JP2014500469A - Plate type heat exchanger and air conditioning circuit for vehicle - Google Patents

Abstract

  The present invention relates to a vehicular plate type heat exchanger (30) for cooling a coolant with a coolant having a plurality of heat exchange plates (40) stacked on each other. Adjacent are a coolant chamber (44) and a coolant chamber (46), each having a coolant and / or coolant inlet (48, 52) and outlet (50, 4). Formed between the heat exchange plates (40), the coolant and / or coolant chambers (44, 46) are embodied and assigned in their entirety as U-shaped flow ducts (64, 68). The inlet (48, 52) is located at the end of the first protrusion of the U-shaped flow duct (64, 68) and the assigned outlet (50, 54) is the second protrusion. It is arranged at the end. The invention also relates to an air conditioning circuit (10) for a vehicle, in particular a vehicle with an electric motor, having a primary circuit (12) for coolant and a secondary circuit (14) for coolant. In the circuit, the primary circuit (12) and the secondary circuit (14) are coupled via a plate heat exchanger (30).

Description

  The present invention includes a plate-type heat exchanger for a vehicle for cooling a coolant with a coolant, having a plurality of heat exchange plates stacked on each other, and an air conditioning circuit for a vehicle, particularly a vehicle having an electric motor. About.

  Coolant or coolant flows through the intermediate space between adjacent plates, and coolant flows from the first side of the plate heat exchanger to the second side opposite the plate heat exchanger, A plate heat exchanger of the type defined at the beginning is known, in which the coolant flows in the opposite direction from the second end to the first end of the plate heat exchanger. The length of the flow duct in the plate heat exchanger here basically corresponds to the length of the plate heat exchanger from the first end to the second end. Thus, the external dimensions of the plate heat exchanger and the location of the connection of the plate heat exchanger depend on the desired length of the flow duct in the plate heat exchanger.

  The object of the present invention is to provide a plate heat exchanger having a compact design for a vehicle and an air conditioning circuit, which is embodied in a compact manner optimized for the installation space. be able to.

  The object of the present invention is achieved by a plate-type heat exchanger for a vehicle for cooling coolant with a coolant having a plurality of heat-exchange plates stacked on each other. In this plate-type heat exchanger, A coolant chamber and a coolant chamber are formed between adjacent heat exchange plates, and each of the coolant chamber and the coolant chamber has an inlet and an outlet for the coolant and / or the coolant. The coolant and / or coolant chambers are embodied in their entirety as U-shaped flow ducts, and the assigned inlet is located at the end of the first protrusion of the U-shaped flow duct. The assigned outlet is located at the end of the second protrusion. The U-shaped flow duct can double the length of the flow duct in the coolant chamber and / or the coolant chamber without increasing the length of the plate heat exchanger, and the coolant and / or It allows the coolant inlet and outlet connections to be aligned in a flexible manner.

  The heat exchange plates preferably have both a main range direction and a secondary range direction running perpendicular thereto in the plane of the plates and are perpendicular to the main range direction and the secondary range direction. Are arranged adjacent to each other in the stacking direction (hereinafter referred to as “direction definition”).

  According to this pre-defined direction definition, the coolant inlet and the outlet are preferably provided in the main range direction at the same end of the heat exchange plate. In this way, the coolant inlet and outlet can be positioned close to each other without reducing the length of the coolant flow duct.

  The heat exchange plate can be generally rectangular and the main range direction can then run in the longitudinal direction of the plate.

  A connection component is provided that allows the expansion valve for the coolant to be attached directly to the plate heat exchanger at the common inlet and outlet connections for all the coolant chambers. In this way, it is possible to dispense with a line system between the expansion valve and the plate heat exchanger.

  In order to achieve a uniform cooling performance in all the coolant chambers, the connecting component has a coolant distributor that homogenizes the distribution of the coolant phase mixture between the multiple coolant chambers of the plate heat exchanger. Can have.

  In the above definition of the direction, the coolant inlet and outlet are provided in the main range direction at the same end or both ends of the heat exchange plate. This allows a variable arrangement of connections for the coolant.

  In any case, provide a common inflow connection for all coolant chambers and a common outflow connection for flexible placement of the plate heat exchanger connection to the primary and secondary circuits In any case, a common inflow connection and a common outflow connection for all coolant chambers can be provided, and a common inflow connection and outflow connection for the coolant Similar to the inflow connection and the outflow connection for liquid, they are arranged in the stacking direction on the same side surface or both side surfaces of the plate heat exchanger.

