WO2021145210A1 - Heat exchanger - Google Patents

Abstract

A heat exchanger (10), provided with a heat exchange unit (20), a first inflow pipe (24a), a first outflow pipe (24b), a second inflow pipe (25a), and a second outflow pipe (25b). The second inflow pipe, the second outflow pipe, and a first pipe, which is one of the first inflow pipe and the first outflow pipe, are provided at one end section of the heat exchange unit. The other first pipe, which is the other of the first inflow pipe and the first outflow pipe, is provided at the other end section of the heat exchange unit. Two pipes, from among one of the first pipes, the second inflow pipe, and the second outflow pipe, are provided on one of the outer surfaces of one end section of the heat exchange unit. The one remaining pipe, from among one of the first pipes, the second inflow pipe, and the second outflow pipe, is provided on the other outer surface of the one end section of the heat exchange unit.

Description

Heat exchanger Cross-reference of related applications

This application is based on Japanese Patent Application No. 2020-005719 filed on January 17, 2020 and Japanese Patent Application No. 2020-166970 filed on October 1, 2020. , Claiming the benefit of that priority, the entire contents of that patent application are incorporated herein by reference.

This disclosure relates to heat exchangers.

Conventionally, there is a heat exchanger described in Patent Document 1 below. The heat exchanger described in Patent Document 1 cools the supercharged intake air by exchanging heat between the supercharged intake air supplied to the internal combustion engine by the supercharger and the cooling water. This heat exchanger has a heat exchange unit composed of a plurality of flow path plates arranged in a laminated manner. Each flow path plate exchanges heat between the cooling water flowing inside the flow path plate and the supercharged intake air flowing outside the flow path plate. As the cooling water, a first cooling water and a second cooling water having a temperature higher than that of the first cooling water are used. Inside the flow path plate, a first cooling water flow path through which the first cooling water flows and a second cooling water flow path through which the second cooling water flows are formed. The flow path plate has a first U-turn portion that makes a U-turn of the flow of the first cooling water flowing through the first cooling water flow path and a second U-turn portion that makes a U-turn of the flow of the second cooling water flowing through the second cooling water flow path. Has a part. The heat exchange section includes a first distribution tank section that distributes cooling water to the first U-turn section of each flow path plate, and a first collecting tank section that collects cooling water that has flowed through the first U-turn section of each flow path plate. It has a second distribution tank portion that distributes cooling water to the second U-turn portion of each flow path plate, and a second collecting tank portion that collects the cooling water that has flowed through the second U-turn portion of each flow path plate. There is.

Japanese Patent No. 6281467

In the heat exchanger through which two types of cooling water flow as described in Patent Document 1, the first inflow pipe and the second inflow pipe for inflowing the cooling water into each distribution tank portion, and each collecting tank portion It is necessary to provide a total of four pipes, a first discharge pipe and a second discharge pipe for discharging the first cooling water. In this regard, when the two distribution tank portions and the two collecting tank portions are formed side by side at one end of the heat exchanger as in the heat exchanger described in Patent Document 1, for example, one end of the heat exchanger. It is necessary to provide four pipes on the upper surface.

On the other hand, since a hose is connected to each pipe, it is necessary to provide a free space around each pipe. Generally, a free space about twice the diameter of the pipe is required around the pipe. In this respect, when four pipes are provided side by side on the upper surface of the heat exchanger, it becomes difficult to provide a space between the pipes. In particular, in recent years, since the heat exchanger itself has been required to be miniaturized, it has become more difficult to provide a space between each pipe.

The purpose of the present disclosure is to provide a heat exchanger capable of securing a space between each pipe.

