JP4661526B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger, and is effective when applied to a so-called multi-flow type radiator that cools cooling water of an internal combustion engine such as a vehicle engine.

  Conventionally, as shown in FIGS. 4 (a) and 4 (b), a multiflow-type radiator includes a plurality of tubes J2 and a core portion J4 having fins J3 joined to the outer surface of these tubes J2, and a plurality of tubes J2. A header tank J5 that communicates with the tube J2 and an insert J7 that is disposed at the end of the core portion J4 and reinforces the core portion J4 (see, for example, Patent Document 1).

  The header tank J5 is composed of a core plate J5a to which a tube J2 is joined and a tank body (not shown) that constitutes a tank internal space. The core plate J5a includes a tube joint surface J51 to which the tube J2 is joined, and a groove portion J52 that is formed over the entire circumference of the tube joint surface J51 and into which an end of a tank body (not shown) is inserted. Have.

The groove portion J52 has a first joint portion J54 disposed substantially parallel to the tube joint surface J51 on the core portion J4 side from the tube joint surface J51. In addition, the insert J7 has a second joint portion J71 facing the first joint portion J54 of the core plate J5a, and the second joint portion J71 is joined to the first joint portion J54 over the entire surface. Has been.
Japanese Patent Laid-Open No. 11-241895

  In such a radiator, when the temperature difference between the adjacent tubes J2 and between the tube J2 and the insert J7 increases, thermal stress accompanying thermal strain is generated in the tube J2 and the insert J7.

  At this time, since the second joint J71 of the insert J7 is entirely joined to the first joint J54 of the core plate J5a, the insert J7 is difficult to deform in the longitudinal direction (thermal strain generation direction), The heat distortion absorption margin decreases. For this reason, when thermal stress repeatedly occurs, there is a problem that the vicinity of the root portion (joint portion) of the insert J7 with the core plate J5a is fatigued.

  Furthermore, since the restraining force of the tube J2 by the insert J7 increases, the tube J2 becomes difficult to deform in the longitudinal direction, and the heat distortion absorption margin decreases. For this reason, when thermal stress repeatedly occurs, there is a problem that the vicinity of the root portion of the tube J2 with the core plate J5a is fatigued.

  An object of this invention is to provide the heat exchanger which can reduce the thermal distortion of a tube and insert in view of the said point.

In order to achieve the above object, the present invention provides a core portion (4) having a plurality of tubes (2) through which a heat medium flows, and orthogonal to the longitudinal direction of the tubes (2) at both longitudinal ends of the tubes (2). The header tank (5) that extends in the direction to communicate with the tube (2) and the end of the core portion (4) are arranged substantially parallel to the longitudinal direction of the tube (2), and heat is generated from the core portion (4). The heat exchanger is provided with an insert (7) supported by the header tank (5) at both ends, and the header tank (5) is joined to the longitudinal end of the tube (2). A core plate (5a) having a tube joint surface (51) and a groove portion (52) formed so as to open outward in the longitudinal direction of the tube (2) over the entire circumference of the tube joint surface (51); (52) the end is inserted into the core plate 5a) and a tank body (5b) that constitutes a space in the tank, and the inner side in the longitudinal direction of the tube (2) of the groove (52) is a first joint (54) joined to the insert (7). The insert (7) has a second joint portion (71) facing the first joint portion (54), and the second joint portion (71) The first feature is that the joint (54) and the core (4) are locally joined in the air flow direction .

  Thereby, since the degree of freedom of expansion and contraction of the insert (7) can be improved, the insert (7) is easily deformed in the longitudinal direction (thermal strain generation direction), and the deformation causes the heat of the insert (7). Distortion can be absorbed. At the same time, since the restraining force of the tube (2) by the insert (7) is reduced, the degree of freedom of expansion and contraction of the tube (2) can be improved. For this reason, it becomes easy to deform | transform a tube (2) to a longitudinal direction (thermal strain generation direction), and the thermal strain of a tube (2) can be absorbed by the deformation | transformation. Therefore, it becomes possible to reduce the thermal distortion of the tube (2) and the insert (7).

Note that “locally bonded” means, for example, that the second bonding portion (71) and the first bonding portion 54 are approximately 20% to 30% in the air flow direction of the core portion (4) of the heat exchanger. It means joining. If the amount of joining is large, the degree of freedom of expansion and contraction of the insert (7) cannot be improved, and if the amount of joining is small, the rigidity of the core part (4) will be reduced. Bonding is preferred in practice.

  Further, the second joint portion (71) has a top portion (71a) protruding toward the first joint portion (54), and the second joint portion (71) is the first portion at the top portion (71a). You may comprise so that it may join with one junction part (54).

  The second feature of the present invention is that the second joint portion (71) is joined to the first joint portion (54) only at the central portion in the air flow direction.

  Thereby, compared with the case where the 2nd joined part (71) is joined to the 1st joined part (54) locally in parts other than the central part in an air flow direction, insert (7) is made into air. Since it can make it easy to deform | transform equally in a flow direction, the thermal distortion of insert (7) can be absorbed more. Therefore, it becomes possible to further reduce the thermal distortion of the tube (2) and the insert (7).

