Heat exchanger and vehicle air-conditioning device

Abstract

The invention provides a heat exchanger and a vehicle air-conditioning device provided with the heat exchanger, which can perform high-efficiency heat exchange, can realize cost reduction and space saving along with reduction of the number of parts, and can prevent damage of an external decoration (a shell) of the device. A heat exchanger (10) is provided with: a plurality of heat exchange cores (11) through which a first heat medium (m1) flows; and a case (3), the interior of which is divided into a plurality of housing chambers (30) by partitions (30P), the heat exchange cores (11) being housed in the housing chambers (30) adjacent to each other with the partitions (30P) therebetween, the housing chambers (30) being configured such that a second heat medium (m2) circulates therethrough, and heat exchange is performed between the second heat medium (m2) and the first heat medium (m1). The housing chambers (30) are configured so as to have an inlet (36) and an outlet (37) for the second heat medium (m2), the second heat medium (m2) is caused to flow through the housing chambers (30) and heat exchange is performed between the second heat medium (m2) and the first heat medium (m1), and a flow path (Fd) on the downstream side of the second heat medium (m2) is provided inside each housing chamber (30) at a position away from the partition (30P).

Description

Technical Field

[0001] The present invention relates to a heat exchanger and a vehicle air conditioner. Background Art

[0002] Conventionally, a heat exchanger including internal components and a housing has been known. The internal components are configured such that a refrigerant flows inside, and the housing is a container that houses the internal components and is configured such that cooling water flows in a space around the internal components (see Patent Document 1). The heat exchanger described in Patent Document 1 is mounted on a vehicle and is configured as a heat exchanger for exchanging heat between a refrigerant circulating in the vehicle and cooling water. One internal component is housed in a rectangular parallelepiped housing.

[0003] In addition, in a heat exchanger, a structure in which a condensing section and an evaporating section are assembled by a header tank is known (for example, see Patent Document 2).

[0004] Patent Document 1: Japanese Unexamined Patent Application Publication No. 2020-85340 Patent Document 2: Japanese Unexamined Patent Application Publication No. 2020-46101

[0005] However, for example, in a vehicle air conditioner or the like, there are a plurality of portions where a first heat medium (e.g., a refrigerant) and a second heat medium (e.g., cooling water or the like) exchange heat. Therefore, if the heat exchangers described in Patent Document 1 are respectively arranged at a plurality of necessary portions, problems such as an increase in cost and an increase in space due to an increase in the number of parts (especially the housing) occur.

[0006] In addition, when considering space saving of a vehicle air conditioner, a method of arranging the condensing section and the evaporating section that constitute the heat exchanger close to each other or integrating them as described in the technology of Patent Document 2 has also been considered. However, in this case, since the temperature difference between the heat media flowing in the two is large, there is a possibility of causing an adverse effect on other parts (e.g., exterior decoration, housing, etc.). Especially in the case where the exterior decoration (housing) of the heat exchanger is made of a resin material or the like, there is a problem that the housing is damaged due to thermal deformation caused by the temperature difference of the heat medium. Summary of the Invention

[0007] Therefore, an object of the present invention is to provide a heat exchanger and a vehicle air conditioner including the heat exchanger, which can perform highly efficient heat exchange, can achieve cost reduction and space saving by reducing the number of parts, and can prevent damage to the exterior decoration (housing) of the device.

[0008] The heat exchanger of the present invention includes: a plurality of heat exchange cores through which a first heat medium flows inside; and a housing whose interior is divided into a plurality of accommodation chambers by partition portions, and the heat exchange cores are respectively accommodated in the accommodation chambers adjacent to each other across the partition portions. The accommodation chambers are configured to respectively allow a second heat medium to flow inside, and heat exchange is performed between the second heat medium and the first heat medium. The accommodation chambers are configured to respectively have an inlet and an outlet for the second heat medium, and the second heat medium flows inside the accommodation chamber to perform heat exchange between the second heat medium and the first heat medium. Inside each of the accommodation chambers, the flow path on the downstream side of the second heat medium is provided at a position farther from the partition portion than the flow path on the upstream side of the second heat medium.

[0009] In addition, the present invention relates to a vehicle air conditioner including the above-described heat exchanger.

[0010] According to the present invention, a heat exchanger and a vehicle air conditioner including the heat exchanger can be provided, which can perform highly efficient heat exchange, can achieve cost reduction and space saving accompanied by reduction in the number of parts, and can prevent damage to the exterior decoration (housing) of the device. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] Figure 1 It is a schematic diagram showing a vehicle air conditioner according to an embodiment of the present invention. Figure 2 It is a schematic top view showing the heat exchanger of the present embodiment. Figure 3 It is a schematic top view showing the heat exchanger of the present embodiment. Figure 4 It is a perspective view of the heat exchanger of the present embodiment. Figure 5 It is a perspective view of the heat exchange core of the present embodiment. Figure 6 It is a schematic top view showing a modified example of the heat exchanger of the present embodiment. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0012] Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following description, the same reference numerals denote parts having the same function, and repeated descriptions of the respective drawings will be appropriately omitted. In addition, in each drawing, a part of the structure is appropriately omitted to simplify the drawing. Moreover, in each drawing, the size, shape, thickness, etc. of the components are exaggerated appropriately.

[0013] Figure 1FIG. 0 is a schematic diagram showing an example of the main structure of a vehicle air conditioner 100 including a heat exchanger 10 according to an embodiment of the present invention. The heat exchanger 10 of the present invention can be applied to various devices that exchange heat between a first heat medium m1 and a second heat medium m2. As an example, it can be used in a vehicle air conditioner 100. The first heat medium m1 is, for example, a refrigerant (e.g., a fluorocarbon refrigerant such as R134a, R1234yf, or a natural refrigerant such as CO2, R290), and the second heat medium m2 is a heat medium different from the first heat medium m1 (e.g., cooling water (LCC, water), antifreeze, cooling oil). In addition, in the present embodiment, the refrigerant refers to a circulating medium in a refrigerant circuit R that undergoes a state change in a heat pump (compression, condensation, expansion, evaporation). On the other hand, the second heat medium m2 is, for example, a circulating medium in a heat medium circuit including an internal combustion engine, a radiator, etc., and refers to a medium that absorbs and dissipates heat without undergoing a state change like a refrigerant. In the following description, the structure referred to as "refrigerant" corresponds to the first heat medium m1, and the structure referred to only as "heat medium" corresponds to the second heat medium m2.