The heat exchanger according to one aspect of the present disclosure is a heat exchanger that exchanges heat between the intake air introduced into the internal combustion engine or the fuel cell and the cooling water of the two systems of the first cooling water and the second cooling water, and is heat. It includes an exchange unit, a first inflow pipe, a first outflow pipe, a second inflow pipe, and a second outflow pipe. The heat exchange section has a core section in which a plurality of flow path forming plate members having a first flow path through which the first cooling water flows and a second flow path through which the second cooling water flows are stacked and arranged. , Heat exchange is performed between the first cooling water and the second cooling water flowing inside the flow path forming plate member and the intake air flowing outside the flow path forming plate member. The first inflow pipe causes the first cooling water to flow into the heat exchange section. The first outflow pipe causes the first cooling water to flow out from the heat exchange section. The second inflow pipe causes the second cooling water to flow into the heat exchange section. The second outflow pipe causes the second cooling water to flow out from the heat exchange section. The direction in which a plurality of flow path forming plate members are stacked and arranged is defined as the plate stacking direction, the heat exchange portion is defined as the intake flow direction in which the intake air flows, and the direction orthogonal to both the plate stacking direction and the intake flow direction is determined. When the direction is set, one of the first inflow pipe and the first outflow pipe, the second inflow pipe, and the second outflow pipe are provided at one end of the heat exchange portion in the predetermined direction. .. At the other end of the heat exchange portion in the predetermined direction, the first pipe of the other of the first inflow pipe and the first outflow pipe is provided. Two of the first pipe, the second inflow pipe, and the second outflow pipe are provided on one outer surface in the plate stacking direction at one end of the heat exchange portion. On the other outer surface in the plate stacking direction at one end of the heat exchange portion, one of the first pipe, the second inflow pipe, and the remaining one of the second outflow pipes is provided.

According to this configuration, as compared with the case where all of the one first pipe, the second inflow pipe, and the second outflow pipe are provided on one outer surface in the plate stacking direction at one end of the heat exchange portion, each It becomes easier to form a space between the pipes. Further, since only the other first pipe is provided at the other end of the heat exchange portion in the predetermined direction, it is easy to form a space around this pipe. Therefore, it is possible to secure a space between each pipe when the heat exchanger is miniaturized.

FIG. 1 is a perspective view showing a perspective structure of the heat exchanger of the first embodiment. FIG. 2 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the first embodiment. FIG. 3 is a plan view showing the planar structure of the first plate piece of the flow path forming plate member of the first embodiment. FIG. 4 is a perspective view showing a perspective structure of a second plate piece of the flow path forming plate member of the first embodiment. FIG. 5 is a cross-sectional view showing a cross-sectional structure around a first outflow pipe of the heat exchanger of the first embodiment. FIG. 6 is a front view showing the front structure of the heat exchanger of the first embodiment. FIG. 7 is a rear view showing the rear surface structure of the heat exchanger of the first embodiment. FIG. 8 is a side view showing the right side structure of the heat exchange portion of the first embodiment. FIG. 9 is a diagram schematically showing the structure of the heat exchange portion of the first embodiment. FIG. 10 is a perspective view showing a perspective structure of the heat exchanger of the second embodiment. FIG. 11 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the second embodiment. FIG. 12 is a diagram schematically showing the structure of the heat exchange portion of the second embodiment. FIG. 13 is a cross-sectional view showing a cross-sectional structure around a second outflow pipe of the heat exchanger of the third embodiment. FIG. 14 is a perspective view showing a perspective structure of the spacer of the third embodiment. FIG. 15 is a perspective view showing a perspective structure of the spacer of the third embodiment. FIG. 16 is a plan view showing the planar structure of the first plate piece of the flow path forming plate member of the fourth embodiment. FIG. 17 is a perspective view showing a perspective structure of a second plate piece of the flow path forming plate member of the fourth embodiment. FIG. 18 is a perspective view showing a perspective structure of the spacer of the fourth embodiment. FIG. 19 is a rear view showing the rear surface structure of the heat exchanger of the fourth embodiment. FIG. 20 is a perspective view showing a perspective structure of the heat exchanger of the fifth embodiment. FIG. 21 is a perspective view showing a cross-sectional perspective structure of the flow path forming plate member of the sixth embodiment. FIG. 22 is a cross-sectional view showing a cross-sectional structure of the flow path forming plate member of the sixth embodiment. FIG. 23 is a cross-sectional view showing a cross-sectional structure along the line XXI-XXI of FIG. FIG. 24 is a plan view showing the planar structure of the first plate piece of the flow path forming plate member of the seventh embodiment. FIG. 25 is a block diagram showing a schematic configuration of the cooling circuit of the eighth embodiment. FIG. 26 is a perspective view showing a perspective structure of the heat exchanger of another embodiment.