  An end plate can be provided in the common inflow connection and / or outflow connection for all the coolant chambers, the end plates being arranged in the stacking direction in front of or behind the heat exchange plate and at least one for the coolant Forming two flow ducts, which connect the common inflow and / or outflow connections of the heat exchange plates to the connection for the coolant system. In this way, the end plate of the plate heat exchanger forms a kind of adapter, which allows a compact and suitably arranged connection to the coolant system.

  In the above definition of direction, a further embodiment provides that the inlet and outlet for the coolant are arranged in the main range direction on both sides of the heat exchange plate, similar to the inlet and outlet for the coolant. To provide that. Assuming the corresponding plate heat exchanger orientation, this connection arrangement allows a connection for the coolant at the top of the heat exchange plate and a connection for the coolant at the bottom of the heat exchange plate. To do. This therefore makes it possible easily to vent the coolant chamber on the one hand and return the oil in the coolant chamber on the other hand.

  The flow directions in adjacent coolant chambers and coolant chambers can be the same or opposite. The heat transfer between the coolant and the coolant along the flow duct can be optimized by selection of the coolant and coolant flow direction.

  According to a further embodiment, the heat exchange plate can form a flow duct in the coolant chamber, which flows from the coolant inlet at one end of the heat exchange plate in the main range direction. Run to the coolant outlet at the opposite end of the exchange plate.

  In order to improve the overall effectiveness of the heat exchange between the coolant and the coolant, the pressure differential through the first protrusion of the U-shaped flow duct for the coolant is The pressure difference through the second protrusion of the U-shaped flow duct for the coolant in the flow direction is between 70% and 100% of, preferably between 80% and 92%. Between 0% and 30% of the total pressure difference, preferably between 8% and 20%.

  The U-shape of the flow duct is preferably formed by an intermediate wall, which is provided by a part connecting adjacent heat exchange plates or by a molding part of at least one heat exchange plate. This allows for a simple design of the plate heat exchanger.

  In order to homogenize the distribution of coolant or coolant in the U-shaped flow duct, the protrusions of the U-shaped flow duct can be formed by a number of elongated ducts arranged adjacent to each other. .

  The invention also relates to an air conditioning circuit for a vehicle, in particular a vehicle having an electric motor, having a primary circuit for coolant and a secondary circuit for coolant, in which the primary circuit, the secondary circuit The circuit is coupled to the plate heat exchanger according to the present invention. The plate heat exchanger itself is a compact design and has a flexible arrangement of connections for the coolant and coolant, thus enabling a compact design that can be implemented in a flexible manner for the air conditioning circuit.

  Additional features and advantages of the present invention may be found in the following description and referenced accompanying drawings.

1 is a schematic diagram of an air conditioning circuit according to the present invention having a primary circuit for coolant and a secondary circuit for coolant. Sectional drawing of the plate type heat exchanger which concerns on this invention along sectional line II-II of FIG. The top view of the plate type heat exchanger which concerns on FIG. 2 in a lamination direction. FIG. 3 is a schematic view of the plate heat exchanger according to FIG. 2 with connections for coolant and coolant disposed on the same side of the plate heat exchanger. FIG. 3 is a schematic view of the plate heat exchanger according to FIG. 2 with connections for coolant and coolant disposed on both sides of the plate heat exchanger. The figure which shows a flow direction figure with the related temperature profile figure which concerns on the 1st Embodiment of this invention. The figure which shows a flow direction figure with the related temperature profile figure which concerns on the 2nd Embodiment of this invention. The figure which shows a flow direction figure with the related temperature profile figure which concerns on the 3rd Embodiment of this invention. The figure which shows a flow direction figure with the related temperature profile figure which concerns on the 4th Embodiment of this invention. FIG. 10 shows the plate heat exchanger according to FIG. 9 with a first arrangement of connections for coolant. The figure which shows the plate-type heat exchanger which concerns on FIG. The figure which shows the plate type heat exchanger which concerns on FIG. The schematic diagram of four heat exchange plates of the plate type heat exchanger concerning the present invention. The figure which shows the deformation | transformation embodiment of four heat exchange plates of the plate type heat exchanger which concerns on this invention. FIG. 3 is a detailed view of the plate heat exchanger according to FIG. 2 with a coolant distributor. FIG. 16 is a schematic view of various embodiments of the coolant distributor according to FIG. 15. FIG. 16 is a schematic view of various embodiments of the coolant distributor according to FIG. 15. FIG. 16 is a schematic view of various embodiments of the coolant distributor according to FIG. 15.