[0014] The vehicle air conditioner 100 of the present embodiment can be mounted on a vehicle powered only by an internal combustion engine. However, compared with a vehicle powered only by an internal combustion engine, it can be appropriately applied to vehicles such as HEVs (Hybrid Electric Vehicles) where it is difficult to ensure sufficient heat only from the waste heat of the internal combustion engine, and EVs (Electric Vehicles) where the waste heat of the internal combustion engine cannot be used for heating. Vehicles such as HEVs and EVs are equipped with a battery (e.g., a lithium battery), and are driven and run by supplying the electric power charged from an external power source to a motor unit including a motor for driving. The vehicle air conditioner 100 is also driven by the electric power supplied from the battery.

[0015] <Overall Structure> As Figure 1 shown, the vehicle air conditioner 100 of the present embodiment includes, for example: a refrigerant circuit R in which a refrigerant (first heat medium) m1 represented by small arrows circulates; a first heat medium circuit 5 in which a heat medium (second heat medium) m2 represented by large arrows circulates; and a second heat medium circuit 6 in which a heat medium (second heat medium) m2 circulates. The air conditioning of the vehicle interior is performed by performing a heat pump operation using the refrigerant circuit R.

[0016] The first heat medium circuit 5 is, for example, a heat medium circuit on the high-temperature side in which the heat medium m2 circulates, and the heat medium m2 exchanges heat with the high-temperature refrigerant m1 flowing in the refrigerant circuit R. The second heat medium circuit 6 is, for example, a heat medium circuit on the low-temperature side in which the heat medium m2 circulates, and the heat medium m2 exchanges heat with the low-temperature refrigerant m1 flowing in the refrigerant circuit R. In the present embodiment, for the sake of convenience of explanation, the first heat medium circuit 5 is referred to as the high-temperature side heat medium circuit 5, and the second heat medium circuit 6 is referred to as the low-temperature side heat medium circuit 6.

[0017] As an example, the high-temperature side heat medium circuit 5 and the low-temperature side heat medium circuit 6 are connected by piping, and the flowing heat medium m2 is of the same type. However, this is not limited thereto, and the high-temperature side heat medium circuit 5 and the low-temperature side heat medium circuit 6 may also be independent circuits not connected by piping. In this case, the heat medium m2 flowing in each heat medium circuit may also be of different types.

[0018] <Refrigerant Circuit> The refrigerant circuit R is constituted by connecting a compressor 1, a heat exchanger 10, an expansion mechanism 4, etc. by piping (refrigerant piping) 70. The compressor 1 sucks the refrigerant m1 from the upstream side in the refrigerant circuit R and compresses it, making the refrigerant m1 into a high-temperature and high-pressure gas and discharging it to the downstream side. The form of the compressor 1 is not particularly limited, and for example, a piston-type or scroll-type electric compressor is used. Although not shown in the drawings, in the refrigerant circuit R, a liquid reservoir for separating the liquid from the refrigerant m1 is provided on the upstream side of the compressor 1. The refrigerant circuit R allows the refrigerant m1, which has become a high-temperature and high-pressure gas by the compressor 1, to pass through the first heat exchanger 10A and dissipate heat from the refrigerant m1 to cool the refrigerant m1. The refrigerant m1 that has passed through the first heat exchanger 10A is decompressed by the expansion mechanism 4, passes through the second heat exchanger 10B and absorbs heat. Moreover, the low-pressure refrigerant m1 is compressed again by the compressor 1. This cycle is repeated.

[0019] <Heat Exchanger> The heat exchanger 10 of the present embodiment includes a first heat exchanger 10A and a second heat exchanger 10B. The first heat exchanger 10A exchanges heat, for example, between the heat medium m2 flowing through the high-temperature side heat medium circuit 5 and the refrigerant m1 flowing through the refrigerant circuit R. The second heat exchanger 10B exchanges heat, for example, between the heat medium m2 flowing through the low-temperature side heat medium circuit 6 and the refrigerant m1 flowing through the refrigerant circuit R.

[0020] <First Heat Exchanger> The first heat exchanger 10A is a refrigerant - heat medium heat exchanger having a refrigerant flow path CA and a heat medium flow path WA. The refrigerant flow path CA is connected to the refrigerant circuit R, and the heat medium flow path WA is connected to the high - temperature side heat medium circuit 5. In this example, the refrigerant flow path CA of the first heat exchanger 10A forms a part of the refrigerant circuit R and functions as a radiator (heater, condenser) for the refrigerant m1 in the refrigerant circuit R. In addition, the heat medium flow path WA of the first heat exchanger 10A forms a part of the high - temperature side heat medium circuit 5 and functions as a heat absorber for the heat medium m2 in the high - temperature side heat medium circuit 5.

[0021] <Second Heat Exchanger> The second heat exchanger 10B is a refrigerant - heat medium heat exchanger having a refrigerant flow path CB and a heat medium flow path WB. The refrigerant flow path CB is connected to the refrigerant circuit R, and the heat medium flow path WB is connected to the low - temperature side heat medium circuit 6. The refrigerant flow path CB of the second heat exchanger 10B forms a part of the refrigerant circuit R and functions as a heat absorber (cooler, evaporator) for the refrigerant m1 in the refrigerant circuit R. In addition, the heat medium flow path WB of the second heat exchanger 10B forms a part of the low - temperature side heat medium circuit 6 and functions as a radiator for the heat medium m2 in the low - temperature side heat medium circuit 6.

[0022] <Expansion Mechanism> The expansion mechanism 4 is composed of an expansion valve, a capillary tube, etc., and decompresses and expands the high - pressure refrigerant m1 that has passed through the first heat exchanger 10A into a low - pressure refrigerant m1.

[0023] <First Heat Medium Circuit> The first heat medium circuit (high - temperature side heat medium circuit) 5 is, for example, a circuit for circulating a heat medium m2 that can exchange heat with the refrigerant m1 in the refrigerant circuit R. For example, it is connected by piping (heat medium piping) 71 to a circulation pump 51, the first heat exchanger 10A, etc. The first heat medium circuit 5 circulates the heat medium m2, for example, via an indoor heat exchanger (such as a radiator of an HVAC (Heating Ventilation and Air - Conditioning) unit) not shown.