Hereinafter, an embodiment of the heat exchanger will be described with reference to the drawings. In order to facilitate understanding of the description, the same components are designated by the same reference numerals as much as possible in each drawing, and duplicate description is omitted.
<First Embodiment>
First, the heat exchanger 10 of the first embodiment shown in FIG. 1 will be described. The heat exchanger 10 of the present embodiment is arranged, for example, in the intake passage of the vehicle. The intake passage supplies the intake air supercharged by the supercharger to the internal combustion engine. The heat exchanger 10 exchanges heat between the supercharged intake air flowing through the intake passage and the cooling water. The heat exchanger 10 is a so-called two-temperature heat exchanger in which two systems of cooling water having different temperatures flow. In the following, of the two types of cooling water, the cooling water having a lower temperature will be referred to as "low temperature side cooling water", and the cooling water having a higher temperature will be referred to as "high temperature side cooling water". In the present embodiment, the high temperature side cooling water corresponds to the first cooling water, and the low temperature side cooling water corresponds to the second cooling water. The low temperature side cooling water is supplied to the heat exchanger 10 through the low temperature side cooling circuit. The low temperature side cooling circuit is, for example, a circuit for circulating cooling water between the low temperature side radiator and the heat exchanger 10. The high temperature side cooling water is supplied to the heat exchanger 10 through the high temperature side cooling circuit. The high temperature side cooling circuit is a circuit for circulating cooling water between, for example, the high temperature side radiator, the internal combustion engine, and the heat exchanger 10. The heat exchanger 10 cools or heats the intake air by exchanging heat between the two types of cooling water and the intake air.

As shown in FIG. 1, the heat exchanger 10 includes a heat exchange unit 20, caulking plates 22, 23, and tanks 30, 31.
The heat exchange unit 20 is formed in a substantially rectangular parallelepiped shape. The heat exchange section 20 is basically formed of an aluminum alloy. The heat exchange unit 20 includes a core unit 21 and pipes 24a, 24b, 25a, 25b.

The core portion 21 is a portion that exchanges heat between the intake air and the cooling water. As shown in FIG. 2, the core portion 21 has a plurality of flow path forming plate members 210 and a plurality of outer fins 211.
The plurality of flow path forming plate members 210 are stacked and arranged at predetermined intervals in the direction indicated by the arrow Z in the drawing. Each flow path forming plate member 210 is formed by joining a plate-shaped first plate piece 210a and a second plate piece 210b. The first plate piece 210a and the second plate piece 210b may be formed separately or integrally. The flow path forming plate member 210 in which the first plate piece 210a and the second plate piece 210b are integrally formed is manufactured, for example, by bending one plate on which the first plate piece 210a and the second plate piece 210b are formed. can. Intake flows in the gap formed between the flow path forming plate members 210 in the direction indicated by the arrow Y in the drawing. The direction indicated by the arrow Y is a direction orthogonal to the direction indicated by the arrow Z.

Hereinafter, the direction indicated by the arrow Z is referred to as "plate stacking direction Z", and the direction indicated by the arrow Y is referred to as "intake flow direction Y". Further, the direction X orthogonal to both the plate stacking direction Z and the intake air flow direction Y is the longitudinal direction of the heat exchange portion 20. Therefore, the direction indicated by the arrow X is referred to as "longitudinal direction X of the heat exchange portion". In the present embodiment, the heat exchange portion longitudinal direction X corresponds to a predetermined direction.

As shown in FIG. 3, the first plate piece 210a is made of a plate-shaped member. The first plate piece 210a is formed with a first recess R11 and a second recess R12.
The first recess R11 is formed so as to extend linearly from one end E11 to the other end E12 of the first plate piece 210a in the longitudinal direction X of the heat exchange portion. In the first recess R11, a high temperature side inner fin 216 for increasing the heat transfer area with respect to the high temperature side cooling water is arranged. A cup portion C11a having a shape protruding in the plate stacking direction Z is formed at one end of the first recess R11. A cup portion C12a having a similar shape is also formed at the other end of the first recess R11. The cup portion C12a is arranged at one end E11 of the first plate piece 210a, and the cup portion C11a is arranged at the other end E12 of the first plate piece 210a. Through holes 212a and 213a are formed in the cup portions C11a and C12a, respectively.

