JP2011085343A - Heat exchanger and air conditioning device for vehicle including the same - Google Patents

Abstract

A heat exchanger having sufficient pressure resistance performance without causing an increase in the number of parts or an increase in size is provided.
In a heat exchanger, header tanks (20A, 20B) are configured such that intermediate plates (60, 90) are sandwiched between a header plate (40) and a tank plate (50), and the intermediate plates (60, 90) are used as reinforcing members. It functions and improves the strength of the header tanks 20A and 20B.
On the intermediate plates 60 and 90 as the reinforcing elements, the bent portions 100 are formed between the center portions in the width direction of the header tanks 20A and 20B and both ends thereof. When the bent portion 100 is elastically deformed, for example, stress generated when the header tanks 20A and 20B are brazed and stress when the refrigerant pressure is applied are generated between the header plate 40, the tank plate 50, and the intermediate plates 60 and 90. Prevent concentration on the joint.
[Selection] Figure 4

Description

  The present invention relates to a heat exchanger and a vehicle air conditioner including the heat exchanger.

In a heat exchanger provided in an air conditioner, a plurality of heat exchange tubes constituting a refrigerant flow path between a pair of header tanks arranged to face each other, and heat exchange fins provided between these heat exchange tubes (For example, refer to Patent Document 1).
The header tank of such a heat exchanger is formed by brazing a combination of a plurality of plates. A space formed between these plates serves as a refrigerant flow path for the header tank.

JP-A-2005-300135

  However, when the conventional heat exchanger as described above is used as a heat exchanger for heating a heat pump, there is a problem that the pressure resistance is insufficient because the refrigerant pressure is high in the heat exchanger for the heat pump.

  As shown in FIG. 12, when the large pressure is applied because the cross-sectional shapes of the two flow paths 3a and 3b of the header tank 3 constituted by a plurality of plates 1 and 2 are irregular. This is because stress concentrates on the bent portion 3 c, the joint portion 3 d between the plates 1 and 2, the joint portion 3 e with the heat exchange tube 4, and the like.

On the other hand, as shown in FIG. 13, it is conceivable that the header tank 6 is formed of two tank pipes 7 and 8 having a circular cross section to ensure a sufficient pressure resistance.
However, in this case, in order to return the refrigerant that has flowed from the heat exchange tube 4 to the one tank pipe 7 to the other tank 8, it is necessary to separately provide a return flow path 9 and increase the number of parts, and the return flow path 9 is provided. This leads to an increase in the size of the heat exchanger. In the configuration shown in FIG. 12, the return of the refrigerant from one flow path 3a to the other flow path 3b is performed through a hole formed in the partition wall 5 provided between the flow paths 3a and 3b. Such a problem does not occur.
The present invention has been made based on such a technical problem, and an object of the present invention is to provide a heat exchanger having sufficient pressure resistance performance without causing an increase in the number of parts or an increase in size.

The heat exchanger of the present invention made for this purpose includes a plurality of heat exchange tubes arranged in parallel to each other, fins provided between adjacent heat exchange tubes, and a plurality of heat exchange tubes. A first header tank connected to one end side, and a second header tank connected to the other end side of the plurality of heat exchange tubes. The first header tank and the second header tank are sandwiched between a header plate into which ends of a plurality of heat exchange tubes are inserted, a tank plate facing the header plate, and the header plate and the tank plate. And an intermediate plate. The header plate, the tank plate, and the intermediate plate are joined to each other at the end portions and the intermediate portion on both sides in the width direction, so that one side of the intermediate portion is sandwiched between the tank plate and the header plate. A refrigerant flow path is formed on each of the other side, and the intermediate plate crosses the refrigerant flow path in a direction connecting the end part and the intermediate part in the refrigerant flow path, and the end part and the intermediate part approach each other. -It has the elastic deformation | transformation part which accept | permits the relative displacement of the direction to separate.
The first header tank and the second header tank are reinforced by an intermediate plate which is provided between the header plate and the tank plate and crosses the refrigerant flow path. Furthermore, since the intermediate plate has an elastically deforming portion, the end portion on both sides in the width direction where the header plate, the tank plate, and the intermediate plate are joined to each other and the intermediate portion are relatively displaced in a direction in which they approach and separate from each other Sometimes, the displacement can be allowed by the elastic deformation of the elastic deformation portion.