[0024] <Second Heat Medium Circuit> The second heat medium circuit (low - temperature side heat medium circuit) 6 is a circuit for circulating a heat medium m2 that can exchange heat with the refrigerant m1 in the refrigerant circuit R. For example, it is connected by piping (heat medium piping 71) to a circulation pump 61, the second heat exchanger 10B, etc. The second heat medium circuit 6 circulates the heat medium m2, for example, via a heat exchange section provided in a temperature control device (such as a battery, a motor, etc.) not shown.

[0025] Refer toFigure 2 and Figure 3 , which illustrates the heat exchanger 10 of the present embodiment. Figure 2 and Figure 3 is a top view schematic diagram showing the schematic structure of the heat exchanger 10 of the present embodiment. Figure 3 is in Figure 2 In the structure shown, a diagram schematically showing the flow paths (indicated by hollow arrows) of the second heat medium m2 in the first accommodation chamber 30A and the second accommodation chamber 30B respectively, and the illustration of the first heat exchange core 11A and the second heat exchange core 11B is omitted.

[0026] Although the descriptions such as up and down are adopted in the description of the present embodiment, the descriptions such as up and down are for facilitating the use to represent the relative relationship of each structure in the drawings. That is, if the heat exchanger 10 is arranged in the opposite up and down state to the illustrated state, the upper side described in the present embodiment becomes the lower side during installation. In addition, if the heat exchanger 10 is arranged horizontally and used, the up and down directions become horizontal, and if it is arranged obliquely and used, the up and down directions become obliquely up and down directions.

[0027] In the heat exchanger 10, a first heat medium (refrigerant) m1 and a second heat medium (a heat medium such as cooling water) m2 flow. However, in the present embodiment, for the convenience of description, the illustrated x-direction in which the refrigerant m1 flows is referred to as the flow direction x, the illustrated y-direction perpendicular to the flow direction x is referred to as the width direction y, and the z-direction perpendicular to the flow direction x and the width direction y is referred to as the stacking direction z for description. There are also cases where the flow direction of the refrigerant m1 changes, such as turning back inside the heat exchanger 10, but overall, the direction from the inflow side to the outflow side is taken as the flow direction x. In addition, in this specification, the xyz directions do not distinguish between the + direction and the - direction.

[0028] Referring to Figure 2 , the heat exchanger 10 of the present embodiment is configured as a single device in which the first heat exchanger 10A and the second heat exchanger 10B separated and shown in the Figure 1 shown loop are integrated. The heat exchanger 10 has a plurality of heat exchange cores 11 (here, the first heat exchange core 11A and the second heat exchange core 11B) and a single housing 3. The first heat exchange core 11A has an inlet 34A and an outlet 35A for the refrigerant m1, and a refrigerant flow path formed inside (the refrigerant flow path CA in Figure 1 ), and the details will be described later. The structure and size of the second heat exchange core 11B are the same as those of the first heat exchange core 11A. The second heat exchange core 11B has an inlet 34B and an outlet 35B for the refrigerant m1, and a refrigerant flow path formed inside ( Figure 1in the refrigerant flow path CB). Thus, in the first heat exchange core 11A and the second heat exchange core 11B, the refrigerant m1 flows inside each of them. In addition, as an example in the present embodiment, the structure and size of the second heat exchange core 11B are the same as those of the first heat exchange core 11A, but this is not limited thereto, and the first heat exchange core 11A and the second heat exchange core 11B may also be heat exchange cores with different structures and / or sizes.

[0029] During the process of the refrigerant m1 circulating in the refrigerant circuit R, its state and temperature change, and the high-temperature refrigerant m1 flows inside the first heat exchange core 11A. Hereinafter, the high-temperature refrigerant m1 flowing through the first heat exchange core 11A is referred to as the high-temperature refrigerant mh1. In addition, hereinafter, the inlet 34A and the outlet 35A of the first heat exchange core 11A are referred to as the high-temperature refrigerant inlet 34A and the high-temperature refrigerant outlet 35A.

[0030] On the other hand, the low-temperature refrigerant m1 flows inside the second heat exchange core 11B. Hereinafter, the low-temperature refrigerant m1 flowing through the second heat exchange core 11B is referred to as the low-temperature refrigerant mc1. In addition, hereinafter, the inlet 34B and the outlet 35B of the second heat exchange core 11B are referred to as the low-temperature refrigerant inlet 34B and the low-temperature refrigerant outlet 35B.

[0031] The housing 3 as a whole has a substantially hexahedral (e.g., substantially rectangular parallelepiped or substantially cube) shape and has a hollow internal space. Specifically, the housing 3 has a substantially square tubular main body 33 with both ends in the stacking direction z open, and upper and lower cover members covering the open portions of the main body 33 (not shown in Figure 1 ). The housing 3 is made of, for example, a resin material.

[0032] As Figure 2 , Figure 3As shown, the internal space of the shell 3 becomes a receiving chamber 30 capable of receiving the heat exchange core 11. Specifically, the shell 3 has a plurality of receiving chambers 30 (here, a first receiving chamber 30A and a second receiving chamber 30B). The internal space of the shell 3 is also roughly hexahedral (for example, roughly rectangular) along the outer shape, but is provided with a partition 30P that divides the internal space into two parts. The partition 30P is also made of, for example, a resin material, and the internal space is divided into a first receiving chamber 30A and a second receiving chamber 30B by the partition 30P. The first receiving chamber 30A and the second receiving chamber 30B both have a shape and size capable of receiving the heat exchange core 11. The first heat exchange core 11A is received in the first receiving chamber 30A to form a first heat exchanger 10A. In addition, the second heat exchange core 11B is received in the second receiving chamber 30B to form a second heat exchanger 10B. A predetermined gap G1 is ensured between the inner wall of the first containment chamber 30A and the outer surface of the first heat exchange core 11A (in this example, the four surfaces opposite to the inner wall of the first containment chamber 30A), and a predetermined gap G2 is also ensured between the inner wall of the second containment chamber 30B and the outer surface of the second heat exchange core 11B (in this example, the four surfaces opposite to the inner wall of the second containment chamber 30B). In addition, the inner wall of the first containment chamber 30A and the outer surface of the first heat exchange core 11A can also fit closely, that is, the size of the gap G1 is substantially 0 (zero). Similarly, the inner wall of the second containment chamber 30B and the outer surface of the second heat exchange core 11B can also fit closely, that is, the size of the gap G2 is substantially 0 (zero).