The second recess R12 is arranged on the downstream side of the intake flow direction Y with respect to the first recess R11. The second recess R12 includes two straight portions W120 and W121 formed so as to extend linearly in the longitudinal direction X of the heat exchange portion, and a turning portion W122 formed so as to communicate one end portions thereof. There is. The turning portion W122 is located at the other end E12 of the first plate piece 210a. The low temperature side inner fins 217 for increasing the heat transfer area with respect to the low temperature side cooling water are arranged in the straight portions W120 and W121, respectively. A cup portion C13a is also formed at the end portion of the straight portion W120 opposite to the end portion connected to the turning portion W122 as in the case of the first recess R11. Further, a cup portion C14a is also formed at an end portion of the straight portion W121 opposite to the end portion connected to the turning portion W122. The cup portions C13a and C14a are located at one end portion E11 of the first plate piece 210a. Through holes 214a and 215a are formed in the cup portions C13a and C14a, respectively.

A plurality of slits S11 are formed between the region A11 in which the first recess R11 is formed and the region A12 in which the second recess R12 is formed in the first plate piece 210a. The slit S11 is provided to suppress heat transfer between the high temperature side region A11 and the low temperature side region A12.

As shown in FIG. 2, the second plate piece 210b is joined to one outer surface of the first plate piece 210a in the plate stacking direction Z by brazing. The space surrounded by the first recess R11 of the first plate piece 210a and the second plate piece 210b forms the high temperature side flow path W11. The high temperature side flow path W11 has a so-called I-flow shape formed in a straight line. The space surrounded by the second recess R12 of the first plate piece 210a and the second plate piece 210b forms the low temperature side flow path W12. The low temperature side flow path W12 has a so-called U flow shape formed in a U shape. In the present embodiment, the high temperature side flow path W11 corresponds to the first flow path, and the low temperature side flow path W12 corresponds to the second flow path.

As shown in FIG. 4, the second plate piece 210b faces the region A21 arranged so as to face the high temperature side region A11 of the first plate piece 210a and the low temperature side region A12 of the first plate piece 210a. It has a region A22 arranged in such a manner. Similar to the first plate piece 210a, the second plate piece 210b is also formed with a plurality of slits S21 between the high temperature side region A21 and the low temperature side region A22. In the high temperature side region A21 of the second plate piece 210b, cup portions C11b and C12b are formed at positions corresponding to the cup portions C11a and C12a of the first plate piece 210a. Through holes 212b and 213b are formed in the cup portions C11b and C12b, respectively. In the low temperature side region A22 of the second plate piece 210b, cup portions C13b and C14b are formed at positions corresponding to the cup portions C13a and C14a of the first plate piece 210a, respectively. Through holes 214b and 215b are formed in the cup portions C13b and C14b, respectively.

As shown in FIG. 5, the cup portion C12a of the first plate piece 210a projects toward the flow path forming plate member 210 adjacent to the upper side. The cup portion C12a of the second plate piece 210b projects downward toward the adjacent flow path forming plate member 210. The upper surface of the cup portion C12a of the first plate piece 210a is joined to the bottom surface of the cup portion C12b of the second plate piece 210b of the adjacent flow path forming plate member 210 by brazing. The through hole 213a formed in the cup portion C12a of the first plate piece 210a and the through hole 213b formed in the cup portion C12b of the second plate piece 210b communicate with each other. The space surrounded by the through holes 213a and 213b and the cup portions C12a and C12b of each flow path forming plate member 210 forms the first collecting tank space T12. The first collecting tank space T12 is open on the upper surface 20a of the heat exchange section 20. A first outflow pipe 24b is joined to the upper surface 20a of the heat exchange portion 20 by brazing so as to communicate with the opening portion of the first collecting tank space T12.

Although not shown, the cup portion C11a of the first plate piece 210a is similarly joined to the cup portion C11b of the second plate piece 210b of the adjacent flow path forming plate member 210, and the cup portions C11a and C11b. The through holes 212a and 212b of the above are communicated with each other. Further, the cup portion C13a of the first plate piece 210a is similarly joined to the cup portion C13b of the second plate piece 210b of the adjacent flow path forming plate member 210, and the through holes 214a of the cup portions C13a and C13b are respectively joined. , 214b communicate with each other. Further, the cup portion C14a of the first plate piece 210a is similarly joined to the cup portion C14b of the second plate piece 210b of the adjacent flow path forming plate member 210, and the through holes 215a of the cup portions C14a and C14b, respectively. , 215b communicate with each other.