  Moreover, the recessed part which continues in the longitudinal direction of the said intermediate plate can also be formed in at least one surface of the width direction intermediate part of an intermediate plate. In this case, it is preferable that the header plate and / or the tank plate is formed with a convex portion having a shape corresponding to the concave portion at a portion facing the concave portion, and the concave portion and the convex portion are joined. By adopting such a configuration, the joining strength between the header plate and the intermediate plate, the tank plate and the intermediate plate can be increased.

At least one of the first header tank and the second header tank has a communication port formed in the intermediate plate that extends across both sides of the intermediate portion, and is provided on one side of the intermediate portion via the communication port. The refrigerant flow path and the refrigerant flow path on the other side communicate with each other. Thereby, a refrigerant | coolant can be returned to the refrigerant | coolant flow path of the other side from the refrigerant | coolant flow path of the one side which pinched | interposed the intermediate part.
At this time, the width in the longitudinal direction of the header tank at the communication port of the intermediate plate is preferably 2.0 mm or more and 3.8 mm or less. Thereby, the flowability of the refrigerant can be ensured while ensuring the strength of the intermediate plate, and the optimum width for preventing the deterioration of the heat exchanger performance can be obtained.

  The header plate, the tank plate, and the intermediate plate preferably each have a plate thickness of 1.0 mm to 2.0 mm. By doing in this way, intensity | strength can be ensured, suppressing the weight increase of the whole heat exchanger. In addition, the volume in the first and second header tanks is not made unnecessarily small, and an optimum plate thickness that suppresses the increase in pressure loss and prevents the performance deterioration of the heat exchanger can be obtained.

  Furthermore, the vehicle air conditioner can be configured by including any of the heat exchangers described above. Thereby, while suppressing the enlargement of the whole air-conditioning unit and preventing the heat exchanger performance from being lowered, a compact and high-performance air conditioner can be provided.

  According to the present invention, the first header tank and the second header tank are reinforced by the intermediate plate that is provided between the header plate and the tank plate and crosses the refrigerant flow path. Further, since the intermediate plate has an elastically deforming portion, the end portion on both sides in the width direction where the header plate, the tank plate, and the intermediate plate are joined to each other and the intermediate portion are relatively displaced in a direction in which they approach and separate from each other. Sometimes the displacement can be tolerated. Thereby, it can prevent that stress concentrates on the junction part of a header plate, a tank plate, an intermediate | middle plate, etc., and can improve the strength performance of a 1st header tank and a 2nd header tank. As a result, a heat exchanger having sufficient pressure resistance performance can be configured without increasing the number of parts or increasing the size.

It is a perspective view which shows the whole structure of the heat exchanger in this Embodiment. It is a perspective developed view which shows one structure of a header tank. It is a perspective perspective view which shows one side of a header tank. It is sectional drawing of a header tank. It is a figure for showing the composition of the intermediate plate provided in the header tank, (a) is a sectional view and (b) is a perspective sectional view. It is a perspective developed view which shows the other structure of a header tank. It is a perspective perspective view which shows the other of a header tank. It is a figure which shows the relationship between the board | plate thickness of the header plate in this Embodiment, a tank plate, and an intermediate | middle plate, and a breaking pressure. It is a figure which shows the relationship between the communicating slit of the intermediate | middle plate in this Embodiment, and a destructive pressure. It is a cross-sectional enlarged view which shows the recessed part provided in the intermediate | middle plate. It is a figure which shows the other example of an intermediate | middle plate. It is a figure which shows an example of the conventional header tank. It is a figure which shows the example of the header tank for improving a pressure | voltage resistant performance.

Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
FIG. 1 is a diagram showing an overall configuration of a heat exchanger 10 in the present embodiment.
The heat exchanger 10 includes a pair of header tanks (first header tank) 20A and header tank (second header tank) 20B, and a plurality of flat shapes provided in parallel between the header tanks 20A and 20B. Heat exchange tube 30 and corrugated fins 31 provided between the heat exchange tubes 30 and 30 adjacent to each other.

  As shown in FIGS. 2 to 4, the header tank 20 </ b> A includes a header plate 40 disposed on the side of the heat exchange tubes 30, 30... In the header tank 20 </ b> A, and an outer side of the heat exchanger 10 facing the header plate 40. And the intermediate plate 60 sandwiched between the header plate 40 and the tank plate 50.

The header plate 40 has a substantially W-shaped cross-section in a plane orthogonal to the axial direction of the header tank 20A, and a joining wall for joining the header plate 40 and the tank plate 50 on both sides in the width direction. The portions 41 and 41 are formed, and the joint surface portion 42 is formed in the intermediate portion in the width direction.
The joint walls 41 and 41 are formed so as to rise toward the side facing the tank plate 50.
The joint surface portion 42 is formed in a direction (surface) that connects the joint wall portions 41 and 41 on both sides.
Between the joining wall part 41 on both sides and the joining surface part 42 on the intermediate part, bulging parts 43 and 43 that bulge toward the opposite side of the opposing tank plate 50 are formed. A plurality of slits 44 having a shape corresponding to the cross-sectional shape of the heat exchange tube 30 are formed in the bulging portions 43 and 43 in order to insert the end portion of the heat exchange tube 30.

Similar to the header plate 40, the tank plate 50 has a substantially W-shaped cross section in a plane orthogonal to the axial direction of the header tank 20A. The header plate 40 and the tank plate 50 are provided on both sides in the width direction. Bonding wall portions 51 and 51 for bonding are formed, and a bonding surface portion 52 is formed in the intermediate portion in the width direction.
The joint walls 51 and 51 are formed so as to rise toward the side facing the header plate 40.
The joint surface portion 52 is formed in a direction (surface) connecting the joint wall portions 51 and 51 on both sides.
Between the joining wall part 51 of both sides and the joining surface part 52 of the intermediate part, the bulging parts 53 and 53 which bulge toward the opposite side to the header plate 40 which opposes are formed.

The intermediate plate 60 is substantially planar, and both end portions 61 and 61 in the width direction and the intermediate portion 62 are sandwiched between the header plate 40 and the tank plate 50.
In the intermediate plate 60, a plurality of openings 63 are formed between both end portions 61, 61 and the intermediate portion 62 on one side from the intermediate portion in the longitudinal direction of the intermediate plate 60.
Further, in the intermediate plate 60, a communication slit (communication port) 64 is formed between the both end portions 61, 61 on the other side from the intermediate portion in the longitudinal direction across the intermediate portion 62 and on both sides thereof. ing.

  Further, between the header plate 40 and the tank plate 50, closing plates 70A, 70B and 70C are respectively provided at one end side, the other end side and the intermediate portion in the longitudinal direction. The space between the plate 50 is closed.

The header plate 40, the tank plate 50, the intermediate plate 60, and the closing plates 70A, 70B, and 70C are joined together by brazing to form a header tank 20A.
In the header tank 20 </ b> A, the header plate 40 and the tank plate 50 are joined to each other via the intermediate plate 60 at the joining wall portions 41, 41 and 51, 51 at both ends and the joining surface portions 42 and 52 at the intermediate portion. Thus, as a whole, it has a glasses-like cross-sectional shape, and refrigerant flow paths 80A and 80B are formed on one side and the other side of the joint surface portion 52 in the width direction, respectively. These refrigerant flow paths 80A and 80B are divided into a refrigerant flow path 80A-1 and a refrigerant flow path 80A-2, and a refrigerant flow path 80B-1 and a refrigerant flow path 80B-2 by a closing plate 70C.

