JP2015206507A - heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger capable of reducing thermal strain generated on a root portion of a header tank and tubes even when a width dimension of the header tank is reduced.SOLUTION: In a heat exchanger which includes a plurality of tubes 2 arranged in parallel with each other to circulate a fluid inside thereof, and a header tank 5 disposed on a longitudinal end portion of the tubes 2, extended in a parallel arrangement direction of the plurality of tubes 2, and communicated with the plurality of tubes 2, and in which the header tank 5 has a core plate 51 to which the plurality of tubes 2 are joined, and a tank body portion 52 fixed to the core plate 51, the core plate 51 has a tube joining face 511 to which the tubes 2 are inserted and joined, and a seal face 512 provided with an elastically deformable packing 53, and a thin portion 55 on which stress acting on the core plate 51 concentrates, is disposed at a side of the tube joining face 511 with respect to the seal face 512 of the core plate 51.

Description

  The present invention relates to a heat exchanger, and is effective when applied to a vehicle heat exchanger mounted on a vehicle.

  2. Description of the Related Art Conventionally, a header tank of a heat exchanger such as a radiator is configured by integrating a metal core plate to which tubes are joined and a resin tank main body forming a tank internal space. A packing (seal member) made of an elastic member such as rubber is disposed between the core plate and the tank main body. The core plate and the tank are compressed by compressing the packing between the core plate and the tank main body. The main body is sealed.

  Specifically, the core plate has a tube joint surface to which the tube is joined, and a groove formed at the outer peripheral edge of the tube joint surface. The core plate side tip portion of the tank main body portion is inserted into the core plate groove portion, and the tank is sandwiched between the core plate groove portion and the tank main body tip portion. The main body is caulked and fixed to the core plate.

  In the heat exchanger having such a configuration, since the groove portion is formed in the core plate, the length in the flow direction of the external fluid (air) in the core plate by the amount of the groove portion (hereinafter also referred to as the width direction dimension). Becomes longer. Thereby, there existed a problem that the width direction dimension as the whole heat exchanger became long.

  On the other hand, the heat exchanger which aimed at thickness reduction by eliminating the groove part of a core plate is disclosed (for example, refer patent document 1). Specifically, in the heat exchanger described in Patent Document 1, a packing is directly disposed on a tube joining surface to which a tube in a core plate is inserted and joined, and an end of a tank main body is disposed on the packing. Has been placed.

US Pat. No. 8,181,694

  By the way, in the conventional heat exchanger in which the tube is joined to the core plate of the header tank, when thermal distortion occurs due to the difference in thermal expansion between the tube and the core plate, the core against the displacement due to the thermal expansion of the tube. Due to the bending of the plate, the thermal strain generated at the root portion (joint portion) between the core plate and the tube is reduced.

  However, in the heat exchanger described in Patent Document 1, the distance from the tube insertion portion in the core plate to the outer end surface in the width direction is shortened, so that thermal distortion due to the difference in thermal expansion occurs between the tube and the core plate. In this case, the amount of deformation on the core plate side is reduced. Thereby, there is a problem that thermal strain is not absorbed and large thermal strain is generated at the root portion (joint portion) between the core plate and the tube.

  In view of the above points, the present invention has an object to provide a heat exchanger that can reduce the thermal distortion generated at the root portion of the header tank and the tube even if the width dimension of the header tank is reduced. To do.

  In order to achieve the above object, according to the first aspect of the present invention, a plurality of tubes (2) that are arranged in parallel with each other and in which a fluid circulates are disposed at the longitudinal ends of the tubes (2). And a header tank (5) that extends in the direction in which the plurality of tubes (2) are juxtaposed and communicates with the plurality of tubes (2). The header tank (5) is joined to the plurality of tubes (2). In the heat exchanger having a core plate (51) and a tank body (52) fixed to the core plate (51), the tube (2) is inserted and joined to the core plate (51). It has a tube joint surface (511) and a seal surface (512) on which an elastically deformable seal member (53) is arranged, and the tube joint surface (512) rather than the seal surface (512) in the core plate (51). 511 The side, characterized in that the stress concentration portion where the stress acting on the core plate (51) is concentrated (55, 57) is provided.