  FIG. 1 shows a schematic diagram of an air conditioning circuit 10 for a vehicle having a primary circuit 12 for coolant and a secondary circuit 14 for coolant.

  The vehicle is, for example, a vehicle with an electric motor, in particular a hybrid vehicle or a pure electric vehicle with a battery to be cooled by an air conditioning circuit.

  In the primary circuit 12, a compressor 16, a capacitor 18, and a dryer 20 are provided. The primary circuit 12 is divided into two secondary regions, each of which can be opened and closed by a valve 22.

  In the first secondary region of the primary circuit 12, an expansion valve 24 and a vaporizer 26 are provided. The carburetor 26 is a part of a vehicle air conditioning system for a vehicle passenger compartment.

  An expansion valve 28 and a plate heat exchanger 30 are provided in the second secondary region of the primary circuit 12. The plate heat exchanger 30 is further integrated with the secondary circuit 14, and allows the coolant in the secondary circuit 14 to be cooled by the coolant in the primary circuit 12.

  The secondary circuit 14 has a pump 32 that pumps coolant through the secondary circuit 14. The secondary circuit 14 also includes a storage device 34 for the coolant. A first cooling device 36 for the battery and a second cooling device 38 for the electronic components are arranged at various positions in the secondary circuit 14. The position of the cooling devices 36, 38 in the secondary circuit 14 may depend in particular on the required cooling performance.

  FIG. 2 shows a cross-sectional view of the plate heat exchanger 30. A plurality of heat exchange plates 40 are stacked on each other in the stacking direction 42, where coolant and / or coolant inlets 48, 52 and coolant chambers 44 each having outlets 50, 54 are provided. The cooling liquid chambers 46 are alternately formed between the adjacent heat exchange plates 40.

  On the right side of FIG. 2, an end plate 56 disposed in the stacking direction behind the heat exchange plate 40 is provided. In the embodiment shown, the end plate 56 serves to attach, for example, the plate heat exchanger 30. The end plate 56 can also be part of the housing of the plate heat exchanger 30.

  The heat exchange plate 40 has both a main range direction 58 and a secondary range direction 60 that runs perpendicular to it in the plane of the plates, the main range direction 58 and the secondary range direction 60 being: Each runs perpendicular to the stacking direction 42. In FIG. 2, the secondary range direction 60 runs perpendicular to the page.

  Multiple inlets 48 of multiple coolant chambers 44 are located in a straight line, thus forming a common inflow connection 49 for all coolant chambers 44. The common inflow connection 49 is provided with a connection component 62 that allows direct attachment of the expansion valve 28 to the plate heat exchanger 30. Such an expansion valve 28 has a small lateral distance between the inflow duct and the outflow duct. In the embodiment according to the present invention, these ducts are coaxial with the inlet 48 and the outlet 50.

  In a manner similar to the coolant inlet 48, the coolant inlets 52 of the multiple coolant chambers 46 are also positioned along a straight line and form a common inlet connection 53 for all the coolant chambers. On the left side of the plate heat exchanger 30, the pipe of the secondary circuit 14 is connected to a common inflow connection 53 of the coolant chamber 46.

  In a manner similar to the inflow connections 49, 53, all the outlets 50, 54 for coolant and / or coolant are embodied as a common outflow connection 51, 55.

  FIG. 3 shows a plan view of the plate heat exchanger 30 in the stacking direction 42. The heat exchange plate 40 is generally elongated and rectangular, and the main range direction 58 is in the longitudinal direction of the heat exchange plate 40. Shown in the area below the plate heat exchanger 30 is a connection component 62, which has a common inflow connection 49 for all the coolant chambers 44, and , Having a common outlet connection 51 for all the coolant chambers 44.

  The distance between the coolant inlet 48 and the outlet 50 in the coolant chamber 44 is smaller than the range of the heat exchange plate 40 in the main range direction 58. As shown in the following drawings, this small distance allows expansion valve 28 to be connected to plate heat exchanger 30 without the need for a coolant pipe or line between expansion valve 28 and plate heat exchanger 30. It can be attached directly to.