  As shown in FIG. 3 and FIG. 5, and on the side where the communication slit 64 of the intermediate plate 60 is formed with respect to the closing plate 70C, the refrigerant flow path 80A-2 and the refrigerant flow path 80B-2 are arranged on the header plate. The joint surface portion 40 of the 40 and the joint surface portion 52 of the tank plate 50 communicate with each other by a communication slit 64.

On the other hand, as shown in FIGS. 6 and 7, the header tank 20 </ b> B includes a header plate 40 disposed on the heat exchange tubes 30, 30... Side in the header tank 20 </ b> B and a heat exchanger 10 facing the header plate 40. The tank plate 50 is disposed on the outside of the tank plate 50, and the intermediate plate 90 is sandwiched between the header plate 40 and the tank plate 50.
In the header tank 20B, components common to the header tank 20A are frequently used. For this reason, in the following description, about the structure which is common with the said header tank 20A, the same code | symbol may be attached | subjected and the description may be abbreviate | omitted.

The intermediate plate 90 is substantially flat, and both end portions 91, 91 and the intermediate portion 92 in the width direction are joined wall portions 41, 41 at both end portions of the header plate 40, a joined surface portion 42 at the intermediate portion, and a tank plate. 50 are sandwiched between the joining wall portions 51 and 51 at both ends and the joining surface portion 52 at the intermediate portion.
A plurality of openings 93 are formed in the intermediate plate 90 along the longitudinal direction of the intermediate plate 90.

  Further, between the header plate 40 and the tank plate 50, closing plates 70 </ b> A and 70 </ b> B are provided at both ends in the longitudinal direction, respectively, and the space between the header plate 40 and the tank plate 50 is closed.

The header plate 40, the tank plate 50, the intermediate plate 90, and the closing plates 70A and 70B are joined together by brazing to form a header tank 20B.
As shown in FIG. 4, the header tank 20 </ b> B includes a header plate 40 and a tank plate 50, joint walls 41, 41 and 51, 51 at both ends thereof, and joint surfaces 42 and 52 at an intermediate part, and an intermediate plate 90. As a whole, they have a glasses-like cross-sectional shape, and refrigerant channels 80C and 80D are formed on one side and the other side of the joint surface portion 52 in the width direction, respectively. Yes. These refrigerant flow paths 80C and 80D are not in communication.

Here, the thickness of each of the header plate 40, the tank plate 50, and the intermediate plates 60 and 90 was examined.
FIG. 8 is an analysis result showing the relationship between the thickness of each of the header plate 40, the tank plate 50, and the intermediate plates 60 and 90 and the breaking pressure.
Here, the burst pressure is, for example, a header tank 20A in a case where the header tanks 20A and 20B may be damaged in a state where the volume of the refrigerant has expanded after heat exchange with air. , 20B represents the internal pressure applied to the inside.

  As an example of the present embodiment, when the refrigerant design pressure is about 3.0 MPa, a plate thickness that can withstand a breaking pressure of at least about 10.0 MPa or more is required as shown in FIG. As shown by the solid line in FIG. 8, the thickness of the intermediate plates 60 and 90 is 1.0 mm or more in order to ensure the strength. Further, the thicker the plate thickness of the intermediate plates 60 and 90, the greater the strength is ensured. However, the weight of the heat exchanger 10 as a whole increases, or the plate thickness of the intermediate plates 60 and 90 increases excessively. There is a possibility that the volume in the header tanks 20A, 20B becomes small, the pressure loss increases, and the performance of the heat exchanger 10 is deteriorated. For this reason, it is important to consider the strength of the header tanks 20A and 20B, the performance of the heat exchanger 10 and further the safety, and to obtain an optimum plate thickness.