  According to this, the tube (2) and the core plate (51) are provided by providing the stress concentration portion (55, 57) closer to the tube joint surface (511) than the seal surface (512) in the core plate (51). When a thermal strain due to a difference in thermal expansion occurs during this period, the stress concentration portions (55, 57) serve as bending starting points, and the core plate (51) can be positively bent. For this reason, the amount of bending of the core plate (51) is increased, and the thermal strain generated between the tube (2) and the core plate (51) can be absorbed. Therefore, even when the dimension in the width direction of the header tank (5) is reduced, it is possible to reduce thermal distortion generated at the root portion between the header tank (5) and the tube (2).

  Moreover, in invention of Claim 6, while being arrange | positioned in parallel mutually, it arrange | positions at the longitudinal direction edge part of the several tube (2) through which a fluid distribute | circulates inside, and a tube (2), and several A header tank (5) that extends in the juxtaposed direction of the tubes (2) and communicates with the plurality of tubes (2), and the header tank (5) is a tube joining surface into which the plurality of tubes (2) are inserted and joined. In the heat exchanger formed in a box shape having (511), the header tank (5) has an outer wall portion (516) bent from the tube joint surface (511) toward the outside in the longitudinal direction of the tube (2). ) And a stress concentration portion (57) where stress acting on the core plate (51) is concentrated is provided at the connection portion between the tube joint surface (511) and the outer wall portion (516). It is characterized by .

  According to this, the tube (2) and the header tank (5) are provided by providing the stress concentration portion (57) at the connection portion between the tube joint surface (511) and the outer wall portion (516) in the header tank (5). When a thermal strain due to a difference in thermal expansion occurs between the stress concentration portion (57) and the bending start point, the header tank (5) can be flexed positively. For this reason, the amount of bending of the header tank (5) is increased, and the thermal strain generated between the tube (2) and the header tank (5) can be absorbed. Therefore, even when the dimension in the width direction of the header tank (5) is reduced, it is possible to reduce thermal distortion generated at the root portion between the header tank (5) and the tube (2).

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a typical front view showing the radiator concerning a 1st embodiment. It is a disassembled perspective view which shows the header tank vicinity of the radiator which concerns on 1st Embodiment. It is III-III sectional drawing of FIG. It is a schematic sectional drawing which shows the cross section which looked at the core plate in 2nd Embodiment from the tube lamination direction. It is a schematic sectional drawing which shows the cross section which looked at the core plate in 3rd Embodiment from the tube lamination direction. It is a schematic sectional drawing which shows the cross section which looked at the core plate in 4th Embodiment from the tube lamination direction. It is a schematic sectional drawing which shows the cross section which looked at the core plate in 5th Embodiment from the tube lamination direction. It is a schematic sectional drawing which shows the cross section which looked at the core plate in 6th Embodiment from the tube lamination direction. It is a schematic sectional drawing which shows the cross section which looked at the core plate in 7th Embodiment from the tube lamination direction. It is a schematic sectional drawing which shows the cross section which looked at the core plate in 8th Embodiment from the tube lamination direction.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, a case where the heat exchanger according to the present invention is applied to an automobile radiator that cools engine cooling water by exchanging heat between engine cooling water and air will be described as an example.

  As shown in FIG. 1, the radiator 1 of the present embodiment includes a core portion 4 composed of a plurality of tubes 2 and fins 3, and a pair of header tanks 5 that are assembled and arranged at both ends of the core portion 4. Yes.

  The tube 2 is a tube through which fluid (engine cooling water in this embodiment) flows. The tube 2 is formed in a flat shape so that the air flow direction coincides with the major axis direction. A plurality of tubes 2 are arranged in parallel in the vertical direction so that the longitudinal direction thereof coincides with the horizontal direction.

  The fins 3 are formed in a wave shape and are joined to flat surfaces on both sides of the tube 2. The fins 3 increase the heat transfer area with the air and promote heat exchange between the engine cooling water flowing through the tube 2 and the air.