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

  Hereinafter, an embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the heat exchanger according to the present invention is applied to a radiator 1 that exchanges heat between cooling water (heat medium) that cools a vehicle engine and air (air).

  FIG. 1 is a front view of a radiator 1 according to the present embodiment, FIG. 2 is a view showing a main part of the present embodiment, (a) is an enlarged plan view, and (b) is an enlarged front view. 2A and 2B, the tank body 5b is not shown.

  In FIG. 1, a tube 2 is a tube through which cooling water flows. The tube 2 is formed in a flat shape so that the air flow direction (perpendicular to the paper surface) coincides with the major axis direction, and the longitudinal direction thereof is A plurality of them are arranged in parallel in the vertical direction so as to coincide with the horizontal direction.

  Fins 3 formed in a wave shape are joined to flat surfaces 2a on both sides of the tube 2 (see FIG. 2B), and the heat transfer area with the air is increased by the fins 3 so that the engine cooling water and the air Promotes heat exchange. Hereinafter, the substantially rectangular heat exchanging portion including the tube 2 and the fin 3 is referred to as a core portion 4.

  The header tank 5 extends in a direction (vertical direction in the present embodiment) orthogonal to the longitudinal direction of the tube 2 at the longitudinal end portions (in the present embodiment, left and right ends) of the tube 2 and communicates with the plurality of tubes 2. Therefore, the header tank 5 includes a core plate 5a into which the tube 2 is inserted and joined, and a tank body 5b that forms a space in the tank together with the core plate 5a.

  The core plate 5a has a tube joint surface 51 to which the tube 2 is joined. In addition, a groove portion 52 having a substantially rectangular cross section into which the end portion of the tank body 5b is inserted is formed around the entire circumference of the tube joint surface 51.

  The groove part 52 is formed by three surfaces. That is, the inner wall portion 53 that is bent substantially vertically from the outer peripheral portion of the tube bonding surface 51 and extends in the longitudinal direction of the tube 2, and the first bonding portion that is bent substantially vertically from the inner wall portion 53 and extends in the tube 2 stacking direction. A groove portion 52 is formed by 54 and the outer wall portion 55 that is bent substantially perpendicularly from the first joint portion 54 and extends in the longitudinal direction of the tube 2.

  In the present embodiment, the core plate 5a is made of metal (for example, aluminum alloy), the tank body 5b is made of resin, and the groove portion 52 of the core plate 5a is made of packing (not shown) made of an elastic material such as rubber. ), And the gap between the tank body 5b and the core plate 5a is liquid-tightly sealed with this packing.

  Further, the radiator tank 5 is provided with a pipe connecting portion 6 to which a cooling water pipe (not shown) connecting the cooling water passage (not shown) provided in the internal combustion engine and the radiator 1 is connected.

  At both ends of the core portion 4, inserts 7 that extend substantially in parallel with the longitudinal direction of the tube 2 and reinforce the core portion 4 are provided. The insert 7 includes a base portion 7a having a surface substantially parallel to the flat surface 2a of the tube 2 and extending substantially parallel to the longitudinal direction of the tube 2, and a direction substantially orthogonal to the base portion 7a (in this embodiment). And ribs 7b extending in the horizontal direction and extending substantially parallel to the longitudinal direction of the tube 2. In the insert 7, the ribs 7 b are respectively provided on both ends of the base portion 7 a in the direction orthogonal to the longitudinal direction of the base portion 7 a, so that the cross-sectional shape of the insert 7 is substantially the same as the side opposite to the core portion 4. It has a U-shaped cross section. Further, the insert 7 is in contact with the core portion 4 so that heat is transmitted from the core portion 4.

  The end of the insert 7 in the longitudinal direction is bent so as to face the groove 52 of the core plate 5a. That is, the insert 7 is bent at a substantially right angle from the longitudinal end portion of the base portion 7a and extends in the tube 2 stacking direction, and the insert 7 is bent at a substantially right angle from the second bonding portion 71. And a distal end 72 extending in the longitudinal direction.

  Here, the support structure of the core plate 5a and the insert 7 will be described.

  3A is a cross-sectional view taken along the line AA in FIG. 2A, and FIG. 3B is a cross-sectional view taken along the line BB in FIG. As shown in FIGS. 3A and 3B, the end of the core plate 5 a in the stacking direction of the tube 2 (hereinafter referred to as the core plate end 56) has the tube 2 so as to substantially cover the end 72 of the insert 7. The end portion 72 is fixed by bending outward in the stacking direction. Further, both end portions of the end portion 72 in the air flow direction are not covered with the core plate end portion 56 and are exposed to the outside.

