION 
       [0011]    It is therefor an object of the invention to provide a kit for producing a heat exchanger in a plate design, particularly for motor vehicles, with a plurality of plate pairs and/or plate groups for forming flow paths, which facilitates the production of different heat exchangers for different applications as well. Moreover, it is also as object of the invention to provide heat exchanger cores, which are used to form heat exchangers, and it is the object of the invention to provide such a heat exchanger. 
         [0012]    For the kit, this is achieved in an embodiment, whereby a kit is provided for producing heat exchangers with at least two types of heat exchanger cores for producing more than two different heat exchangers, whereby the kit advantageously comprises a first type of heat exchanger core with a plurality of pairs of plates to create a plurality of parallel flow paths between the pairs of plates and, further, comprises a second type of heat exchanger core with a plurality of groups of three plates to create a plurality of two parallel flow paths, whereby in each case a flow path is formed between two of the three plates, whereby a first heat exchanger with a heat exchanger core of the first type can be produced, whereby a second heat exchanger with two heat exchanger cores of the first type can be produced, whereby a third heat exchanger with a heat exchanger core of the first type and with a heat exchanger core of the second type can be produced, whereby a fourth heat exchanger with two heat exchanger cores of the second type can be produced, and a fifth heat exchanger with a heat exchanger core of the second type can be produced. It is advantageous according to the invention that the heat exchanger cores are designed in such a way that they can be used alone, can be combined and used with another core of the same type, and also can be combined and used with a heat exchanger core of the other type. 
         [0013]    As a result, when a heat exchanger core of the first type is used as a simple, narrow evaporator, it can thus be used as space-saving. This can occur advantageously in small vehicles with low required cooling capacities. 
         [0014]    In the case of higher required cooling capacities, if two heat exchanger cores of the first type are used, these can be arranged in a series or parallel connection to one another and used so that an increased cooling capacity with a double space requirement can be realized. 
         [0015]    When the heat exchanger is used as a storage evaporator, a heat exchanger core of the first type with a heat exchanger core of the second type can be used, whereby in this case the refrigerant can flow parallel or serially through flow paths of the first core and of the second core, whereby the cold store medium can flow through further flow paths of the second heat exchanger core. 
         [0016]    Two heat exchangers of the second type can also be connected together, so that, for example, an increased cooling capacity can be realized with a simultaneous cold store effect. 
         [0017]    Furthermore, the second type of heat exchanger core alone can be used, for example, as a two-row evaporator or as a one-row evaporator with a cold store. As a result, a storage evaporator with a lower cooling capacity is realized, for example. 
         [0018]    The heat exchanger cores of the first and/or second type can be provided with connecting devices and/or interconnecting devices for introducing and/or discharging and/or transferring fluid into or between or out of the heat exchanger cores or between flow channels of the heat exchanger cores. 
         [0019]    With respect to the heat exchanger core, in an embodiment, a heat exchanger core is provided in a plate design, particularly for use in a kit, for forming a heat exchanger, with a plurality of plate pairs for forming first flow paths, whereby in each case two plates of a plate pair form the first flow path between them and a region for second flow paths each is formed between adjacent plate groups. 
         [0020]    With respect to the heat exchanger core, in an embodiment, a heat exchanger core is provided in a plate design, particularly for use in a kit, for forming a heat exchanger, with a plurality of plate pairs for forming third and fourth flow paths, whereby the third flow path is formed between a first and a second plate of a plate group and the fourth flow path is formed between a second plate and a third plate of the plate group, and in each case a region for the fifth flow path is formed between adjacent plate groups. 
         [0021]    At least individual plates can have openings and/or wells as connecting and interconnecting regions and have channel-forming structures, such as embossings, for forming flow paths between connecting regions. 
         [0022]    The first plate and second plate of the plate pair at two opposite end regions in each case can have a connecting region as an inlet or outlet of the first flow path and a channel-forming structure between the two connecting regions to form the first flow path. 
         [0023]    The first plate and/or second plate of the plate pair at an end region can have two connecting regions as an inlet or outlet of the first flow path and a channel-forming structure between the two connecting regions to form the first flow path. 