  The header tank 5 extends in a direction orthogonal to the tube longitudinal direction at both ends of the tube 2 in the longitudinal direction (hereinafter referred to as tube longitudinal direction) and communicates with the plurality of tubes 2. In the present embodiment, the header tank 5 is disposed at the left and right ends of the tube 2, extends in the vertical direction, and communicates with the plurality of tubes 2. The header tank 5 includes a core plate 51 into which the tube 2 is inserted and joined, and a tank main body 52 that forms a tank space together with the core plate 51.

  Further, side plates 6 that reinforce the core portion 4 are provided at both ends of the core portion 4 in the stacking direction of the tubes 2 (hereinafter referred to as tube stacking direction). The side plate 6 extends in parallel with the tube longitudinal direction, and both end portions thereof are connected to the header tank 5.

  Next, the detailed structure of the header tank 5 is demonstrated based on FIG. 2 and FIG. In addition, in FIG. 2, illustration of the packing 53 mentioned later is abbreviate | omitted. Moreover, in FIG. 3, illustration of the tube 2 and the tank main-body part 52 mentioned later is abbreviate | omitted.

  As shown in FIGS. 2 and 3, the header tank 5 includes a core plate 51, a tank body 52 and a packing 53. The tube 2 and the side plate 6 are inserted and joined to the core plate 51. The tank body 52 and the core plate 51 constitute a tank internal space that is a space in the header tank 5. The packing 52 is a seal member that seals between the core plate 51 and the tank main body 52.

  In the present embodiment, the core plate 51 is made of an aluminum alloy. The tank body 52 is made of resin such as glass reinforced polyamide reinforced with glass fiber.

  Then, in a state where the packing 53 is sandwiched between the core plate 51 and the tank main body 52, the tank main body 52 is plastically deformed so as to press a caulking claw 517 (described later) of the core plate 51 against the tank main body 52. Is fixed to the core plate 51 by caulking. In the present embodiment, the packing 53 has a rectangular cross-sectional shape viewed from the tube stacking direction. In addition, the packing 53 of this embodiment is comprised by the rubber | gum which can be elastically deformed (this example ethylene-propylene-diene rubber (EPDM)).

  The core plate 51 has a tube joint surface 511 on which the tube 2 is inserted and joined, and a seal surface 512 on which the packing 53 is disposed. A surface pressure of the packing 53 is applied to the seal surface 512 when the tank body 52 is caulked and fixed.

  In the present embodiment, the tube joint surface 511 and the seal surface 512 are parallel to each other. Specifically, the tube joint surface 511 and the seal surface 512 are perpendicular to the tube longitudinal direction.

  The tube joining surface 511 and the seal surface 512 are different from each other in the distance in the tube longitudinal direction from the end surface in the tube longitudinal direction of the tube 2 (hereinafter referred to as the tube end surface 20). In this embodiment, the distance of the tube longitudinal walk from the tube joining surface 511 to the tube end surface 20 is shorter than the distance in the tube longitudinal direction from the seal surface 512 to the tube end surface 20. That is, the seal surface 512 is disposed on the inner side in the longitudinal direction of the tube 2 (side closer to the core portion 4) than the tube joint surface 511.

  The tube joint surface 511 and the seal surface 512 are connected via an inclined surface 513 inclined with respect to the tube longitudinal direction. In the present embodiment, the inclined surface 513 is inclined with respect to each of the tube joint surface 511 and the seal surface 512. Specifically, the angle formed by the seal surface 512 and the inclined surface 513 and the angle formed by the tube joint surface 511 and the inclined surface 513 are obtuse angles.

  A number of tube insertion holes 511a into which the tube 2 is inserted and brazed are formed in the tube joining surface 511 and the inclined surface 513 along the tube stacking direction. The tube 2 is inserted and joined to the tube joining surface 511 and the inclined surface 513.