[0033] As an example, the housing 3, the first storage chamber 30A and the second storage chamber 30B are respectively Figure 2 When viewed from above in the stacking direction z shown, it is a rectangle (rectangle) whose length in the flow direction x is longer than the length in the width direction y. That is, when viewed from above, the first receiving chamber 30A has a short side SS1 and a long side LS1, and the second receiving chamber 30B also has a short side SS2 and a long side LS2. Moreover, the two receiving chambers 30A and 30B are arranged adjacent to each other in such a manner that the long sides LS1 and LS2 are aligned in the flow direction x. In addition, one of the opposite short sides SS1 of the first receiving chamber 30A is composed of a partition 30P and is shared with one of the opposite short sides SS2 of the second receiving chamber 30B. That is, the first receiving chamber 30A and the second receiving chamber 30B are adjacent to each other through the partition 30P.

[0034] The main body portion 33 of the housing 3 has opposite first and second side surfaces 33A and 33B, and opposite third and fourth side surfaces 33C and 33D. The first side surface 33A is composed of one pair of long side portions LS1 and LS2, and the second side surface 22B is composed of the other pair of long side portions LS1 and LS2. In addition, the fourth side surface 33D is composed of one short side portion (here, the short side portion SS1), and the third side surface 33C is composed of the other short side portion (here, the short side portion SS2).

[0035] The plurality of accommodation chambers 30 each include an inlet 36 (36A, 36B) and an outlet 37 (37A, 37B) for the heat medium m2, and the heat medium m2 flows inside the housing 3 (the first accommodation chamber 30A and the second accommodation chamber 30B). In this example, an inlet 36A communicating with the first accommodation chamber 30A is provided on the second side surface 33B (the long side portion LS1 of the first accommodation chamber 30A). Similarly, an inlet 36B communicating with the second accommodation chamber 30B is provided on the second side surface 33B (the long side portion LS2 of the second accommodation chamber 30B). In addition, an outlet 37A communicating with the first accommodation chamber 30A is provided on the fourth side surface 33D (the short side portion SS1 of the first accommodation chamber 30A), and an outlet 37B communicating with the second accommodation chamber 30B is provided on the third side surface 33C (the short side portion SS2 of the second accommodation chamber 30B).

[0036] In this example, a first heat exchange core 11A is accommodated in the first accommodation chamber 30A, and a high-temperature first heat medium m1 (high-temperature refrigerant mh1) flows inside the first heat exchange core 11A. Further, a second heat medium m2 that circulates in the high-temperature side heat medium circuit 5 and exchanges heat with the high-temperature refrigerant mh1 flows in the first accommodation chamber 30A. The temperature of the second heat medium m2 changes during the circulation in the high-temperature side heat medium circuit 5, and becomes the high-temperature side second heat medium m2 in the vehicle air conditioner 100 when flowing in the first accommodation chamber 30A. In the present embodiment, particularly in the description of the heat exchanger 10, for the sake of convenience of explanation, the second heat medium m2 flowing in the first accommodation chamber 30A is referred to as the high-temperature side heat medium mh2. In addition, the first accommodation chamber 30A is a high-temperature side accommodation chamber for the high-temperature side heat medium mh2 to flow. Hereinafter, the inlet 36A of the first accommodation chamber 30A is referred to as the high-temperature side heat medium inlet 36A, and the outlet 37A of the first accommodation chamber 30A is referred to as the high-temperature side heat medium outlet 37A.

[0037] The second heat exchange core 11B is housed in the second housing chamber 30B. A low-temperature first heat medium m1 (low-temperature refrigerant mc1) flows inside the second heat exchange core 11B. Further, a second heat medium m2 that circulates in the low-temperature side heat medium circuit 6 and exchanges heat with the low-temperature refrigerant mc1 flows in the second housing chamber 30B. In this case, the second heat medium m2 flowing in the second housing chamber 30B becomes the second heat medium m2 on the low-temperature side in the vehicle air conditioner 100, and in the present embodiment, particularly in the description of the heat exchanger 10, it is referred to as the low-temperature side heat medium mc2. Further, the second housing chamber 30B is a low-temperature side housing chamber through which the low-temperature side heat medium mc2 flows. Hereinafter, the inlet 36B of the second housing chamber 30B is referred to as the low-temperature side heat medium inlet 36B, and the outlet 37B of the second housing chamber 30B is referred to as the low-temperature side heat medium outlet 37B.

[0038] The second heat medium m2 (high-temperature side heat medium mh2) flowing into the first housing chamber 30A from the high-temperature side heat medium inlet 36A flows through the gap G1 between the inner wall of the first housing chamber 30A and the first heat exchange core 11A and the gap (described later) formed by the first heat exchange core 11, and flows toward the high-temperature side heat medium outlet 37A, and exchanges heat with the first heat medium m1 (high-temperature refrigerant mh1) flowing inside the first heat exchange core 11A.

[0039] Similarly, the second heat medium m2 (low-temperature side heat medium mc2) flowing into the second housing chamber 30B from the low-temperature side heat medium inlet 36B flows through the gap G2 between the inner wall of the second housing chamber 30B and the second heat exchange core 11B and the gap (described later) formed by the second heat exchange core 11B, and flows toward the low-temperature side heat medium outlet 37B, and exchanges heat with the first heat medium m1 (low-temperature refrigerant mc1) flowing inside the second heat exchange core 11B.

[0040] The heat exchanger 10 of the present embodiment houses two heat exchange cores 11 (11A, 11B) in one housing 3 (the housing 3 can be shared), and thus, compared with a structure in which each heat exchange core 11 is individually (separately) housed in a housing, the number of parts can be reduced, and cost reduction and space saving accompanying this can be achieved.

[0041] Further, the first housing chamber 30A and the second housing chamber 30B are reliably partitioned by a partition portion 30P and house the first heat exchange core 11A and the second heat exchange core 11B, respectively, and thus the first heat exchange core 11A and the second heat exchange core 11B can be regarded as different temperature control objects. That is, the second heat medium m2 that has been temperature-controlled to a desired temperature range can be supplied to different temperature control objects (the first heat exchange core 11A, the second heat exchange core 11B), respectively.

[0042] Specifically, for example, the first heat exchange core 11A is used as the high-temperature side heat exchange core 11A through which the high-temperature refrigerant mh1 flows in the vehicle air conditioner 100 (refrigerant circuit R), and the second heat exchange core 11B is used as the low-temperature side heat exchange core 11B through which the low-temperature refrigerant mc1 flows in the vehicle air conditioner 100 (refrigerant circuit R).