         [0024]    The first plate, the second and third plate of the plate group at two opposite end regions in each case can have two connecting regions as an inlet or outlet of the third flow path or of the fourth flow path, whereby the first and second plate in each case between an opposite connecting region have a channel-forming structure between one of the two connecting regions to form the third and fourth flow path, whereby the third plate is provided between the first and second plate as a partition wall between the third and fourth flow path. 
         [0025]    In an embodiment, heat exchangers with at least two heat exchanger cores can have the distance of the plate pairs or the plate groups of a heat exchanger core to form the second and/or fifth flow paths selected in such a way that in the case of adjacent heat exchanger cores of a heat exchanger, it is the same or different, such as smaller or larger than in the adjacent heat exchanger core. 
         [0026]    The depth of the flow channels perpendicular to the plane, defined by the plate pairs or plate groups, can be selected individually for each flow channel. 
         [0027]    Further, plate pairs can be formed from a paired arrangement of plates and with a partition wall between adjacent plates, which form pairs of flow channels, characterized in that flow through the flow channels of a plate pair is a counterflow. 
         [0028]    Further scope of applicability of the present invention will become apparent from the detailed description given hereinafter. However, it should be understood that the detailed description and specific examples, while indicating preferred embodiments of the invention, are given by way of illustration only, since various changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art from this detailed description. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0029]    The present invention will become more fully understood from the detailed description given hereinbelow and the accompanying drawings which are given by way of illustration only, and thus, are not limitive of the present invention, and wherein: 
           [0030]      FIG. 1  illustrates an arrangement of two heat exchanger cores, a heat exchanger of a first type, and a heat exchanger of a second type; 
           [0031]      FIG. 2  illustrates an assembled arrangement of two heat exchanger cores; 
           [0032]      FIG. 3  illustrates an arrangement of two heat exchanger cores of a first type; 
           [0033]      FIG. 4  illustrates an arrangement of two heat exchanger cores of a second type; 
           [0034]      FIG. 5  illustrates a heat exchanger core of a first type; 
           [0035]      FIG. 6  illustrates a heat exchanger core of a second type; 
           [0036]      FIG. 7  illustrates two plates of a plate pair; 
           [0037]      FIG. 8  illustrates three plates of a plate group; 
           [0038]      FIG. 9  illustrates a number of plate pairs; 
           [0039]      FIG. 10  illustrates a number of plates and a detail of a plate; 
           [0040]      FIG. 11   a  illustrates a plate in detail; 
           [0041]      FIG. 11   b  illustrates a plate in a detail; 
           [0042]      FIG. 11   c  illustrates a pair of plates of a plate group in a detail; 
           [0043]      FIG. 11   d  illustrates a pair of plates of a plate group in a detail; 
           [0044]      FIG. 12  illustrates an arrangement of plate pairs and plate groups in a view; 
           [0045]      FIG. 13  illustrates an arrangement of plate pairs with plate groups in a view from the opposite side; 
           [0046]      FIG. 14  illustrates an arrangement of plate pairs and plate groups in a sectional cut through the plate pairs and the plate groups; 
           [0047]      FIG. 15  illustrates a plate with an overflow channel between adjacent passages; 
           [0048]      FIG. 16  illustrates the plate of  FIG. 15  from the back; 
           [0049]      FIG. 17  illustrates a view of a heat exchanger; 
           [0050]      FIG. 18  illustrates the view of plate pairs; 
           [0051]      FIG. 19  illustrates a view of plates; 
           [0052]      FIG. 20  illustrates a section of plates; 
           [0053]      FIG. 21  illustrates a section of plates; 
           [0054]      FIG. 22  illustrates a section of plate pairs; 
           [0055]      FIG. 23  illustrates a sectional cut through the plate pairs according to  FIG. 22 ; 
           [0056]      FIG. 24  illustrates a sectional cut through the plate pairs according to  FIG. 22 ; 
           [0057]      FIG. 25  illustrates a section of plate pairs; 
           [0058]      FIG. 26  illustrates a sectional cut through the plate pairs according to  FIG. 25 ; 
           [0059]      FIG. 27  illustrates a sectional cut through the plate pairs according to  FIG. 25 ; 
           [0060]      FIG. 28  illustrates a schematic view of a heat exchanger; and 
           [0061]      FIG. 29  illustrates a schematic view of a plate pair. 