  In addition, side plate insertion holes (not shown) into which the side plate 6 is inserted and brazed are formed in the tube joining surface 511 and the inclined surface 513 in the tube stacking direction in each of the tube joining surface 511 and the inclined surface 513. One is formed at each end. The side plate 6 is inserted and joined to the tube joining surface 511 and the inclined surface 513.

  A substantially cylindrical burring portion 514 that contacts the outer wall of the tube 2 is provided at the edge of the tube insertion hole 511a. The burring portion 514 is formed by subjecting the tube insertion hole 511a to burring and expanding the dimension of the tube insertion hole 511a so as to be substantially the same as the outer dimension of the tube 2. Similarly, a substantially cylindrical burring portion (not shown) that contacts the outer wall of the side plate 6 is also provided at the edge of the side plate insertion hole.

  A rib 515 is provided between adjacent tubes 2 on the inclined surface 513 of the core plate 51. The rib 515 is formed so as to protrude from the inclined surface 513 toward the outer side of the header tank 5 (inner side in the longitudinal direction of the tube 2). In the present embodiment, the rib 515 is formed from the inner side end of the header tank 5 to the outer side end of the inclined surface 513. As described above, by providing the rib 515 on the core plate 51, the thermal distortion generated between the tube 2 and the core plate 51 can be reduced.

  The core plate 51 has an outer wall portion 516 that is bent at a substantially right angle from the seal surface 512 toward the opposite side of the core portion 4 and extends in the tube stacking direction or the air flow direction.

  A bulging portion 521 that bulges toward the outer side of the header tank 5 is formed in a portion of the tank main body 52 that faces the tube 2. Thereby, it is comprised so that the inner surface of the tank main-body part 52 and the outer surface of the tube 2 may not contact.

  At the end of the tank body 52 on the core plate 51 side, a flange portion 522 having a larger thickness than other portions is provided. The flange portion 522 is disposed on the seal surface 512 of the core plate 51 via the packing 53.

  By the way, the core plate 51 is provided with a plurality of caulking claw portions 517 formed so as to protrude from the outer wall portion 516 to the tank body portion 52 side. The caulking claw portion 517 is disposed at a portion corresponding to the flange portion 522 of the tank main body portion 52. The tank body 52 is assembled to the core plate 51 by fixing the crimping claw 517 to the flange 522 of the tank body 52.

  Inside the tube 2, an inner column portion 21 that is formed so as to connect the two flat surfaces and increases the pressure resistance of the tube 2 is provided. In the present embodiment, the inner column portion 21 is disposed in the center portion in the air flow direction inside the tube 2. The inner pillar 21 divides the fluid passage inside the tube 2 into two.

  Here, as shown in FIGS. 2 and 3, the core plate 51 is disposed between the inclined surface 513 and the outer wall portion 516 and connected to both the inclined surface 513 and the outer wall portion 516. The part is referred to as the bottom 54. In the present embodiment, the inclined surface 513, the outer wall portion 516, and the bottom portion 54 form a groove portion 510 for arranging the packing 53.

  A packing 53 is disposed on the bottom 54 of the core plate 51. For this reason, a part of the inner side surface of the header tank 5 in the bottom portion 54 constitutes a seal surface 512. Therefore, the bottom portion 54 of the present embodiment corresponds to “a portion of the core plate 51 where the seal surface 512 is provided” described in the claims.

  On the tube joint surface 511 side (that is, the inner side of the header tank 5) with respect to the seal surface 512 in the core plate 51, a thin portion 55 having a smaller plate thickness than the bottom portion 54 is provided. The thin portion 55 is configured by forming a recess 56 in the core plate 51. In the thin portion 55, stress acting on the core plate 51 is concentrated. Therefore, the thin portion 55 of this embodiment corresponds to the “stress concentration portion” described in the claims.

  The thin wall portion 55 is provided on the surface of the core plate 51 facing the tank body portion 52, that is, the inner surface of the header tank 5. Specifically, a recess 56 is formed on the surface of the core plate 51 that faces the tank body 52. The thin portion 55 extends in the longitudinal direction of the core plate 51 (in the present embodiment, the tube stacking direction).