As shown in FIG. 6, a second distribution tank space T21 and a second assembly tank space T22 are formed at one end E11 of the heat exchange portion 20 so as to be aligned with the first assembly tank space T12 in the intake flow direction Y. ing. The second distribution tank space T21 is composed of a space surrounded by through holes 214a and 214b of each flow path forming plate member 210 and cup portions C13a and C13b. The second collecting tank space T22 is composed of a space surrounded by through holes 215a and 215b of each flow path forming plate member 210 and cup portions C14a and C14b. The second distribution tank space T21 is open on the upper surface 20a of the heat exchange section 20. A second inflow pipe 25a is joined to the upper surface 20a of the heat exchange portion 20 by brazing so as to communicate with the opening portion of the second distribution tank space T21. The second collecting tank space T22 is open at the bottom surface 20b of the heat exchange unit 20. A second outflow pipe 25b is joined to the bottom surface 20b of the heat exchange portion 20 by brazing so as to communicate with the opening portion of the second collecting tank space T22.

As shown in FIG. 7, a first distribution tank space T11 is formed in the other end E12 of the heat exchange unit 20. The first distribution tank space T11 is composed of a space surrounded by through holes 212a and 212b of each flow path forming plate member 210 and cup portions C11a and C11b. The first distribution tank space T11 is open on the upper surface 20a of the heat exchange section 20. A first inflow pipe 24a is joined to the upper surface 20a of the heat exchange portion 20 by brazing so as to communicate with the opening portion of the first distribution tank space T11.

In the heat exchanger 10 of the present embodiment, the space formed by the cup portions C11a and C11b corresponds to the first inflow portion, the space formed by the cup portions C12a and C12b corresponds to the first outflow portion, and the cup portion. The space formed by C13a and C13b corresponds to the second inflow portion, and the space formed by the cup portions C14a and C14b corresponds to the second outflow portion.

In the heat exchange unit 20, the high temperature side cooling water flows into the first distribution tank space T11 through the hose connected to the first inflow pipe 24a. The high-temperature side cooling water that has flowed into the first distribution tank space T11 is distributed to the high-temperature side flow path W11 of each flow path forming plate member 210. The high-temperature side cooling water that has flowed through the high-temperature side flow path W11 of each flow path forming plate member 210 is collected in the first collecting tank space T12 and then discharged from the first outflow pipe 24b.

Further, in the heat exchange unit 20, the low temperature side cooling water flows into the second distribution tank space T21 through the hose connected to the second inflow pipe 25a. The high-temperature side cooling water that has flowed into the second distribution tank space T21 is distributed to the low-temperature side flow path W12 of each flow path forming plate member 210. The low-temperature side cooling water that has flowed through the low-temperature side flow path W12 of each flow path forming plate member 210 is collected in the second collecting tank space T22 and then discharged from the second outflow pipe 25b.

As shown in FIG. 2, the inflow side caulking plate 22 is provided on the outer peripheral portion of the end portion on the upstream side of the intake flow direction Y in the heat exchange core portion 21. As shown in FIG. 8, the inflow side caulking plate 22 is formed in a square ring shape. As shown in FIG. 2, a bent portion 220 is formed at one end of the inflow side caulking plate 22 on the downstream side in the intake flow direction Y so as to be bent inward. The inflow side caulking plate 22 is fixed to the heat exchange core portion 21 by joining the tip portion of the bent portion 220 to the heat exchange core portion 21 by brazing. The inflow side tank 30 is inserted into the inflow side caulking plate 22. A packing 32a for sealing the gap between the inflow side caulking plate 22 and the inflow side tank 30 is arranged. As shown in FIG. 1, the inflow side tank 30 is fixed to the heat exchange core portion 21 by caulking the inflow side caulking plate 22 into the inflow side tank 30.

As shown in FIG. 2, the outflow side caulking plate 23 also has the same shape as the inflow side caulking plate 22. That is, the outflow side caulking plate 23 also has a bent portion 230. The bent portion 230 is joined to the heat exchange core portion 21 by brazing, so that the outflow side caulking plate 23 is fixed to the heat exchange core portion 21. The outflow side tank 31 and the packing 32b are inserted into the outflow side caulking plate 23. As shown in FIG. 1, the outflow side caulking plate 23 is crimped to the outflow side tank 31, so that the outflow side tank 31 is fixed to the heat exchange core portion 21. In the present embodiment, the caulking plates 22 and 23 correspond to the assembling members to which the tanks 30 and 31 are assembled.