       
    
    
     DETAILED DESCRIPTION 
       [0062]      FIG. 1  shows the arrangement of two heat exchanger cores  1 ,  2 , which can be connected together to form a heat exchanger. In this case, heat exchanger core  1  has a plurality of plate pairs  3 , which are arranged adjacent to one another, whereby corrugated fins  4  are arranged in free spaces between the particular adjacent plate pairs for better heat transfer during the flow of air between the particular adjacent plate pairs  3 . As a feed and discharge, plates  3  at their opposite ends have connections or openings, formed as such as cups  5 ,  6 , which are also used to connect plate pairs  3  to one another. 
         [0063]    Heat exchanger core  2  is formed with a plurality of plate groups  7 , whereby again adjacent plate groups  7  leave free spaces  8  for the flow of air, whereby a mount for corrugated fins can be provided for improved heat exchange for the flow of air. 
         [0064]      FIG. 1  thus shows an arrangement of two heat exchanger cores  1 ,  2 , whereby first heat exchanger core  1  is a heat exchanger core of a first type, formed with a plurality of pairs of plates to create a plurality of parallel flow paths between the pairs of plates. Within the plate pairs, a flow path is created for a fluid to flow through the plate, whereby entry and exit of the fluid into the plate or out of the plate is permitted through a connecting opening formed by a cup in the plate. 
         [0065]    Second heat exchanger core  2  is a heat exchanger core of the second type, which is formed with a plurality of groups of three plates to create a plurality of two parallel flow paths, whereby in each case a flow path is formed between two of the three plates. To this end, the plate groups at their two opposite ends each have two connecting openings for an inlet and outlet for a first and/or a second fluid, so that either two different fluids can flow through this heat exchanger core  2  in the particular different flow channels, or also in a different application a fluid can flow in different flow paths in two flows through the heat exchanger core, whereby at one of the two heat exchanger core ends a redirection of the fluid from the one flow path to the other flow path is then provided. Said redirection is not shown in  FIG. 1 , however. In this regard, reference is made to  FIGS. 15 and 16 , which show a plate  200 , where an overflow channel is provided as redirection between cups  201 . Inlets and outlets in second heat exchanger core  2  are evident in the circular or substantially circular openings  10 ,  11 , which are arranged at the top or bottom end region of the particular plate group. The plurality of adjacent plate groups form an inlet and outlet distribution channel via cup-shaped openings  10 ,  11  as connecting regions, so that a fluid flowing into the heat exchanger core through opening  10 ,  11  and the corresponding cup can be distributed over the length of the heat exchanger core before it can flow through the flow channels along the heat exchanger plate group, before it is again collected at the opposite end in the area of the cup connection, before the fluid can be conveyed out of the heat exchanger. This applies both to the flow channel between the first and the second plate and between the second and third plate. It is evident that opening  10  is adjacent to opening  11  and has a smaller cross section, so that different flow rates for the different media can be realized throughout. However, in a further exemplary embodiment it can also be expedient if openings  10 ,  11  of the flow paths are of the same size. 
         [0066]      FIG. 2  shows the arrangement of the two heat exchanger cores  1 ,  2  in an arrangement in which the heat exchanger cores are connected to one another, whereby a heat exchanger is produced that has a first core with a plurality of parallel flow paths, and has a second core with a plurality of two adjacent flow paths. 
         [0067]    Such a heat exchanger according to  FIG. 2  can be used, for example, as a storage evaporator, whereby a first flow path  12  between opening  5  and opening  6  is used as a refrigerant flow path and then a redirection occurs to opening  11  as an inlet, so that the refrigerant can flow through the flow path between the two openings  11 ,  11   a  as connections and then can leave the evaporator. Flow path  13  can be used between the openings as connections  10 ,  10   a  as the storage medium flow path, so that during normal operation of the evaporator the storage medium in this flow path is cooled and in case that the refrigerant circuit of the climate control system is in a start/stop situation, for example, the flowing air, indicated by arrow  14 , is cooled further by the heat exchange between the storage medium in flow path  13 , so that also during a temporary standstill phase of the refrigerant circuit of the climate control system a certain cooling capacity can still be provided during the start/stop operation. 