  The common inflow connection 53 and the common outflow connection 55 of all the coolant chambers 46 of the plate heat exchanger 30 are then arranged at small intervals in the upper region of the plate heat exchanger 30. .

  FIG. 4 is a plan view in the direction of the secondary range direction 60 and shows a schematic view of the plate heat exchanger 30. As can be clearly seen from this point of view, a common inflow connection 49 and a common outflow connection 51 for all the coolant chambers 44 and a common inflow connection 53 and a common outflow connection 55 for all the coolant chambers 46 Are arranged on the same side surface of the plate heat exchanger 30 with respect to the stacking direction 42.

  FIG. 5 shows a modified arrangement of the inflow connection 53 and the outflow connection 55 of the coolant chamber 46 on the opposite surface of the plate heat exchanger 30 with respect to the stacking direction 42. The inflow connection 49 and the outflow connection 51 of the coolant chamber 44 have a common connection component 62 in which the expansion valve 28 is directly provided.

  In any case, the pipeline element of the secondary circuit 14 is connected to the inflow connection 53 and the outflow connection 55 of the coolant chamber 46.

  FIG. 6 shows the coolant flow profile in the coolant chamber 44, the coolant profile in the coolant chamber 46, and the coolant and coolant temperatures for the first embodiment of the plate heat exchanger 30. Show the profile.

  The coolant passes through the inlet 48 and enters the coolant chamber 44 formed by two adjacent heat exchange plates 40. The coolant chamber 44 as a whole is a U-shaped flow duct 64, and the coolant inlet 48 is disposed at the end of the first protrusion of the U-shaped flow duct 64, The outlet 50 is disposed at the end of the second protrusion. The two protrusions of the U-shaped flow duct 64 are separated by an intermediate wall 66.

  “U” extends over substantially the entire length of the heat exchange plate 40.

  The coolant chamber 46 is embodied as a U-shaped flow channel 68 for coolant in a manner similar to the intermediate wall 66. The inlet 52 of the coolant chamber 46 is disposed at the end of the first protrusion of the U-shaped flow duct 68 in the coolant chamber 46, and the outlet 54 is disposed at the end of the second protrusion. The The U-shape of the coolant flow duct 68 is thus reversed compared to the coolant U-shaped flow duct 64, where the protrusions of the two flow ducts 64, 68 are Stacked together.

  In the embodiment according to FIG. 6, the flow directions of the coolant and the coolant in the adjacent coolant chamber 44 and the coolant chamber 46 in the two protrusions are opposed to each other.

FIG. 6 also shows the temperature profiles from position A ₁ to A ₂ at the first protrusion A and from position B ₁ to position B ₂ at the second protrusion B in both chambers 44, 46. Show. Coolant inflow temperature at 10 ° C. A ₂ and coolant outflow temperature at 4 ° C. B ₁ , and coolant inflow temperature at 4 ° C. A ₁ and coolant at 1 ° C. B ₂ Assuming an outflow temperature, an effective difference at a temperature Δtlog of 5.1K occurs at the protrusion A, and an effective difference at a temperature Δtlog of 3.6K occurs at the protrusion B, giving a total of 4. An average difference at a temperature Δtlog of 4K occurs between adjacent chambers 44 and 46, respectively. The greater the temperature difference between the coolant and the coolant, the better the heat exchange between the two.

  FIG. 7 shows a second embodiment of the plate heat exchanger 30, where the design is basically the same as the first embodiment. The second embodiment is different from the first embodiment in that the flow direction in the coolant chamber 44 is reversed. In the coolant chamber 44, the inlet 48 is therefore replaced with the outlet 50 compared to the first embodiment.

  Therefore, the flow directions in the adjacent coolant chamber 44 and coolant chamber 46 are the same.

The coolant now flows _first from B ₁ to B ₁₂ through the protrusion B of the U-shaped flow duct 64 and cools from 4 ° C. to 2 ° C. in this process. The coolant then flows through the protrusion A from A ₁ to A ₂ where it cools from 2 ° C. to 1 ° C. The saturation temperature is 0 ° C. As is clear from the temperature profile diagram, the temperature difference at the protrusion A is larger than that of the previous embodiment, where the effective temperature difference at Δtlog is 7K. In the protrusion B, the temperature difference is, in contrast, somewhat smaller, Δtlog is 2.5K. The average effective temperature difference through the flow duct is 4.7K in Δtlog. By making the flow direction the same in the adjacent coolant chamber 44 and coolant chamber 46, a U-shaped flow duct can surprisingly achieve an improved temperature difference, resulting in a plate type The effectiveness of the heat exchanger 30 is increased.