As shown in FIG. 1, in the heat exchanger 10, the intake air flows in from the opening portion 30a of the inflow side tank 30. As shown in FIG. 2, the intake air that has flowed into the inflow side tank 30 flows through the gap formed between the flow path forming plate members 210 and flows into the outflow side tank 31, and then flows out as shown in FIG. It is discharged from the opening portion 31a of the side tank 31. As shown in FIG. 2, the outer fins 211 arranged between the flow path forming plate members 210 increase the heat transfer area with respect to the intake air. In the present embodiment, the inflow side tank 30 corresponds to a guide unit that guides the introduction of intake air into the heat exchange unit 20. Further, the outflow side tank 31 corresponds to a guide portion that guides the air that has passed through the heat exchange portion 20.

In the heat exchanger 10, when the intake air flows through the gap formed between the flow path forming plate members 210, the high temperature side cooling water and the low temperature side cooling water flowing inside each flow path forming plate member 210 are The intake air is cooled or heated by exchanging heat with the intake air flowing outside each flow path forming plate member 210.
According to the heat exchanger 10 of the present embodiment described above, the actions and effects shown in the following (1) to (6) can be obtained.

(1) A first outflow pipe 24b, a second inflow pipe 25a, and a second outflow pipe 25b are provided at one end E11 of the heat exchange unit 20. A first inflow pipe 24a is provided at the other end E12 of the heat exchange unit 20. A first outflow pipe 24b and a second inflow pipe 25a are provided on the upper surface 20a of the plate stacking direction Z at one end E11 of the heat exchange portion 20. A second outflow pipe 25b is provided on the bottom surface 20b of the plate stacking direction Z at one end E11 of the heat exchange section 20. According to such a configuration, as compared with the case where all of the first outflow pipe 24b, the second inflow pipe 25a, and the second outflow pipe 25b are provided on the upper surface 20a of the one end portion E11 of the heat exchange portion 20. It becomes easier to form a space between each pipe. Further, since only the first inflow pipe 24a is provided at the other end E12 of the heat exchange portion 20, it is easy to form a space around the first inflow pipe 24a. Therefore, even when the heat exchanger 10 is miniaturized, it is possible to form a space between the pipes.

(2) The caulking plates 22 and 23 are joined to the heat exchange portion 20 by brazing. Since the caulking plates 22 and 23 for assembling the heat exchange portion 20 and the tanks 30 and 31 are required to have a certain degree of durability, a thicker member is used as compared with the flow path forming plate member 210. As a result, the heat capacity of the caulking plates 22 and 23 tends to be large. Therefore, when brazing each part in the manufacturing process of the heat exchanger 10, it is necessary to consider the temperature rising property of the caulking plates 22 and 23. If the high temperature side flow path W11 of the heat exchange unit 20 is formed in a U shape as in the heat exchanger described in Patent Document 1 described above, four pipes are arranged at one end E11 of the heat exchange unit 20. there is a possibility. In the case of such a structure, when the heat exchanger 10 is put into the furnace for brazing and heated, the heat is transferred to the four pipes having a large heat capacity, and the area around the portion where the four pipes are arranged. There is a concern that the temperature of the caulking plate will not rise easily. As a result, insufficient brazing may occur. In this regard, if the pipes 24a, 24b, 25a, 25b are dispersedly arranged in the heat exchange section 20 as in the heat exchanger 10 of the present embodiment, the caulking plates 22 and 23 are partially heated. Since it is possible to avoid a difficult situation, the caulking plates 22 and 23 can be brazed to the heat exchange unit 20 more reliably. As a result, the manufacturability of the heat exchanger 10 can be improved.

(3) In order to improve the strength of the caulking plates 22 and 23, it is important to reduce the residual stress generated in them as much as possible. In this regard, when the heat exchanger 10 is mounted on the vehicle, hoses for cooling water are connected to the pipes 24a, 24b, 25a, 25b, and therefore heat exchange is performed by an external force applied to each pipe at that time. Residual stress is likely to occur in the peripheral portion of each pipe in the portion 20. If four pipes are arranged at one end E11 of the heat exchange unit 20, residual stress is locally concentrated at one end of the caulking plates 22 and 23 arranged near one end E11 of the heat exchange unit 20. Therefore, there is a concern that the strength of the caulking plates 22 and 23 will decrease at that portion. In this regard, if the pipes 24a, 24b, 25a, 25b are dispersedly arranged in the heat exchange section 20 as in the heat exchanger 10 of the present embodiment, the pipes 24a, 24b, 25a, and 25b are locally arranged in a part of the caulking plates 22, 23. Since it is possible to avoid the concentration of residual stress, it is possible to suppress a decrease in the strength of the caulking plates 22 and 23.