         [0068]    It is advantageous, if a heat exchanger core of  FIG. 1 , as labeled with reference character  1 , can also be used as a single heat exchanger, see  FIG. 5 , whereby such a heat exchanger  20  can be used, for example, as a plate evaporator in a climate control system with little available installation space. Said heat exchanger  20  as an evaporator would in fact provide only a reduced cooling capacity, but in small vehicles such as, for example, in small electric vehicles, this might be completely sufficient. Heat exchanger  20  has a core  25  of a plurality of plate pairs  26 , which are arranged spaced apart from one another, so that air can flow through interspaces  24  and can be cooled thereby. The airflow direction is indicated by arrow  27 . Plate pairs  26  have connections formed by cups, which are used to form the header space and are used for the mutual attachment to adjacent plate pairs. A fluid can flow into one connecting region, see arrow  21 , and the fluid can flow out again from an opposite connecting region, see arrow  22 . Flow path  23 , formed by the plate pair and through which the fluid flows lies between the two connecting regions. 
         [0069]    Furthermore, two such heat exchanger cores according to reference character  1  of  FIG. 1  can be used in a parallel connection or in a series connection, so that, for example, a two-row evaporator unit can be formed by two heat exchanger cores of the first type. This is shown in  FIG. 3 .  FIG. 3  shows a heat exchanger  30  made up of two heat exchanger cores  31 ,  32  of the first type. Each of the two heat exchanger cores  31 ,  32  have a plurality of plate pairs  33 ,  34 , each of which is arranged spaced apart from one another in a row in the particular core, so that, for example, air can flow through interspaces  35 ,  36  between plate pairs  33 ,  34  and can be cooled thereby. The airflow direction is indicated by arrow  37 . Plate pairs  33  have cup-shaped connections  38 ,  39 , which are also used to form header spaces  40 ,  41  and are used for the mutual attachment to adjacent plate pairs. Plate pairs  34  have cup-shaped connections  42 ,  43 , which are also used to form header spaces  44 ,  45  and are used for the mutual attachment to adjacent plate pairs. For example, a fluid can flow into first core  31  in a connecting region  38 . The fluid flows through flow channel  46  and can leave first core  31  at  39 . It is redirected in order to enter the second core at  43 . Next, the fluid flows through second flow channel  47  and out of an opposite connecting region  42  again flows out of second core  32 . The redirection is not shown; it can occur through a tube or the like. 
         [0070]    Alternatively, only one heat exchanger core according to reference character  2  of  FIG. 1  can be used (see  FIG. 6 ), whereby in this case a double flow is made possible, because each plate assembly group already forms two flow paths, through which flow can occur in different flow directions, so that this represents an alternative to an evaporator, for example, which can be used when only limited installation space is available.  FIG. 6  shows a heat exchanger  50  having only one heat exchanger core  51  of the second type. Heat exchanger core  51  has a plurality of plate groups  52  which are arranged spaced apart from one another in a row, so that, for example, air can flow through interspaces  53  between plate groups  52  and can be cooled thereby. The airflow direction is indicated by arrow  54 . Plate pairs  52  form two parallel flow channels  55 ,  56 , each of which is formed by two of the three plates of plate group  52 . 
         [0071]    The connections of the two flow channels or flow paths  55 ,  56  are formed by connections  57 ,  58 ,  59 ,  60 , which are formed as cups, which are also used to form the particular header spaces  61 ,  62 ,  63 ,  64  and are used for the mutual attachment to adjacent plate pairs or plate group. In a connecting region  57  a fluid can flow into first flow channel  55 , for example. The fluid then flows through flow channel  55  and as an outlet at cup  58  can leave first flow channel  55 . The fluid is then redirected in order to enter second flow channel  56  at cup  59 . Next, the fluid flows through second flow channel  56  from cup  59  to cup  60  and there, at the outlet located opposite to the inlet, again flows out of the second flow channel. The redirection is not shown; it can occur through a tube or the like. 