  FIG. 8 shows a third embodiment of the plate heat exchanger 30. The flow direction in the U-shaped flow ducts 64 and 68 of the coolant chamber 44 and / or the coolant chamber 46 is the same as in the second embodiment. In the third embodiment, the pressure difference through the protrusion B of the U-shaped flow duct 64 for the coolant is between 70% and 100%, preferably 80% and 92% of the overall pressure difference. Only that the pressure difference through the protrusion A is between 0% and 30% of the overall pressure difference, preferably between 8% and 20%. This is different from the second embodiment. In the protrusion B, which is the first protrusion in the coolant flow direction, the coolant is significantly cooled, reaching 0.5 ° C. in the illustrated example. Cooling occurs as a result of static pressure dropping due to pressure loss and as a result of decreasing coolant saturation temperature.

In contrast, no further cooling of the coolant in the protrusion A occurs because the saturation temperature is finally reduced by a minimum of about 0.5 K due to a small pressure drop in the protrusion A. However, this drop in temperature has superimposed 1 K coolant overheating, resulting in the temperature at the coolant outlet A ₂ of the protrusion A being 0.5 K higher than the inlet A ₁ . In this way, there can be a very large temperature difference between the coolant chamber 44 and the coolant chamber 46 in the region of the protrusion A, where the effective temperature difference at Δtlog is: 7.6K. In the protrusion B, the effective temperature difference at Δtlog is 3.2K. The average effective temperature difference between the two protrusions was 5.4K in Δtlog, resulting in further improvement in the effectiveness of the plate heat exchanger 30.

  The pressure difference at the two protrusions of the U-shaped flow duct 64 for the coolant can be achieved in various ways. In the example shown, the pressure difference is achieved by different flow resistances at the two protrusions of the flow duct 64. For this, various fin arrangements in the flow duct or various inserts in the flow duct are provided. Alternatively, for example, the intermediate wall 66 does not evenly divide the two protrusions of the U-shaped flow duct 64 so that the two protrusions can be embodied with different flow cross sections.

  FIG. 9 shows a fourth embodiment of the plate heat exchanger 30 in which only the coolant flow duct 64 in the coolant chamber 44 is embodied in a U shape. The position of the expansion valve 28 in the coolant chamber 44 is indicated by a dotted line. The embodiment of the coolant chamber 44 and the direction of coolant flow through the U-shaped flow duct 64 is similar to the third embodiment of the plate heat exchanger 30. In the fourth embodiment, the coolant chamber 46 has a coolant at the opposite end of the heat exchange plate 40 in parallel with the main range direction 58 from the coolant inlet 52 at one end of the heat exchange plate 40. It differs from the previous embodiment in that it has a flow duct 70 that runs to the outlet 54.

  The difference between the upper and lower temperature diagrams in FIG. 9 relates to the regions of the protrusions A and B of the coolant chamber 44. Region A and region B are part of the same flow duct 70 through which there is a unidirectional flow in the adjacent coolant chamber 46. The temperature profile of the coolant is therefore similar in both regions.

  The coolant temperature profile corresponds to the coolant temperature profile in the third embodiment of the plate heat exchanger 30.

  The effective temperature difference at the protrusion A is 5.64K in Δtlog, and the effective temperature difference in the region of the protrusion B is 4.63K in Δtlog.

  In the embodiment shown in FIG. 9, the flow duct 70 of the coolant chamber 46 does not require an intermediate wall 66. Therefore, what is required is to provide an intermediate wall 66 in the coolant chamber 44. The intermediate wall 66 is thus only required for every other chamber in the plate heat exchanger 30, which simplifies the design of the plate heat exchanger 30.

  Various connection variants for connecting the plate heat exchanger 30 to the secondary circuit 14 are provided in FIGS. 10, 11 and 12.

  FIG. 10 shows a perspective view of the plate heat exchanger 30, where the expansion valve 28 is provided at the lower part on the left side of the plate heat exchanger 30. Due to the space requirements of the expansion valve 28, the outlet connection 55 for the cooling liquid is only at the same end in the main range direction 58 of the plate heat exchanger 30 on the side surface located opposite the expansion valve 28 in the stacking direction 42. It is possible that there is. The inflow connection 53 located in the upper part in the main range direction 58 may be located on the same side in the laminating direction 42 as the outflow connection 55 on the side surface opposite to the laminating direction 42 as shown by the dotted line in FIG. it can.