  From the above analysis results, when the design pressure of the present embodiment is about 3.0 MPa, the plate thickness of the intermediate plates 60 and 90 that secure the strength that can withstand the breaking pressure up to 20.0 MPa is 2.0 mm or less. According to this, safety can be sufficiently ensured, and the optimum thickness can be obtained without degrading the performance of the heat exchanger 10. Accordingly, the thickness of each of the header plate 40, the tank plate 50, and the intermediate plates 60 and 90 is preferably 1.0 mm or more and 2.0 mm or less, more preferably 1.3 mm or more and 1 .. 5 mm or less.

  Here, how to obtain each plate thickness will be described. For example, when the header tack is cylindrical, the stress generated in the circumferential direction in the header tank is σ: generated stress, P: internal pressure, r: cylindrical internal radius, t, : Assuming the plate thickness, it is obtained by the following formula (1).

The header tank is destroyed when the generated stress σ exceeds the tensile strength σ _B , and the relationship of Expression (2) is established.

  The generated stress σ is expressed by the following equation (3), where L is the inner circumference (circumference) of the cylindrical header tank and A is the inner product (cross-sectional area).

  Therefore, the plate thickness t in the case of a cylindrical header tank is obtained by the following equation (4), and at least the plate thickness t is at least necessary for securing the strength.

  In the present embodiment, which is not a cylindrical header tank, it is necessary to make the thickness equal to or greater than the thickness t in Equation (4) in consideration of safety. Based on this, a coefficient α (coefficient considering safety) of the following equation is calculated, and an optimum plate thickness t is finally obtained from the following equation.

FIG. 9 is an analysis result showing the relationship between the communication slit 64 of the intermediate plate 60 and the fracture stress.
In the present embodiment, as described above, when the intermediate plate 60 has a thickness that can withstand a breaking pressure of 10.0 MPa or more, as shown by a solid line from the analysis result of FIG. 64 is preferably at least a slit width of 3.8 mm or less. As the slit width of the communication slit 64 is reduced, the strength of the intermediate plate 60 is ensured. However, if the slit width is too small, the refrigerant becomes difficult to pass through the communication slit 60, and the flowability of the refrigerant is impaired. This may lead to a decrease in heat exchanger performance. For this reason, when these are taken into consideration, the slit width of the communication slit 64 is preferably set to 2.0 mm or more. Furthermore, if the heat exchanger performance and safety (strength ensuring) are improved, the slit width of the communication slit 64 is preferably 2.5 mm or more and 3.0 mm or less.

  In the heat exchanger 10 configured as described above, the refrigerant that has flowed from the inlet 22A into the refrigerant flow path 80A-1 of one header tank 20A passes through the heat exchange tube 30 and flows into the refrigerant flow of the other header tank 20B. It flows into the road 80C. At this time, the refrigerant flows into one side corresponding to the refrigerant flow path 80A-1 in the refrigerant flow path 80C. Then, the refrigerant moves to the other side in the refrigerant flow path 80C, that is, the side corresponding to the refrigerant flow path 80A-2, and flows through the heat exchange tube 30 to the refrigerant flow path 80A-2 of one header tank 20A.

  The refrigerant that has flowed into the refrigerant flow path 80A-2 flows into the refrigerant flow path 80B-2 through the communication slit 64. Thereafter, the refrigerant passes through the heat exchange tube 30 from the refrigerant flow path 80B-2 and flows into the refrigerant flow path 80D of the other header tank 20B. At this time, the refrigerant flows into one side corresponding to the refrigerant flow path 80B-2 in the refrigerant flow path 80D. Then, the refrigerant moves to the other side in the refrigerant flow path 80D, that is, the side corresponding to the refrigerant flow path 80B-1, and flows through the heat exchange tube 30 to the refrigerant flow path 80B-1 of one header tank 20A. It is discharged from the outlet 22B to the outside of the heat exchanger 10.