  In the present embodiment, the thin portion 55 is provided at a connection portion between the bottom portion 54 and the inclined surface 513 in the core plate 51. That is, the thin portion 55 is arranged on the outer side of the tank with respect to the rib 515 in the core plate 51. The thin portion 55 is formed by pressing so that the connecting portion between the bottom portion 54 and the inclined surface 513 is crushed from the inner side of the header tank 5 when the core plate 51 is formed.

  As described above, in the present embodiment, the thin portion 55 is provided on the tube joint surface 511 side with respect to the seal surface 512 in the core plate 51. According to this, when a thermal strain due to a difference in thermal expansion occurs between the tube 2 and the core plate 51, stress concentrates on the thin wall portion 55 to become a bending start point, and the core plate 51 (specifically, the bottom portion). 54 and outer wall 516) can be positively deflected. For this reason, the amount of bending of the core plate 51 is increased, and the thermal strain generated between the tube 2 and the core plate 51 can be absorbed. Therefore, even when the width direction dimension (air flow direction dimension) of the header tank 5 is reduced, it is possible to reduce the thermal distortion generated at the root portion between the header tank 5 and the tube 2.

  Further, in the present embodiment, the thin portion 55 is disposed on the outer side of the header tank 5 with respect to the rib 515 in the core plate 51. According to this, since both the rib 515 and the thin portion 55 can be provided on the core plate 51, the thermal strain alleviating effect by providing the rib 515, and the thermal strain absorbing effect by providing the thin portion 55, Both can be obtained.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. In the present embodiment, the arrangement position of the recess 56 is different from that in the first embodiment.

  As shown in FIG. 4, the recess 56 of the present embodiment is formed on the surface of the core plate 51 that does not face the tank body 52, that is, the outer surface of the header tank 5. For this reason, the thin portion 55 is provided on the surface of the core plate 51 that does not face the tank main body 52. Other configurations are the same as those of the first embodiment. Therefore, according to the exhaust heat exchanger of the present embodiment, the same effect as that of the first embodiment can be obtained.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. In the present embodiment, the arrangement position of the recess 56 is different from that in the first embodiment.

  As shown in FIG. 5, the recesses 56 of the present embodiment are provided on both the surface of the core plate 51 that faces the tank body 52 and the surface that does not face the tank body 52. For this reason, the plate | board thickness of the thin part 55 of this embodiment becomes thinner than the plate | board thickness of the thin part 55 of the said 1st Embodiment.

  For this reason, in this embodiment, when the thermal distortion by a thermal expansion difference arises between the tube 2 and the core plate 51, the core plate 51 can be bent more positively. For this reason, the amount of bending of the core plate 51 becomes larger, and the thermal strain generated between the tube 2 and the core plate 51 can be more reliably absorbed.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIG. In this embodiment, compared with the said 1st Embodiment, the shape of the packing 53 and the arrangement position of the recessed part 56 differ.

  As shown in FIG. 6, the packing 53 of this embodiment has a circular cross-sectional shape as viewed from the tube stacking direction. For this reason, the packing 53 is in point contact with the core plate 51. Therefore, the seal surface 512 of the present embodiment has a smaller area than the seal surface 512 of the first embodiment. The recess 56 is provided on the surface of the bottom 54 that does not face the tank body 52.

  Other configurations are the same as those of the first embodiment. Therefore, according to the exhaust heat exchanger of the present embodiment, the same effect as that of the first embodiment can be obtained.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to FIG. The present embodiment is different from the first embodiment in that a spring structure portion 57 is employed as a stress concentration portion.

  As shown in FIG. 7, an elastically deformable spring structure 57 is provided on the tube joint surface 511 side of the seal surface 512 in the core plate 51. In the present embodiment, the spring structure portion 57 is formed by curving a connection portion between the bottom portion 54 and the inclined surface 513 in the core plate 51 in an arc shape. In the spring structure portion 57, stress acting on the core plate 51 is concentrated. Therefore, the spring structure portion 57 of the present embodiment corresponds to the “stress concentration portion” described in the claims.