  Further, as shown in FIG. 2A, the second joint 71 of the insert 7 has a “<” shape with a central portion in the air flow direction protruding toward the first joint 54 of the core plate 5a. Is formed. In other words, the second joint portion 71 of the insert 7 is in contact with the first joint portion 54 of the core plate 5a only at the central portion in the air flow direction, and the first portion of the core plate 5a is in other portions. A gap 8 is formed between the joint portion 54 and the gap 8 increases as it goes outward from the center of the second joint portion 71 in the air flow direction. In addition, the site | part (In this embodiment, air flow direction center part) protruded in the 1st junction part 54 side in the 2nd junction part 71 is called the top part 71a.

  Moreover, in this embodiment, the tube 2, the core plate 5a, and the insert 7 are integrally joined by brazing. For this reason, the insert 7 is joined to the core plate 5a at two locations (the first joint portion 54 and the outer wall portion 55) at the central portion in the air flow direction, and at one location (outside) at the other portions. They are joined only by the wall 55).

  As described above, the degree of freedom of expansion and contraction of the insert 7 can be improved by joining the second joint portion 71 of the insert 7 to the first joint portion 54 of the core plate 5a only by the top portion 71a. Therefore, the insert 7 is easily deformed in the longitudinal direction (thermal strain generation direction), and the deformation of the insert 7 can be absorbed by the deformation. At the same time, since the restraining force of the tube 2 by the insert 7 is reduced, the degree of freedom of expansion and contraction of the tube 2 can be improved. For this reason, the tube 2 is easily deformed in the longitudinal direction (thermal strain generation direction), and the deformation of the tube 2 can be absorbed by the deformation. Therefore, it becomes possible to reduce the thermal distortion of the tube 2 and the insert 7.

  Furthermore, by providing the top portion 71a at the center of the second joint portion 71 of the insert 7 in the air flow direction, the top portion 71a can be inserted into the other portion of the second joint portion 71 of the insert 7 as compared with the case where the top portion 71a is provided. 7 can be easily deformed equally in the air flow direction, so that the thermal strain of the insert 7 can be absorbed more. Therefore, the thermal distortion of the tube 2 and the insert 7 can be further reduced.

(Other embodiments)
In the above embodiment, the embodiment in which the present invention is applied to the cross-flow type radiator 1 in which the cooling water flows in the horizontal direction has been described. However, the present invention is applied to a down-flow type radiator in which the cooling water flows in the vertical direction. You can also

  Moreover, in the said embodiment, although the 2nd junction part 71 of the insert 7 and the 1st junction part 54 of the core plate 5a were joined only in the center part in an air flow direction, it is not restricted to this part, If the 2nd junction part 71 of the insert 7 and the 1st junction part 54 of the core plate 5a are joining locally, it can be joined in arbitrary parts.

  Moreover, in the said embodiment, although one part of the 2nd junction part 71 of the insert 7 was protruded to the 1st junction part 54 side of the core plate 5a, it is not restricted to this, For example, the 1st junction part 54 is used. A part of the protrusion may protrude toward the second joint 71.

It is a front view of radiator 1 concerning an embodiment of the present invention. It is a figure which shows the principal part of the radiator 1 which concerns on embodiment of this invention, (a) is a top view, (b) is a front view. (A) is AA sectional drawing of Fig.2 (a), (b) is BB sectional drawing of Fig.2 (a). It is a figure which shows the principal part of the conventional radiator, (a) is a top view, (b) is a front view.

Explanation of symbols

  2 ... Tube, 4 ... Core part, 5 ... Header tank, 5a ... Core plate, 5b ... Tank body, 7 ... Insert, 51 ... Tube joint surface, 52 ... Groove part, 54 ... First joint part, 71 ... Second , 71a... Top.

Claims (3)

A core portion (4) having a plurality of tubes (2) through which a heat medium flows;
A header tank (5) extending in a direction perpendicular to the longitudinal direction of the tube (2) at both longitudinal ends of the tube (2) and communicating with the tube (2);
At the end of the core portion (4), the tube (2) is arranged substantially in parallel with the longitudinal direction of the tube (2), heat is transferred from the core portion (4), and both ends are supported by the header tank (5). A heat exchanger comprising an insert (7),
The header tank (5) has a tube joining surface (51) to which the longitudinal ends of the tube (2) are joined and the longitudinal direction of the tube (2) over the entire circumference of the tube joining surface (51). A tank body having a core plate (5a) having a groove (52) formed to open to the outside, and an end inserted into the groove (52), and constituting a tank internal space together with the core plate (5a) (5b) and
The inner side in the longitudinal direction of the tube (2) of the groove (52) is a first joint (54) joined to the insert (7),
The insert (7) has a second joint (71) facing the first joint (54),
The said 2nd junction part (71) is joining locally in the air flow direction of a said 1st junction part (54) and the said core part (4), The heat exchanger characterized by the above-mentioned. The second joint portion (71) has a top portion (71a) protruding toward the first joint portion (54),
The heat exchanger according to claim 1, wherein the second joint (71) is joined to the first joint (54) at the top (71a). It said second joint (71) A heat exchanger according to claim 1 or 2, characterized in that it is joined only at the central portion of the first joint portion (54) in the direction of air flow .

Images