         [0072]    Furthermore, it would be possible to combine two heat exchanger cores according to reference character  2  of  FIG. 1 , i.e., two heat exchanger cores of the second type, to form a heat exchanger, which provides four flow paths, therefore two flow paths per heat exchanger core, in order to also enable four flows within the provided installation space, for example.  FIG. 4  shows such a heat exchanger  70 , which have only one first heat exchanger core  71  of the second type and one second heat exchanger core  72  of the second type. In order to avoid repetitions, the mode of action of the two heat exchanger cores  71 ,  72  will be explained according to the heat exchanger core of  FIG. 6 . In this case, for example, a fluid flows from a first core  71  and then is redirected to a second core  72 , and then flows through this second core  72 , before the fluid again leaves said core  72 . 
         [0073]      FIG. 7  shows two identically formed plates  80  and  81  of a plate pair  82  and are arranged laterally reversed to one another. The two plates each have a cup  83  and an opposite cup  84 , which are formed at opposite end regions of the plate. The cups point from the base surface  85  of the plate in a direction perpendicular to it, so that they protrude from base surface  85  of the plate. Furthermore, the plate has a circumferential edge  86 , which projects in the direction perpendicular to the plane of plate  85 , whereby edge  86  projects in the opposite direction than cup  87  or  88  of openings  83 ,  84 . If two plates are now connected to one another, they rest against one another at circumferential edges  86  and can there be sealingly soldered together. This has the effect that between the two plates a flow channel  89  arises that is used for flow through the plate and is in fluid communication with openings  83 ,  84 . 
         [0074]      FIG. 8  shows a plate group with plates  90 ,  91 , and  92 . In this case, plate  90  has a base plane  93  and a correspondingly projecting circumferential edge  94 , whereby openings  95  and  96  formed by circumferential cups, are provided at the two opposite ends, whereby the cups in regard to base plane  93  are embossed perpendicular thereto and project in a different direction than circumferential edge  94 . 
         [0075]    As is evident, flow channel  97  is embossed between openings  95  and is in fluid communication with them, whereby the flow channel is separated from opening  96  and is not in communication with it. 
         [0076]    Plate  91  is formed planar and at the two opposite ends each has openings  98 ,  99 , which are formed without cups, whereby plate  91  is also formed planar and has no embossed structures. If plate  90  is now placed on plate  91 , the two plates touch in the area of circumferential edge  94  and can be connected together fluid-tight so that, on the one hand, openings  98  are aligned with openings  95  and fluid channel  97  is defined between plate  90  and plate  91 , whereby openings  96  are aligned with openings  99 , but are not in communication with fluid channel  97 . 
         [0077]    Plate  92  also has openings  100 ,  101  at its opposite ends, whereby in base area  102  of the plate a fluid channel  103  is formed which communicates with openings  101 , whereby a circumferential edge  104  is formed projecting in a direction perpendicular to the plane of base surface  102 , whereby openings  100  are embossed in the circumferential edge and thus are not in fluid communication with flow channel  103 . Openings  100  and  101  are designed with cups projecting perpendicular to the direction of base plane  102 , whereby these project toward the back in  FIG. 8  and thus project opposite to circumferential edge  104 . 
         [0078]    If plate  92  is connected to plate  91 , a fluid-tight connection occurs in edge region  104  between the two plates, whereby openings  99  and  101  are each aligned and create a fluid communication to fluid channel  103 , and openings  98  and  100  align with one another but these openings do not have any fluid communication with fluid channel  103 . If plates  90 ,  91 , and  92  are now connected to one another, two fluid channels  97  and  103  arise, which are separated from one another by the interposition of plate  91 , and which are in communication with openings for the introduction and discharge of a fluid. Thus, openings  95 ,  98 , and  100  connect fluid channel  97  and openings  96 ,  99 , and  101  connect fluid channel  103 . 
         [0079]      FIG. 9  shows an arrangement of a plurality of plate pairs according to  FIG. 7 , whereby plate pairs  110  are soldered together and then connected to one another adjacently, so that they touch in the region of projecting cups  111  and thereby define a distance between the plate pairs that is greater than the extent of the plate perpendicular to the base plane of the plate, so that a region  112  remains open between the two neighboring plates for the flow, for example, of air. 