Now, in this embodiment, as shown in FIGS. 4 and 5A, the intermediate plate 60 has a bent portion (elasticity) between the center portion in the width direction of the header tank 20A and both end portions thereof. (Deformation part) 100 is formed.
Here, the bent portion 100 is formed by bending the intermediate plate 60 into, for example, a crank shape between the center portion side 100a and the end portion side 100b of the header tank 20A, and thereby the center portion side 100a and the end portion side 100b. Are formed at different heights. The bending portion 100 is elastically deformed when the intermediate portion 62 of the intermediate plate 60 and the end portions 61 on both sides are relatively displaced in the directions approaching and separating from each other. Here, in the present embodiment, the distal end portion 30a of the heat exchange tube 30 inserted from the slit 44 abuts against the central portion side 100a of the intermediate plate 60 so as to form a gap with the end portion side 100b. Is provided.

  Further, the distal end portion 30 a of the heat exchange tube 30 can be configured to penetrate the intermediate plates 60 and 90 and be located closer to the tank plate 50 than the intermediate plates 60 and 90. In such a configuration, the rigidity of the header tanks 20 </ b> A and 20 </ b> B can be improved by the heat exchange tube 30.

  As shown in FIGS. 5 and 10, in the present embodiment, in the intermediate portions 62 and 92 of the intermediate plates 60 and 90, one surface and the other surface are continuous in the longitudinal direction of the intermediate plates 60 and 90. Recesses 95A and 95B are formed. Convex portions 96A and 96B having outer shapes corresponding to the concave portions 95A and 95B are formed on the joint surface portion 42 of the header plate 40 and the joint surface portion 52 of the tank plate 50, respectively. The concave portions 95A and 95B and the convex portions 96A and 96B can ensure a long contact length between the header plate 40, the tank plate 50, and the intermediate plate 60, and can improve the bonding strength.

  In the heat exchanger 10 as described above, the header tanks 20A and 20B are configured such that the intermediate plates 60 and 90 are sandwiched between the header plate 40 and the tank plate 50. Functions as a reinforcing member and can improve strength. Therefore, the heat exchanger 10 that can sufficiently cope with a high-pressure refrigerant can be configured. In addition, such header tanks 20A and 20B do not require a significant change in the manufacturing process as compared with the conventional case, and do not take time and effort. Moreover, since it is not necessary to increase the thickness of the header plate 40 or the tank plate 50, the header tanks 20A and 20B can suppress an increase in size, weight, and material cost of the heat exchanger 10.

In the header tank 20A, a communication slit 64 is formed in the intermediate plate 60 so that the refrigerant flow path 80A-2 and the refrigerant flow path 80B-2 communicate with each other, thereby securing a refrigerant return flow path in the header tank 20A. Has been. Therefore, it is not necessary to add the return flow path 9 as shown in FIG. 13 in order to secure the return flow path of the refrigerant, and also in this respect, an increase in the size of the heat exchanger 10 can be avoided.
In addition, openings 63 and 93 are formed in the intermediate plates 60 and 90, and the flow of the refrigerant is not obstructed in portions other than the communication slit 64.

  Since the bent portions 100 are formed between the center portions in the width direction of the header tanks 20A and 20B and the both end portions of the intermediate plates 60 and 90 as the reinforcing elements, the rigidity of this portion is set to other values. It can be made lower than the portion. Due to the elastic deformation of the bent portion 100, for example, the stress generated when the header tanks 20A and 20B are brazed and the stress when the refrigerant pressure is applied are generated between the header plate 40, the tank plate 50, and the intermediate plates 60 and 90. Concentration at the joint can be prevented. Thereby, the strength performance of the header tanks 20A and 20B can be improved.

  Further, since the intermediate plates 60 and 90 are formed with recesses 95A and 95B corresponding to the outer shapes of the joining surface portion 42 of the header plate 40 and the joining surface portion 52 of the tank plate 50, the header plate 40, the tank plate 50, And the contact length of the intermediate | middle plate 60 can be ensured long, and joining strength can be improved.