[0043] Here, the first accommodation chamber 30A and the second accommodation chamber 30B are reliably separated by the partition portion 30P, and the high-temperature side heat medium mh2 flowing in the first accommodation chamber 30A and the low-temperature side heat medium mc2 flowing in the second accommodation chamber 30B do not mix. On the other hand, the partition portion 30P is in a state where one surface contacts the high-temperature side heat medium mh2 and the other surface contacts the low-temperature side heat medium mc2, and a temperature difference is generated between the two surfaces of one (shared) partition portion 30P. If this temperature difference is too large, especially when the partition portion 30P and the housing 3 are made of resin, there is a possibility of thermal deformation occurring.

[0044] In the present embodiment, by studying the flow paths of the heat medium m2 (the high-temperature side heat medium mh2 and the low-temperature side heat medium mc2), the thermal deformation occurring in the housing 3 due to the temperature difference of the heat medium m2 is suppressed. The following will explain this.

[0045] Refer to Figure 3 , the flow path (high-temperature flow path F1) of the high-temperature side heat medium mh2 in the first accommodation chamber 30A flows from the high-temperature side heat medium inlet 36A to the high-temperature side heat medium outlet 37A. The high-temperature side heat medium mh2 passes through the heat medium flow path WA (described later) divided by the first heat exchange core 11A and actually flows in a complex path, but in the following description, it is macroscopically and schematically described as a path from the high-temperature side heat medium inlet 36A toward the high-temperature side heat medium outlet 37A. That is, the high-temperature flow path F1 is formed in a substantially L shape as a whole from the high-temperature side heat medium inlet 36A toward the high-temperature side heat medium outlet 37A.

[0046] If the flow path (low-temperature flow path F2) of the low-temperature side heat medium mc2 in the second accommodation chamber 30B is also macroscopically and schematically described, it is formed in a substantially L shape as a whole from the low-temperature side heat medium inlet 36B toward the low-temperature side heat medium outlet 37B.

[0047] Moreover, in this example, it is configured that the downstream side of the high-temperature flow path F1 (the region near the high-temperature side heat medium outlet 37A that is more downstream than the center of the high-temperature flow path F1 and especially includes the downstream end, the downstream region Fd1) is farther from the partition portion 30P than the upstream side of the high-temperature flow path F1 (the region near the high-temperature side heat medium inlet 36A that is more upstream than the center of the high-temperature flow path F1 and especially includes the upstream end, the upstream region Fu1).

[0048] Specifically, in this example, the high-temperature side heat medium flow inlet 36A and the high-temperature side heat medium flow outlet 37A are arranged such that the upstream region Fu1 of the high-temperature flow path F1 is close to the partition portion 30P and the downstream region Fd1 of the high-temperature flow path F1 is away from the partition portion 30P.

[0049] The high-temperature side heat medium flow inlet 36A is arranged near the partition portion 30P in the long side portion LS1 (the second side surface 33B), and the high-temperature side heat medium flow outlet 37A is arranged at a position close to the first side surface 33A in the short side portion SS1 (the fourth side surface 33D) opposite to the partition portion 30P. Thus, the high-temperature flow path F1 flows in the width direction y (the direction toward the first side surface 33A) along the partition portion 30P in the upstream region Fu1, gradually bends the flow path in the flow direction x toward the fourth side surface 33D, and flows along the first side surface 33A in the downstream region Fd1.

[0050] The low-temperature flow path F2 is arranged to be line-symmetric with the high-temperature flow path F1 with the partition portion 30P as the center. That is, it is configured such that the downstream side of the low-temperature flow path F2 (the region near the low-temperature side heat medium flow outlet 37B, which is more downstream than the low-temperature flow path F2 and includes the downstream end portion, the downstream region Fd2) is farther away from the partition portion 30P than the upstream side of the low-temperature flow path F2 (the region near the low-temperature side heat medium flow inlet 36B, which is more upstream than the low-temperature flow path F2 and especially includes the upstream end portion, the upstream region Fu2).

[0051] Specifically, in this example, the low-temperature side heat medium flow inlet 36B and the low-temperature side heat medium flow outlet 37B are arranged such that the upstream region Fu2 of the low-temperature flow path F2 is close to the partition portion 30P and the downstream region Fd2 of the low-temperature flow path F2 is away from the partition portion 30P.

[0052] The low-temperature side heat medium flow inlet 36B is arranged near the partition portion 30P in the long side portion LS2 (the second side surface 33B), and the low-temperature side heat medium flow outlet 37B is arranged at a position close to the first side surface 33A in the short side portion SS2 (the third side surface 33C) opposite to the partition portion 30P. Thus, the low-temperature flow path F2 flows in the width direction y (the direction toward the first side surface 33A) along the partition portion 30P in the upstream region Fu2, gradually bends the flow path in the flow direction x toward the third side surface 33C, and flows along the first side surface 33A in the downstream region Fd2.

[0053] The high-temperature-side heat medium mh2 flowing in the first accommodation chamber 30A is at the highest temperature near the high-temperature-side heat medium outlet 37A after being heat-exchanged by the first heat exchange core 11A, and is at a lower temperature near the high-temperature-side heat medium inlet 36A than near the high-temperature-side heat medium outlet 37A. In addition, the low-temperature-side heat medium mc2 flowing in the second accommodation chamber 30B is at the lowest temperature near the low-temperature-side heat medium outlet 37B after being heat-exchanged by the second heat exchange core 11B, and is at a higher temperature near the low-temperature-side heat medium inlet 36B than near the low-temperature-side heat medium outlet 37B. That is, near the high-temperature-side heat medium outlet 37A and the low-temperature-side heat medium outlet 37B (the downstream regions Fd1 of the high-temperature flow path F1 and Fd2 of the low-temperature flow path F2), the temperature difference between the high-temperature-side heat medium mh2 and the low-temperature-side heat medium mc2 is larger than that near the high-temperature-side heat medium inlet 36A and the low-temperature-side heat medium inlet 36B (the upstream regions Fu1 of the high-temperature flow path F1 and Fu2 of the low-temperature flow path F2), and is the largest in the refrigerant circuit R.

[0054] Therefore, in the present embodiment, it is configured such that both the high-temperature-side heat medium outlet 37A and the low-temperature-side heat medium outlet 37B are provided at positions (as much as possible) away from the partition portion 30P, so that the downstream regions Fd1 of the high-temperature flow path F1 and Fd2 of the low-temperature flow path F2 are away from the partition portion 30P.