         [0080]      FIG. 10  shows a similar example of the arrangement of plate groups  113  according to  FIG. 8 , whereby these plate groups are also again connected together and adjacent plate groups come into contact with one another via projecting cups  114 ,  115 . A free space  116  is again opened between the plate groups for the flow, for example, of air. 
         [0081]      FIG. 11   a  shows a detail of a plate  82  according to  FIG. 7 , as does  FIG. 11   b , whereby plate  82  has a planar base region  85  compared with which circumferential edge  86  projects, whereby simultaneously opening  83  has a cup  87 , which projects in a different direction compared with base surface  85 . This can also be readily seen in  FIG. 11   b , so that cup  87  in  FIG. 11   b  projects forward compared with base surface  85 , whereby circumferential edge  86  in  FIG. 11   b  projects backwards. 
         [0082]    A similar situation can be seen in  FIGS. 11   c  and  11   d  for plates  90  and  92 , whereby plate  91  cannot be seen in this view of  FIGS. 11   c  and  11   d . Plates  92  and  90  each have at their opposite ends two openings  95  and  100  or  101  and  96 , whereby these openings are surrounded by cups, which project compared with base region  97  or  102  of the plates. As can be seen, flow channel  103  or flow channel  97  is in fluid communication with another opening, so that flow channel  97  is connected to opening  95 , whereas flow channel  103  is connected to opening  101 . If these plates are now placed one on top of the other according to  FIG. 8 , small openings  95 ,  100  can be connected to one another, while large openings  96  and  101  can be connected to one another. Fluid channels  97  or  103  are designed as to allow flow in conjunction with the particular openings, whereby the two flow channels  97  and  103  are separated from one another by the interposition of plate  91  (not shown). 
         [0083]      FIG. 12  shows the arrangement of plate pairs and plate groups in an adjacent arrangement, whereby the plate pairs of plates  82  are arranged in the air flow direction ahead of the arrangement of the plate groups of plates  90 ,  91 ,  92 . 
         [0084]    It can be seen that flow channel  85  is exposed to the air flow first before flow occurs around flow channel  97  or flow channel  103  (not shown).  FIG. 13  shows this from the other side, so that it can be seen that air first flows around flow channel  85  before it flows around flow channel  103 .  FIG. 14  shows this again in a sectional cut, whereby it is evident that flow channel  85  is formed by two plates  82 , whereby flow channels  97  and  103  are formed by plates  90 ,  91 , and  92 , whereby the two flow channels  90  and  103  in a direction perpendicular to the air direction together only occupy the region occupied by air channel  85  of the two plates  82 . 
         [0085]      FIG. 17  shows a heat exchanger  300  with a heat exchanger core, whereby heat exchanger core  301  is formed by a plurality of plate pairs, arranged in parallel and having two plates, which by the interposition of a partition wall form two flow paths between a plate and the partition wall. 
         [0086]    Heat exchanger  300  has a plurality of plate pairs  302 , arranged adjacent to one another, whereby corrugated fins  303  are preferably arranged between the plate pairs. Each plate pair (also see  FIG. 18 ) has two inlet openings  304 ,  305 ,  306 ,  307 , designed as cups, at a first end region and at a second end region. In this case, a cup of an end of region  304  or  305  forms an inlet-side cup, whereby the outlet-side cup associated with flow path  308  is arranged in the other end region. Accordingly, on each side in each end region, an inlet-side and an outlet-side cup is provided as a heat exchanger inlet or outlet. 
         [0087]      FIG. 18  to this end shows three plate pairs, shown spaced apart and having two plates and a wall inserted between them, whereby these plate pairs are arranged to form a plate packet  310 . 
         [0088]      FIG. 19  shows the arrangement of a plate pair, having plates  311  and  312 , whereby plate  311  forms a flow channel  313  and plate  312  a flow channel  314 . These flow channels are formed by embossings between two cups, whereby only two of the four shown cups are connected to the flow channel. Thus, cup  315  and cup  316  are connected to flow channel  313 , whereby cups  317  and  318  are not connected to flow channel  313 . In the case of plate  312 , cup  319  and cup  320  are connected to flow channel  314 , whereby cup  321  and cup  322  are not connected to the flow channel. If the two plates  311  and  312  with the interposition of wall  323  are soldered together, a fluid communication occurs between cups  315  and  321  and  316  and  322  and  318  and  319  and  317  with  320 , so that cups  315 ,  321  are an inlet cup for flow channel  313  and cups  317  and  320  are an outlet cup. The same applies to the arrangement of flow channel  314 . 