(4) As a heat exchanger that exchanges heat between intake air and cooling water, for example, a so-called case-insertion type heat exchanger having a structure in which a heat exchange portion is inserted and fixed in a box-shaped duct case through which intake air passes. There is. In such a case-insertion type heat exchanger, in order to ensure the sealing property between the duct case and the heat exchange portion, a flange portion is formed in the heat exchange portion, and then the duct case is fastened with bolts via the flange portion. A structure for fixing the duct case and the heat exchange portion, or a structure for fixing the duct case and the heat exchange portion by welding via a flange portion is generally adopted. Therefore, it is necessary to provide a bolt hole or a welded portion on the peripheral edge of the flange portion. As a result, the width of the flange portion becomes long, which causes a problem that the size of the heat exchange portion becomes small. In this regard, in the case of a structure in which the heat exchange section 20 and the tanks 30 and 31 are assembled via the caulking plates 22 and 23 as in the heat exchanger 10 of the present embodiment, it is necessary to provide a flange portion in the heat exchange section 20. Therefore, it is possible to solve the problem that the size of the heat exchange unit 20 is reduced as described above.

(5) In the case-insertion type heat exchanger, the duct case has a structure in which a portion where the intake air flows in, a portion where the heat exchange portion is inserted, and a portion where the intake air flows out are integrally formed. Therefore, basically, the inflow portion of the intake air, the insertion portion of the heat exchange portion, and the outflow portion of the intake air are all formed of the same material. On the other hand, in the heat exchanger 10 of the present embodiment, since the inflow side tank 30 and the outflow side tank 31 are separate bodies, it is possible to form them with different materials. In the inflow side tank 30, since the intake air can be warmed up by the cooling water flowing through the high temperature side flow path W11, even if condensed water is generated in the inflow side tank 30, the condensed water can be evaporated. It is possible. As a result, it is unlikely that the condensed water adheres to the outflow side tank 31, so that corrosion due to the adhesion of the condensed water is unlikely to occur in the outflow side tank 31. Therefore, as the material of the outflow side tank 31, it is possible to use an inexpensive material having lower corrosion resistance than the inflow side tank 30, for example, a resin material. Further, since the packing 32b provided between the outflow side tank 31 and the heat exchange section 20 is also less likely to be corroded, it is possible to use an inexpensive material having low corrosion resistance as the material.

(6) If the high temperature side flow path W11 has the shape of the I flow as in the heat exchanger 10 of the present embodiment, the high temperature side cooling flowing through the high temperature side flow path W11 is compared with the shape of the U flow. The resistance to water flow is reduced. This has the advantage that the pump that pumps the cooling water in the high-temperature side cooling circuit can be miniaturized. However, when the high temperature side flow path W11 has the shape of an I flow, the high temperature side cooling water flows through the high temperature side flow path W11 from the upstream side to the downstream side while exchanging heat with the intake air, so that the high temperature side flow Deviations are likely to occur in the temperature of the cooling water between the upstream side and the downstream side of the path W11. This causes a deviation in the temperature distribution of the intake air in the longitudinal direction X of the heat exchange portion. In this regard, in the heat exchanger 10 of the present embodiment, since the low temperature side flow path W12 arranged on the downstream side of the high temperature side flow path W11 in the intake flow direction Y has a U flow shape, it is assumed that the high temperature side is on the high temperature side. Even if there is a deviation in the temperature distribution of the intake air that has passed through the flow path W11, the deviation in the temperature distribution of the intake air is alleviated by exchanging heat with the low temperature side cooling water that flows through the low temperature side flow path W12. It becomes easy to be done.