[0055] When heat media m2 with a large temperature difference flow on both sides across (in contact with) one (shared) partition portion 30P, there is a problem that the resin-made partition portion 30P and the housing 3 around it are thermally deformed and the housing 3 is damaged. In the present embodiment, the regions (opportunities) where the heat media m2 that can cause the temperature difference to become larger come into contact with each other across the partition portion 30P and other parts of the housing 3 can be minimized, so that the thermal deformation of the housing 3 caused by the temperature difference of the heat media m2 can be suppressed.

[0056] In addition, both the high-temperature-side heat medium inlet 36A and the low-temperature-side heat medium inlet 36B are provided at positions (as much as possible) close to the partition portion 30P. Thereby, the upstream regions Fu1 of the high-temperature flow path F1 and Fu2 of the low-temperature flow path F2 (regions where the temperature difference between the high-temperature-side heat medium mh2 and the low-temperature-side heat medium mc2 is small) flow on both sides along (in contact with) the partition portion 30P, and as the temperature difference between the two becomes larger, they become paths that leave the partition portion 30P and head towards the high-temperature-side heat medium outlet 37A and the low-temperature-side heat medium outlet 37B. That is, the upstream regions Fu1 of the high-temperature flow path F1 and Fu2 of the low-temperature flow path F2 with relatively small temperature differences can flow approximately along the vicinity of the partition portion 30P, so that the space for the heat media m2 with a large temperature difference to flow near the partition portion 30P can be reduced.

[0057] In addition, asFigure 2 As shown, the refrigerant m1 flowing in each of the heat exchange cores 11A and 11B flows in a manner opposite to the heat medium m2. Therefore, when considering the temperature difference between the high-temperature refrigerant mh1 and the low-temperature refrigerant mc1, the high-temperature refrigerant mh1 and the low-temperature refrigerant mc1 after approximately heat exchange, that is, the high-temperature refrigerant mh1 and the low-temperature refrigerant mc1 with a small temperature difference, also flow near the partition portion 30P, thereby also forming a structure capable of suppressing thermal deformation of the housing 3.

[0058] As a result, the high-temperature side heat medium inlet 36A and the low-temperature side heat medium inlet 36B are close to each other, and the high-temperature side heat medium outlet 37A and the low-temperature side heat medium outlet 37B are separated from each other (to the maximum extent). That is, the distance (distance between the outlets) L2 between the high-temperature side heat medium outlet 37A and the low-temperature side heat medium outlet 37B is greater than the distance (distance between the inlets) L1 between the high-temperature side heat medium inlet 36A and the low-temperature side heat medium inlet 36B. That is, by making the distance L2 between the outlets greater than the distance L1 between the inlets, the area (opportunity) where the heat media m2 with a larger temperature difference contact each other across the partition portion 30P and other parts of the housing 3 can be minimized, and thermal deformation of the housing 3 caused by the temperature difference of the heat medium m2 can be suppressed.

[0059] Furthermore, as Figure 2 shown, preferably, the first accommodation chamber 30A and the second accommodation chamber 30B are adjacently arranged such that their long side portions LS1 and LS2 are aligned (the extending directions are the same). In this case, the high-temperature side heat medium outlet 37A is provided at the short side portion SS1 (or the position of the long side portion LS1 farthest from the partition portion 30P) of the first accommodation chamber 30A opposite to the partition portion 30P, and the low-temperature side heat medium outlet 37B is provided at the short side portion SS2 (or the position of the long side portion LS2 farthest from the partition portion 30P) of the second accommodation chamber 30B opposite to the partition portion 30P. Thereby, compared with the case where the accommodation chambers 30A and 30B are adjacently arranged with the short sides SS1 and SS2 aligned, the distance L2 between the outlets can be increased. That is, the downstream region Fd1 of the high-temperature flow path F1 and the downstream region Fd2 of the low-temperature flow path F2 can be separated to the maximum extent, which is more preferable in terms of suppressing thermal deformation of the housing 3.

[0060] Here, regarding the distance between the inflow port 36 (inflow port 37) and the partition portion 30P, the "distance from the inflow port 36 (inflow port 37) to the partition portion 30P" refers to, for example, "the perpendicular distance from the opening portions OP of the inflow port 36 and the outflow port 37 to the surface of the partition portion 30P when viewed from above in the stacking direction z". The opening portions OP of the inflow port 36 and the outflow port 37 are, for example, opened in a substantially circular shape on the inner surface of the housing chamber 30, and are arranged parallel (opposite) or perpendicular to the surface of the partition portion 30P according to the positions of the inflow port 36 and the outflow port 37. In the case where the opening portion OP is arranged perpendicular to the surface of the partition portion 30P ( Figure 3 in the case of the inflow port 36), this distance is the perpendicular distance between the central axis C1 of the opening portion OP and the center in the thickness direction of the partition portion 30P (the plane passing through this center) C0 (refer to Figure 3 the distance d1). In the case where the opening portion OP is arranged parallel to the surface of the partition portion 30P (in an opposite manner) ( Figure 3 in the case of the outflow port 37), this distance is the perpendicular distance between the (plane) of the opening portion OP and the center in the thickness direction of the partition portion 30P (the plane passing through this center) (refer to Figure 3 the distance d2).

[0061] In addition, the distance L1 between the inflow ports (the distance L2 between the outflow ports) refers to, for example, "the perpendicular distance across the partition portion 30P between the opening portions OP when viewed from above in the stacking direction z". In the case where the opening portions OP are arranged perpendicular to the surface of the partition portion 30P ( Figure 3 in the case of the inflow port 36), this distance is the perpendicular distance across the partition portion 30P between the central axes C1 of the opening portions OP (refer to Figure 3 the distance d3). In the case where the opening portions OP are arranged parallel to the surface of the partition portion 30P (in an opposite manner) ( Figure 3 in the case of the outflow port 37), this distance is the perpendicular distance across the partition portion 30P between the (planes) of the opening portions OP (refer to Figure 3 the distance d4).

[0062] In addition, in the above example, the first heat exchange core 11A (the first housing chamber 30A) side is set as the high temperature side, and the second heat exchange core 11B (the second housing chamber 30B) side is set as the low temperature side, but the same applies even if they are replaced (the same applies in the following description).