         [0089]      FIGS. 20 and 21  show the arrangements of cups  319 ,  321  of  FIG. 19  in an enlarged illustration, whereby cups  319  and  321  in  FIG. 20  are formed separated from one another and cup  319  is in fluid communication with flow channel  314 , whereas cup  321  is separated from flow channel  314 .  FIG. 21  also shows two cups  330  and  331 , whereby between the two cups  330  a crossover  332  is provided, allowing a fluid overflow from cup  330  to cup  331 . 
         [0090]      FIG. 22  shows a plate packet with three plate pairs in a perspective illustration with only the uppermost region of plate packet  340  being shown.  FIG. 23  shows a sectional cut along line  1  of  FIG. 22  and  FIG. 24  shows a sectional cut along line  2  of  FIG. 22 . It is evident that a plate pair  350 ,  351  each is provided with an intermediate layer  352 , whereby a flow channel  353  is arranged between plates  350  and  351  on one side of partition wall  352 , while a second flow channel  354  is arranged on the other side of the partition wall. This pattern repeats for each plate pair of the three shown plate pairs, so that in each case two flow channels  354 ,  353  are arranged between the plate pairs on both sides of partition wall  352 . 
         [0091]      FIG. 24  shows flow channels  353  and  354  likewise arranged on one side of partition wall  352 .  FIG. 25  shows plate packet  340 , whereby  FIG. 26  shows a sectional cut along line  3  of  FIG. 25 , and  FIG. 27  a sectional cut along line  4  of  FIG. 25 . 
         [0092]    In  FIGS. 26 and 27  plates  350  and  351  are shown with the interposition of partition wall  352 , whereby flow channels  354  and  353  can be seen. In sectional cut  3  it can be observed that the flow channels do not run over the entire width of the plate, whereas the flow channels in  FIG. 27  run substantially over the entire plate. This is so because the channel course toward the cup must be reduced from the substantially full width to about half the width. 
         [0093]    A heat exchanger, has a row of plate pairs, can be formed by the design of the plate pairs, whereby each half forms both a first flow channel connected to an inlet header or to an outlet header and a second flow channel, which is likewise provided with an inlet header and an outlet header. In this case, the cups, connected together in series, constitute the particular inlet header or outlet header. The particular plate pair has two opposite plates, whereby a partition wall or a partition sheet separating the flow channels of the particular plates from one another, is provided between the two plates. If the flow to the flow channels is a counterflow, the partition sheet is used to separate the opposite fluid flows through the flow channels, whereby the cups of the individual plate pairs, arranged in series to one another, form the fluid inlet header or the fluid outlet header. 
         [0094]      FIG. 28  shows the schematic arrangement of plate pairs  400 ,  401 , having an inflow-side cup  402  and an outflow-side cup  403 . The fluid flow occurs from the inlet-side cup  402  through flow channel  401  to a passover  404 , from where the fluid can flow into second flow channel  400 , in order to flow to cup  403 . This is carried out with the plate pairs arranged next to one another in rows, whereby the two flow channels  400  and  401  can be operated in counterflow to one another. 
         [0095]      FIG. 29  shows this in an enlarged illustration. Plate pair  401 ,  400  is provided with fins  405  on both sides for the flow of air. 
         [0096]    The invention relates to a heat exchanger with an internally integrated heat transfer with two flow channels operated in counterflow in a tube. 
         [0097]    The configuration of a heat exchanger in a plate design is described below; alternatively embodiments such as, e.g., those with a flat tube design are also possible. 
         [0098]    The heat exchanger has a row of plate pairs, half of which in each case have both a first flow channel connected to the inlet header or cup and a second flow channel connected to the outlet header or cup. The plate pair is again made up of two opposite plates and a partition sheet located between them. The partition sheet is used to separate the opposite fluid flows; the connected cups of the plate pairs, arranged in series, on the one hand, form the fluid inlet header for distributing the fluid to the individual first flow channels and, on the other, the fluid outlet header for collecting the fluid from the individual two flow channels. 