In the above-described embodiment, the specific shapes of the header tanks 20A and 20B have been exemplified. However, the cross-sectional shape and the openings 63 and 93 formed in the intermediate plates 60 and 90 and the communication are provided unless departing from the gist of the present invention. The shape, size, number, arrangement, and the like of the slits 64 can be changed as appropriate. For example, as shown in FIG. 11, the opening 63 can be a long hole whose major axis is the longitudinal direction of the intermediate plate 60 so as not to disturb the refrigerant flow as much as possible.
Further, the bent portion 100 is formed on the intermediate plates 60 and 90 between the center side 100a and the end side 100b of the header tanks 20A and 20B, and the intermediate portion 62 and the end portions 61 on both sides approach each other. Any other shape, material, etc. may be used as long as relative displacement in the separating direction is allowed.
In addition to this, as long as it does not depart from the gist of the present invention, the configuration described in the above embodiment can be selected or changed to another configuration as appropriate.

  DESCRIPTION OF SYMBOLS 10 ... Heat exchanger, 20A ... Header tank (first header tank), 20B ... Header tank (second header tank), 30 ... Heat exchange tube, 31 ... Fin, 40 ... Header plate, 41, 51 ... Joining Wall part, 42, 52 ... Joining surface part, 43, 53 ... Swelling part, 50 ... Tank plate, 60, 90 ... Intermediate plate, 61, 91 ... End part, 62, 92 ... Intermediate part, 63, 93 ... Opening, 64: Communication slit (communication port), 70A to 70C: Blocking plate, 80A, 80B, 80C, 80D ... Refrigerant flow path, 95A, 95B ... Recess, 96A, 96B ... Projection, 100 ... Bending part (elastic deformation part) )

Claims (6)

A plurality of heat exchange tubes arranged in parallel to each other;
Fins provided between the heat exchange tubes adjacent to each other;
A first header tank connected to one end side of the plurality of heat exchange tubes;
A second header tank connected to the other end side of the plurality of heat exchange tubes,
The first header tank and the second header tank are
A header plate into which ends of the plurality of heat exchange tubes are inserted;
A tank plate facing the header plate;
An intermediate plate sandwiched between the header plate and the tank plate,
The header plate, the tank plate, and the intermediate plate are joined to each other at the end portions and the intermediate portion on both sides in the width direction, thereby sandwiching the intermediate portion between the header plate and the tank plate. The refrigerant flow path is formed on each of the one side and the other side,
The intermediate plate crosses the refrigerant flow path in a direction connecting the end portion and the intermediate portion in the refrigerant flow path, and also has a relative displacement in a direction in which the end portion and the intermediate portion approach and separate from each other. A heat exchanger having an elastically deformable portion to allow. On at least one surface of the intermediate portion in the width direction of the intermediate plate, a concave portion continuous in the longitudinal direction of the intermediate plate is formed,
In the header plate and / or the tank plate, a convex portion having a shape corresponding to the concave portion is formed in a portion facing the concave portion, and the concave portion and the convex portion are joined. The heat exchanger according to claim 1.   In at least one of the first header tank and the second header tank, a communication port that extends across both sides of the intermediate portion is formed in the intermediate plate, and the intermediate portion is connected via the communication port. The heat exchanger according to claim 1 or 2, wherein the refrigerant flow path on one side sandwiched and the refrigerant flow path on the other side communicate with each other.   4. The heat exchanger according to claim 1, wherein a thickness of each of the header plate, the tank plate, and the intermediate plate is 1.0 mm or more and 2.0 mm or less. 5. .   The heat exchanger according to claim 3, wherein a width of the communication port of the intermediate plate is 2.0 mm or more and 3.8 mm or less.   A vehicle air conditioner comprising the heat exchanger according to any one of claims 1 to 5.

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