  In the plate heat exchanger 30 shown in FIG. 11, an additional end plate 56 is provided on the side surface and is located on the opposite side of the expansion valve 28 of the plate heat exchanger 30 in the stacking direction 42. The end plate 56 forms a flow duct, indicated by a dotted line, for the coolant, which flows the common outlet connection 55 of the heat exchange plate 40 and the connection 72 for the coolant system of the secondary circuit 12. Connect to. By doing so, the common inflow and outflow connections 53, 55 of the coolant chamber 46 are located at both ends of the plate heat exchanger 30 in the main range direction 58, but the plate heat exchanger 30 Each of the line systems of the secondary circuit 14 can be provided at the same end in the main range direction 58.

  FIG. 12 shows a similar embodiment, where the coolant connection of the secondary circuit 14 is located on both sides of the surface of the plate heat exchanger 30 in the stacking direction 42.

  FIG. 13 then represents an embodiment of the plate heat exchanger 30, where the heat exchange plates 40 are each a flat design, separated by wall elements 74, a coolant chamber 44 and a coolant chamber. 46. Additional wall elements form an intermediate wall 66 that connects adjacent heat exchange plates 40.

  FIG. 14 shows a further embodiment of the plate heat exchanger 30, in which in each case two adjacent heat exchange plates 40 have a shaped part 76, both of which are cooled. An intermediate wall 66 of the liquid chamber 46 is formed. The intermediate wall 66 of the coolant chamber 44, in contrast, is formed by wall elements that connect adjacent heat exchange plates 40 together in a manner similar to FIG.

  An insert 78 that divides the coolant chamber 44 or coolant chamber 46 into small parallel ducts that run along the protrusions A and B in FIGS. 6-9 is shown in FIGS. 13 and 14 as coolant chamber 44 and coolant. It is provided in the chamber 46.

  FIG. 15 shows a detailed view of the plate heat exchanger 30 according to FIG. 2, where a throttle direction 80 is provided in the region of the connecting component 62. In the embodiment shown in FIG. 15, the throttle device 80 is a pipe having an adjusted diameter that protrudes at least partially from the connecting flange to one or more coolant chambers 44. A filter 82 is provided in front of the throttle device 80.

  FIG. 16 a shows an embodiment of a simple design of the coolant distributor 81, where the common inlet connection 49 of the coolant chamber 44 is provided with a relatively large opening compared to the throttle device 80. This opening causes only a part of the overall pressure difference between the high and low pressure, the remainder of the pressure difference being compensated by the expansion valve 28.

  FIG. 16 b shows an embodiment of a coolant distributor having pipes with adjusted diameters that extend into a common inlet connection 49 of the coolant chamber 44.

  As the coolant exits the reduced opening 81 or the pipe with the adjusted diameter, the mixture of coolant phases vortexes where the mixture is homogenized and between the multiple coolant chambers 44. Can be more uniformly distributed. In this way, uniform cooling performance in all the coolant chambers 44 is achieved.

  FIG. 16 c shows a coolant distributor 81 in the form of a distribution insert that allows for a homogeneous distribution of the coolant phase mixture between the multiple coolant chambers 44 of the plate heat exchanger 30.

Claims (14)