         [0099]    The two plates  311 ,  312  differ only in the transition region between the plate channel and cups; in fluid inlet plate  311  a flow connection is embossed between flow channel  313  and the fluid inlet cup, whereby in the case of fluid plate  312  a connection between flow channel  314  and the fluid outlet cup exists. 
         [0100]    These connection embossings can be carried out alternately in the plate tool and thus both plates can be produced in one and the same tool with an interchangeable set. This reduces the tool costs and increases the number of identical parts. 
         [0101]    The flow through the above-described heat exchanger is such that a fluid such as, for example, a refrigerant or coolant, etc., flows in over the first header as the inlet header, e.g., on the top block side into the first plate channel half  311 , then is conveyed via a connecting element between the two opposite headers, designated as the inlet header and outlet header at the lower block side, into the second plate channel half  312 , flows through it, and then again flows out of this second channel half via the second header, then again designated as an outlet header on the top block side. 
         [0102]    The advantage of this type of flow is the homogenization of the temperature profile, e.g., as an evaporator, by an equalization of the different temperatures of the opposite fluid flows based on the heat transfer between the two channel halves, on the one hand, and by an equalization of the temperature of the air flowing around the two channel halves, on the other. 
         [0103]    The connecting elements between the two opposite headers on the bottom block side can be a separate connecting part or can also be in a side part with an integrated redirection channel, or the like. 
         [0104]    In the case of a two-block connection, the fluid is simultaneously distributed via the inlet header to all first plate channel halves  311 , arranged in parallel, and is distributed further after the redirection by means of the connecting element to all second plate channel halves  312 . 
         [0105]    In a multiblock connection, the fluid is distributed simultaneously only to a certain number of first plate channel halves  311 , arranged in parallel, after which the fluid passover occurs from one header to the neighboring header directly in the plates, e.g., over embossed connecting channels between the adjacent header cups of a plate, before—after flowing through the second plate channel halves  312 —the fluid is conveyed further into the next block, and there the same distribution process continues as in the first block. 
         [0106]    The flow channel exchanger, such as particularly the plate evaporator, alternatively can also be of a single-tank design, i.e., with only one tank on one side of the heat exchanger. 
         [0107]    The interconnection of the individual modules can vary, depending on the arrangement and/or embodiment. 
         [0108]    A pressure drop is produced in the evaporator depending on the mass flow or operating point. 
         [0109]    Depending on the pressure drop, different absolute pressures arise and thereby different evaporation pressures between the evaporator inlet and outlet. 
         [0110]    This may cause the evaporation temperature at the evaporator inlet at great pressure drops to be much higher than the temperature associated with the evaporation pressure at the outlet. Depending on the arising pressure drop across the heat exchanger, this leads to a temperature response of the evaporating refrigerant. In addition, overheating of the refrigerant at the end of the evaporation at the evaporator outlet is desirable in order to produce a stable overheating signal at the injection valve (e.g., 5K). 
         [0111]    However, this creates local hot zones in the evaporator, which can be homogenized by suitable measures, such as, e.g., multiple interconnections one after the other in the air direction. 
         [0112]    By integration of an inner heat transfer surface in the evaporator over substantially the entire height, local hot zones between the evaporator inlet and outlet can be minimized. 
         [0113]    A stable overheating in the counterflowing refrigerant at the outlet can be produced between the incoming refrigerant by the heat transfer at the integrated inner heat transfer surface. Because of the much greater heat transfer, this occurs in a much smaller section of the evaporator than in conventional systems with multiple connections. 
         [0114]    The temperature of the flowing refrigerant through the evaporator reaches a lower average temperature level much quicker and the overheating zone in the evaporator can be reduced to a minimum. This results in a high driving average temperature gradient and an increase in performance associated therewith. 
         [0115]    The invention being thus described, it will be obvious that the same may be varied in many ways. Such variations are not to be regarded as a departure from the spirit and scope of the invention, and all such modifications as would be obvious to one skilled in the art are to be included within the scope of the following claims.