  In the present embodiment, the spring structure portion 57 is provided on the tube joint surface 511 side with respect to the seal surface 512 in the core plate 51. According to this, when a thermal strain due to a difference in thermal expansion occurs between the tube 2 and the core plate 51, stress concentrates on the spring structure portion 57 to become a bending start point, and the core plate 51 (specifically, The bottom 54 and the outer wall 516) can be flexed positively. For this reason, it becomes possible to acquire the effect similar to the said 1st Embodiment.

(Sixth embodiment)
Next, a sixth embodiment of the present invention will be described with reference to FIG. The present embodiment is different from the first embodiment in that an inner wall portion 518 is provided instead of the inclined surface 513 of the core plate 51.

  As shown in FIG. 8, the core plate 51 of the present embodiment has an inner wall portion 518 that is bent at a substantially right angle from the tube joint surface 511 toward the core portion 4 and extends in the tube stacking direction or the air flow direction. ing. The tube joint surface 511 and the seal surface 512 (bottom portion 54) of the core plate 51 are connected by an inner wall portion 518. The inner wall portion 518 is configured to be orthogonal to the air flow direction or the tube stacking direction. Further, the thin portion 55 of the present embodiment is provided at a connection portion between the bottom portion 54 and the inner wall portion 518 in the core plate 51.

  Other configurations are the same as those of the first embodiment. Therefore, according to the exhaust heat exchanger of the present embodiment, the same effect as that of the first embodiment can be obtained. Furthermore, in this embodiment, since the inner wall portion 518 is configured to be orthogonal to the air flow direction, the dimension of the header tank 5 in the air flow direction, that is, the width direction dimension can be further reduced.

(Seventh embodiment)
Next, a seventh embodiment of the present invention will be described with reference to FIG. In this embodiment, compared with the said 1st Embodiment, the point which eliminated the groove part 510 for arrange | positioning the packing 53 in the core plate 51 differs.

  As shown in FIG. 9, in the core plate 51 of the present embodiment, the tube joint surface 511 and the seal surface 512 are arranged on the same plane. The thin portion 55 is disposed between the tube joint surface 511 and the seal surface 512.

  Other configurations are the same as those of the first embodiment. Therefore, according to the exhaust heat exchanger of the present embodiment, the same effect as that of the first embodiment can be obtained. Furthermore, in this embodiment, since the groove part 510 for arrange | positioning the packing 53 was abolished, the air flow direction dimension of the header tank 5, ie, the width direction dimension, can be made smaller.

(Eighth embodiment)
Next, an eighth embodiment of the present invention will be described with reference to FIG. In this embodiment, compared with the said 1st Embodiment, the structure of the header tank 5 differs.

  As shown in FIG. 10, the header tank 5 is formed in a box shape having a tube joint surface 511 into which a plurality of tubes 2 are inserted and joined. In the present embodiment, the header tank 5 is made of a metal such as an aluminum alloy.

  Specifically, the header tank 5 is formed in a substantially rectangular parallelepiped shape having a tube joint surface 511, an outer wall portion 516, and an upper wall portion 519. The outer wall portion 516 is a peripheral wall member that is bent at a substantially right angle from the tube joint surface 511 toward the tube longitudinal direction outer side (the side opposite to the core portion 4) and extends in the tube stacking direction or the air flow direction. Further, the upper side wall portion 519 extends in parallel with the tube joint surface 511 and is connected to the outer side wall portion 516.

  A spring structure 57 that is elastically deformable is provided at a connection portion between the tube joining surface 511 and the outer wall portion 516. In the present embodiment, the spring structure portion 57 is formed by curving a connection portion between the tube joint surface 511 and the outer wall portion 516 in the core plate 51 in an arc shape. In the spring structure portion 57, stress acting on the core plate 51 is concentrated. Therefore, the spring structure portion 57 of the present embodiment corresponds to the “stress concentration portion” described in the claims.