[0063] Hereinafter, with reference to Figure 4 and Figure 5 , specific examples will be given to explain the heat exchanger 10 of the present embodiment in more detail. Figure 4 and Figure 5 The structures of the heat exchanger 10 shown in are examples, and the heat exchanger 10 is not limited toFigure 4 and Figure 5 the structure shown.

[0064] <Heat exchanger> Figure 4 is a perspective view of the exterior of the heat exchanger 10, Figure 5 is a perspective view of the heat exchange core 11. Referring to Figure 4 , the heat exchanger 10 has a housing 3 that houses the heat exchange core 11 therein, and the housing 3 has a substantially hexahedral outer shape. The housing 3 has a rectangular tubular main body portion 33 that is open at both ends in the stacking direction z, and an upper lid member 31 and a lower lid member 32 that cover the openings. Further, on the first accommodation chamber 30A side, a high-temperature refrigerant inlet 34A for the high-temperature refrigerant mh1 to flow in and a high-temperature refrigerant outlet 35A for the high-temperature refrigerant mh1 to flow out are provided at diagonal positions of the upper lid member 31. In addition, on the side of the first accommodation portion 30A, a high-temperature side heat medium inlet 36A for the high-temperature side heat medium mh2 to flow in is provided on the second side surface 33B of the housing 3, and a high-temperature side heat medium outlet 37A for the high-temperature side heat medium mh2 to flow out is provided on the fourth side surface 33D.

[0065] In addition, on the second accommodation chamber 30B side, a low-temperature refrigerant inlet 34B for the low-temperature refrigerant mc1 to flow in and a low-temperature refrigerant outlet 35B for the low-temperature refrigerant mc1 to flow out are provided at diagonal positions of the upper lid member 31. In addition, on the side of the second accommodation portion 30B, a low-temperature side heat medium inlet 36B for the low-temperature side heat medium mc2 to flow in is provided on the second side surface 33B of the housing 3, and a low-temperature side heat medium outlet 37B for the low-temperature side heat medium mc2 to flow out is provided on the third side surface 33C.

[0066] Figure 5 is a perspective view of one of the heat exchange cores 11 (for example, the first heat exchange core 11A). The first heat exchange core 11 (first accommodation chamber 30A) and the second heat exchange core 11B (second accommodation chamber 30B) have the same structure except for the heat medium flowing inside, so in Figure 5 , the first heat exchange core 11A and the second heat exchange core 11B, that is, the high-temperature side and the low-temperature side, are not distinguished for description.

[0067] <Heat exchange core> When the heat exchange core 11 (e.g., the first heat exchange core 11A) is viewed from above in the stacking direction z, two gaskets 15 are provided at diagonal positions. Each gasket 15 has a through hole, and the refrigerant inlet 34 (e.g., the high-temperature refrigerant inlet 34A) of the heat exchange core 11 is constituted by the through hole of one gasket 15, and the refrigerant outlet 35 (e.g., the high-temperature refrigerant outlet 35A) is constituted by the through hole of the other gasket 15. The heat exchange core 11 is housed in the housing 3 except for the two gaskets 15. The main part of the heat exchange core 11 is housed in the housing 3 and covered by the upper cover member 31 and the lower cover member 32 (see Figure 4 ).

[0068] The heat exchange core 11 includes: a core part 12 in which a plurality of heat exchange plates 2 are stacked in the stacking direction z; an upper end plate 13 provided above the core part 12 in the stacking direction z; and a lower end plate 14 provided below the core part 12 in the stacking direction z. The heat exchange plates 2, the upper end plate 13, the lower end plate 14, and the gaskets 15 are made of aluminum, and these aluminum parts are integrated by brazing for aluminum or the like to form the heat exchange core 11. The outer surface of the heat exchange core 11 may also be coated with resin so that the aluminum heat exchange core 11 is not deteriorated by the second heat medium m2. A flow path of the refrigerant m1 flowing from the refrigerant inlet 34 to the refrigerant outlet 35 is formed inside one heat exchange plate 2 ( Figure 1 the refrigerant flow paths CA, CB shown). In addition, a gap is ensured between the stacked (upper and lower) heat exchange plates 2 (the flow path bulging portions 221, 211), and this gap becomes a flow path of the second heat medium m2 ( Figure 1 the heat medium flow paths WA, WB shown).

[0069] The heat medium m2 flowing into the housing chamber 30 from the heat medium inlet 36 (e.g., the high-temperature side heat medium inlet 36A) is branched in the stacking direction z and the width direction y and passes between a plurality of heat exchange plates 2 and through the gap G1 between the side surface of the core part 12 and the housing 3, and flows out from the heat medium outlet 37 (e.g., the high-temperature side heat medium outlet 37A). As a result, as macroscopically and schematically shown, the heat medium m2 flows in the Figure 3 high-temperature flow path F1 shown (similarly in the low-temperature flow path F2). Moreover, in each heat exchange core 11, the first heat medium m1 and the second heat medium m2 flow in opposite directions. In this way, heat exchange is performed between the first heat medium m1 inside the heat exchange plate 2 and the second heat medium m2 outside the heat exchange plate 2.

[0070] <Modification example> Refer to Figure 6 to describe a modification example of the present embodiment. The heat exchanger 10 only needs to have a structure in which the region (opportunity) where the heat media m2 that can increase the temperature difference come into contact with each other across the partition portion 30P and other parts of the housing 3 is minimized. InFigure 6 In the figure, the high-temperature flow path F1 and the low-temperature flow path F2 are macroscopically and schematically represented by large arrows. In addition, the end side of the large arrow is the downstream regions Fd1 and Fd2, and the base end side is the upstream regions Fu1 and Fu2.

[0071] Figure 6 An example is to rotate the orientation (the flow direction x of the first heat medium m1) of each housing chamber 30A, 30B and the heat exchange cores 11A, 11B by Figure 2 90 degrees, and configure them in a manner where the short side portions SS1, SS2 are aligned. In this case, it becomes a structure where the long side portions LS1, LS2 face the partition portion 30P, and both the inlet 36 and the outlet 37 are provided on the short sides SS1, SS2.

[0072] In addition, in the Figure 6 shown structure, it can also be a structure where the outlet 37 is provided on the long side portions LS1, LS2.