A plate-type heat exchanger (30) for a vehicle for cooling a coolant with a coolant having a plurality of heat exchange plates (40) stacked on each other,
A coolant chamber (44) and a coolant chamber (46) are formed between adjacent heat exchange plates (40), the coolant chamber (44) and the coolant chamber (46) may be formed of the coolant and / or Each has an inlet (48, 52) for cooling liquid and an outlet (50, 54),
The coolant and / or coolant chambers (44, 46) are embodied in their entirety as U-shaped flow ducts (64, 68), and the assigned inlets (48, 52) are: A plate-type heat exchanger, wherein the outlet is arranged at the end of the first protrusion of the U-shaped flow duct and the assigned outlet is arranged at the end of the second protrusion . The heat exchange plates (40) have both a main range direction (58) and a secondary range direction (60) running perpendicular thereto in the plane of the plates, and the main range direction ( 58) and the stacking direction (42) running perpendicular to the secondary range direction (60), and adjacent to each other,
The inlet (48) for the coolant and the outlet (50) are provided at the same end of the heat exchange plate (40) in the main range direction (58). Item 2. A plate heat exchanger according to Item 1.   A common inflow connection (49) for all the coolant chambers (44) and an outflow connection (51), the expansion valve (28) for the coolant being connected to the plate heat exchanger (30) 3. A plate-type heat exchanger according to claim 2, characterized in that a connecting component (62) is provided which allows direct attachment to the housing.   The connecting component (62) has a coolant distributor (81) for homogenizing the distribution of the coolant phase mixture between the different coolant chambers (44) of the plate heat exchanger (30); The plate-type heat exchanger according to claim 3. The heat exchange plates (40) have both a main range direction (58) and a secondary range direction (60) running perpendicular thereto in the plane of the plates, and the main range direction ( 58) and the stacking direction (42) running perpendicular to the secondary range direction (60), and adjacent to each other,
The inflow port (50) and the outflow port (52) for the coolant are provided in the main range direction (58) at the same end or both ends of the heat exchange plate (40). The plate type heat exchanger according to any one of claims 1 to 4. In any case, there is one common inflow connection (49) and a common outflow connection (51) for all the coolant chambers (44), and in any case, all the coolants A common inflow connection (53) for the chamber (46) and a common outflow connection (55);
The common inflow connection (49) for the coolant and the outflow connection (51) are similar to the inflow connection (53) and the outflow connection (55) for the coolant, and the plate heat exchanger (30 The plate-type heat exchanger according to any one of claims 1 to 5, wherein the plate-type heat exchanger is disposed in the stacking direction (42) on the same side surface or both side surfaces. A common inflow connection (53) and / or outflow connection (55) for all the coolant chambers (46);
An end plate (56) disposed in the stacking direction (42) in front of or behind the heat exchange plate (40) and forming at least one flow duct for the coolant;
The at least one flow duct connects the common inflow connection (53) and / or outflow connection (55) of the heat exchange plate (40) to a connection (72) for a coolant system. A plate heat exchanger according to any one of claims 1 to 6. The heat exchange plates (40) have both a main range direction (58) and a secondary range direction (60) running perpendicular thereto in the plane of the plates, and the main range direction ( 58) and the stacking direction (42) running perpendicular to the secondary range direction (60), and adjacent to each other,
The inlet (48) and the outlet (50) for the coolant are formed at both ends of the heat exchange plate (40) in the same manner as the inlet (52) and the outlet (54) for the coolant. The plate type heat exchanger according to claim 1, wherein the plate type heat exchanger is provided in the main range direction (58).   The plate heat exchanger according to claim 8, wherein the flow directions in the adjacent coolant chamber (44) and the coolant chamber (46) are the same or opposite. The heat exchange plate (40) forms a flow duct (70) in the coolant chamber (46),
The flow duct (70) extends from the coolant inlet (52) at one end of the heat exchange plate (40) to the opposite side of the heat exchange plate (40) in the main range direction (58). A plate heat exchanger according to any one of claims 1 to 7, characterized in that it runs to the coolant outlet (54) at the end.   The pressure difference through the first protrusion of the U-shaped flow duct (64) for the coolant is between 70% and 100% of the total pressure difference, preferably 80% and 92%. The pressure difference through the second protrusion of the coolant U-shaped flow duct (64) in the flow direction is between 0% and 30% of the total pressure difference 11. A plate heat exchanger according to any of claims 1 to 10, characterized in that it is preferably between 8% and 20%.   The U-shape of the flow duct (64, 68) is formed by a portion (74) connecting the adjacent heat exchange plates (40) or by a molding (76) of at least one heat exchange plate (40). The plate-type heat exchanger according to any one of claims 1 to 11, wherein the plate-type heat exchanger is formed by an intermediate wall (66) formed.   13. Plate according to claim 1, characterized in that the protrusions of the U-shaped flow ducts (64, 68) are formed by a number of elongated ducts arranged adjacent to each other. Mold heat exchanger. An air conditioning circuit (10) for a vehicle, in particular a vehicle with an electric motor, having a primary circuit (12) for coolant and a secondary circuit (14) for coolant;
Air conditioning characterized in that the primary circuit (12) and the secondary circuit (14) are coupled via a plate heat exchanger (30) according to any of claims 1 to 13. circuit.

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