  As described above, in this embodiment, the spring structure portion 57 is provided at the connection portion between the tube joint surface 511 and the outer wall portion 516 in the header tank 5. According to this, when a thermal distortion due to a difference in thermal expansion occurs between the tube 2 and the header tank 5, stress concentrates on the spring structure portion 57 to be a bending start point, and the header tank 5 is positively bent. be able to. For this reason, it becomes possible to acquire the effect similar to the said 1st Embodiment.

  By the way, in the said 1st Embodiment, since the header tank 5 is comprised by combining the metal core plate 51 and the resin tank main-body part 52, it is packing between the core plate 51 and the tank main-body part 52. 53 must be sealed. On the other hand, in this embodiment, since the header tank 5 is integrally formed in a box shape from metal, it is not necessary to provide the packing 53, and the number of parts can be reduced.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention. Further, the means disclosed in each of the above embodiments may be appropriately combined within a practicable range.

  (1) In the above embodiment, the example in which the rib 515 is provided between the adjacent tubes 2 on the inclined surface 513 of the core plate 51 has been described, but the present invention is not limited thereto, and the rib 515 may not be provided. Similarly, in the above-described embodiment, the example in which the burring portion 514 is provided at the edge of the tube insertion hole 511a has been described. However, the present invention is not limited thereto, and the burring portion 514 may not be provided.

  (2) In the seventh embodiment, the example in which the spring structure portion 57 is employed as the stress concentration portion has been described, but the stress concentration portion is not limited to this. For example, as the stress concentration portion, a thin portion having a thinner plate thickness than other portions of the header tank 5 may be employed.

  (3) In the above embodiment, the example in which the heat exchanger of the present invention is applied to the radiator 1 has been described. However, the present invention is also applied to other heat exchangers such as an evaporator and a refrigerant radiator (refrigerant condenser). Is possible.

2 Tube 5 Header tank 51 Core plate 52 Tank body 53 Packing (seal member)
55 Thin-walled part (stress concentration part)
57 Spring structure (stress concentration part)
511 Tube joint surface 512 Seal surface

Claims (6)

A plurality of tubes (2) arranged in parallel with each other and in which a fluid flows;
A header tank (5) disposed at a longitudinal end of the tube (2) and extending in a parallel arrangement direction of the plurality of tubes (2) and communicating with the plurality of tubes (2);
The header tank (5) includes a core plate (51) to which the plurality of tubes (2) are joined, and a tank body (52) fixed to the core plate (51). A vessel,
The core plate (51) has a tube joint surface (511) to which the tube (2) is inserted and joined, and a seal surface (512) on which an elastically deformable seal member (53) is disposed. ,
Stress concentration portions (55, 57) where stress acting on the core plate (51) is concentrated are provided closer to the tube joint surface (511) than the seal surface (512) of the core plate (51). A heat exchanger characterized by that.   The heat exchanger according to claim 1, wherein the stress concentration portion (55, 57) is provided on a surface of the core plate (51) facing the tank main body portion (52). .   The heat exchanger according to claim 1 or 2, wherein the stress concentration portion (55, 57) extends in a longitudinal direction of the core plate (51). The core plate (51) has a thin portion (55) having a thin plate thickness as compared with a portion (54) provided with the seal surface (512) in the core plate (51),
The heat exchanger according to any one of claims 1 to 3, wherein the stress concentration portion is the thin portion (55). The core plate (51) is provided with an elastically deformable spring structure (57),
The heat exchanger according to any one of claims 1 to 3, wherein the stress concentration portion is the spring structure portion (57). A plurality of tubes (2) arranged in parallel with each other and in which a fluid flows;
A header tank (5) disposed at a longitudinal end of the tube (2) and extending in a parallel arrangement direction of the plurality of tubes (2) and communicating with the plurality of tubes (2);
The header tank (5) is a heat exchanger formed in a box shape having a tube joint surface (511) into which the plurality of tubes (2) are inserted and joined,
The header tank (5) has an outer wall portion (516) bent from the tube joint surface (511) toward the outside in the longitudinal direction of the tube (2),
The connection portion between the tube joining surface (511) and the outer wall portion (516) is provided with a stress concentration portion (57) where stress acting on the header tank (5) is concentrated. Heat exchanger.

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