[0073] In addition, in the Figure 2 shown structure, it can also be configured such that the inflow directions of the inlets 36A, 36B of the first housing chamber 30A and the second housing chamber 30B are opposite. Specifically, for example, the high-temperature side heat medium inlet 36A can be provided on the first side surface 33A, and the low-temperature side heat medium inlet 36B can be provided on the second side surface 33B. In addition, the positions of the outlets 37A, 37B respectively provided on the short side portions SS1, SS2 can be set at positions offset along the width direction y (for example, a position where one is close to the second side surface 33B and the other is close to the first side surface 33A).

[0074] Furthermore, in the Figure 2 shown structure, the two inlets 36 can also be provided at positions not adjacent to the partition portion 30P (such as near the approximate center of the long side portions LS1, LS2, etc.). As long as it is a structure where the downstream regions Fd1 of the high-temperature flow path F1 and the downstream region Fd2 of the low-temperature flow path F2 where the temperature difference between the high-temperature side heat medium mh2 and the low-temperature side heat medium mc2 is the largest are separated from (more separated than the upstream regions Fu1, Fu2) the partition portion 30P, the two inlets 36 do not necessarily have to be provided at positions adjacent to the partition portion 30P.

[0075] In addition, for example, in the Figure 2 shown structure, for example, the high-temperature medium outlet 37A can be provided at a position on the first side surface 33A close to the fourth side surface 33D, and the low-temperature medium outlet 37B can also be provided at a position on the first side surface 33A close to the third side surface 33D.

[0076] Figure 6The structures shown and the above-mentioned structure are both structures in which the distances from the flow outlets 37A and 37B to the partition portion 30P are greater than the distances from the flow inlets 36A and 36B to the partition portion 30P. Or it is a structure in which the distance L2 between the flow outlets is greater than the distance L1 between the flow inlets.

[0077] Thereby, the downstream regions Fd1 of the high-temperature flow path F1 and the downstream regions Fd2 of the low-temperature flow path F2, where the temperature difference between the high-temperature heat medium mh2 and the low-temperature heat medium mc2 can be maximized, can be separated from the partition portion 30P (separated by a greater distance than the distances between the upstream regions Fu1, Fu2 and the partition portion 30P).

[0078] In addition, Figure 6 The structures shown can also cause the upstream regions Fu1 of the high-temperature flow path F1 and the upstream regions Fu2 of the low-temperature flow path F2, where the temperature difference between the high-temperature heat medium mh2 and the low-temperature heat medium mc2 is small, to follow along the partition portion 30P. Therefore, thermal deformation of the housing 3 due to the temperature difference of the heat medium m2 can be suppressed.

[0079] In addition, although not shown in the drawings, a heat insulation member may be accommodated in the partition portion 30P, or the partition portion 30P may be constituted by a heat insulation member.

[0080] In addition, the refrigerant flow paths (similarly for the heat medium flow paths) provided in the plurality of heat exchange cores 11 may have the same shape in all the heat exchange cores 11, or the shape of the refrigerant flow paths in one or a part of the heat exchange cores 11 may be different from the shape of the refrigerant flow paths in other heat exchange cores 11.

[0081] In addition, the number of the accommodation chambers 30 and the heat exchange cores 11 may also be three or more, as long as it is a structure in which the downstream side flow paths Fd of the second heat medium m2 flowing inside the adjacent accommodation chambers 30 are provided at positions farther from the partition portion 30P than the upstream side flow paths Fu.

[0082] As described above, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the gist of the present invention. Description of Reference Numerals

[0083] 1 Compressor 3 Housing 5 High-temperature heat medium circuit 6 Low-temperature heat medium circuit 10 Heat exchanger 11 Heat exchange core 11, 11A, 11B Heat exchange cores 15 Gasket portion 30 Accommodation chamber 30P Partition portion 33 Main body portion 34 Refrigerant inlet 34A High-temperature refrigerant inlet 34B Low-temperature refrigerant inlet 35 Refrigerant outlet 35A High-temperature refrigerant outlet 35B Low-temperature refrigerant outlet 36 Inlet 36A High-temperature side heat medium inlet 36B Low-temperature side heat medium inlet 37 Outlet 37A High-temperature side heat medium outlet 37B Low-temperature side heat medium outlet 38 Flow chamber 70 Pipe (refrigerant pipe) 71 Pipe (heat medium pipe) F1 High-temperature flow path F2 Low-temperature flow path Fu Upstream side flow path Fd Downstream side flow path Fu1, Fu2 Upstream region Fd1, Fd2 Downstream region R Refrigerant circuit m1 Refrigerant (first heat medium) m2 Heat medium (second heat medium) mc1 Low-temperature refrigerant mc2 Low-temperature side heat medium mh1 High-temperature refrigerant mh2 High-temperature side heat medium.

Claims

1. A heat exchanger, characterized in that, Comprising: A plurality of heat exchange cores through which a first heat medium flows internally; and A housing whose interior is divided into a plurality of accommodation chambers by partition portions, The heat exchange cores are respectively accommodated in the accommodation chambers adjacent to each other across the partition portions, The accommodation chambers are configured such that a second heat medium flows through them respectively, and heat exchange occurs between the second heat medium and the first heat medium, The accommodation chambers are configured to respectively have an inlet and an outlet for the second heat medium, and the second heat medium flows through the accommodation chamber to perform heat exchange between the second heat medium and the first heat medium, Inside each of the accommodation chambers, the flow path on the downstream side of the second heat medium is provided at a position farther from the partition portion than the flow path on the upstream side of the second heat medium.

2. The heat exchanger according to claim 1, wherein Inside each of the adjacent accommodation chambers, the flow path on the upstream side of the second heat medium is provided at a position close to the partition portion.

3. The heat exchanger according to claim 1, wherein In the adjacent accommodation chambers, their respective inlets are provided at positions close to the partition portion, and their respective outlets are provided at positions far from the partition portion.

4. The heat exchanger according to claim 1, wherein In the adjacent accommodation chambers, the distance between their respective outlets is greater than the distance between their respective inlets.

5. The heat exchanger according to claim 1, wherein The temperature difference on the downstream side of the second heat medium flowing in the adjacent accommodation chambers respectively is greater than the temperature difference on the upstream side.

6. The heat exchanger according to claim 1, wherein In one of the adjacent accommodation chambers, the heat exchange core that functions as a heater is accommodated, and in the other, the heat exchange core that functions as a cooler is accommodated.

7. An air conditioning device for a vehicle, characterized in that It has the heat exchanger according to any one of claims 1 to 6.

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