<Second Embodiment>
Next, a second embodiment of the heat exchanger 10 will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.
In the heat exchanger 10 of the first embodiment having a structure as shown in FIG. 2, when the brazing material of each part of the heat exchange part 20 is melted when brazing each part of the heat exchange part in the manufacturing process, The gap between the parts is reduced. In particular, in a portion where a plurality of flow path forming plate members 210 are arranged, such as the core portion 21 of the heat exchange portion 20, there are many places where the gap between the parts is reduced. Therefore, as shown in FIG. 9, the outer shape of the heat exchange core portion 21 is deformed from the shape shown by the alternate long and short dash line to the shape shown by the solid line, that is, deformed so as to shrink in the plate stacking direction Z. If a gap is formed between the heat exchange core portion 21 and the caulking plates 22 and 23 as a result of such a subduction phenomenon of the heat exchange core portion 21, there is a concern that they cannot be brazed. In order to eliminate this concern, the heat exchanger 10 of the present embodiment has a structure as shown in FIG.

As shown in FIG. 10, the heat exchanger 10 of the present embodiment includes a duct case 60 arranged so as to surround the heat exchange core portion 21. The duct case 60 is composed of an upper duct plate member 61 and a lower duct plate member 62. The lower duct plate member 62 is composed of a plate-shaped member formed in a concave shape, and is formed on the bottom surface of the heat exchange core portion 21 in the plate stacking direction Z and on both side surfaces of the heat exchange core portion 21 in the heat exchange portion longitudinal direction X. They are arranged so as to face each other. The upper duct plate member 61 is made of a plate-shaped member, and is arranged so as to face the upper surface of the heat exchange core portion 21 in the plate stacking direction Z. The duct case 60 is formed in a square ring shape as a whole by joining the upper duct plate member 61 to the lower duct plate member 62 so as to close the upper opening portion of the lower duct plate member 62.

As shown in FIG. 11, bent portions 611 and 612 are formed at both ends of the upper duct plate member 61 in the intake flow direction Y so as to be bent outward. The bent portions 611 and 612 are joined to the bent portions 220 and 230 of the caulking plates 22 and 23 by surface contact and brazing, respectively.

According to the heat exchanger 10 of the present embodiment described above, the actions and effects shown in the following (7) and (8) can be further obtained.
(7) In the heat exchanger 10 of the present embodiment, as shown in FIG. 12, the heat exchange core portion 21 temporarily changed from the shape shown by the alternate long and short dash line to the shape shown by the solid line during the brazing step. Even so, it is possible to secure a state in which the bent portion 611 of the upper duct plate member 61 is in contact with the bent portion 220 of the inflow side caulking plate 22. Similarly, it is possible to secure a state in which the bent portion 612 of the upper duct plate member 61 is in contact with the bent portion 230 of the inflow side caulking plate 22. Therefore, since the bent portions 611 and 612 of the upper duct plate member 61 and the bent portions 220 and 230 of the caulking plates 22 and 23 are more reliably joined by brazing, the heat exchange core portion 21 and the caulking plates 22 and 23 are joined. The state of joining with can be maintained.

(8) The heat exchange unit 20 further includes a duct case 60 provided so as to surround the outer periphery of the heat exchange core unit 21. According to such a configuration, the flow of intake air can be guided by the duct case 60, so that the heat exchange performance of the heat exchanger 10 can be improved.
<Third Embodiment>
Next, a third embodiment of the heat exchanger 10 will be described. Hereinafter, the differences from the heat exchanger 10 of the second embodiment will be mainly described.

In the plate pieces 210a and 210b of each flow path forming plate member 210, a sacrificial layer may be applied to the inner surface of the core material. The sacrificial layer is made of a metal containing a material that is potentially lower than the core material in a predetermined ratio, for example, an aluminum alloy containing zinc (Zn). In the plate pieces 210a and 210b having such a structure, the cooling water flowing through the high temperature side flow path W11 and the low temperature side flow path W12 comes into contact with the sacrificial layer. As a result, the sacrificial layer is preferentially corroded over the core material, so that the core material is less likely to be corroded.

By the way, in the heat exchanger 10 shown in FIG. 5, the ends of the plate pieces 210a and 210b of each flow path forming plate member 210 are in contact with each other. Therefore, when the sacrificial layer is applied to the surface of the core material of the plate pieces 210a and 210b, the sacrificial layers of the plate pieces 210a and 210b come into contact with each other. In the case of such a structure, there is a concern that zinc is locally concentrated at the portion where the sacrificial layers of the plate pieces 210a and 210b are in contact with each other, and the corrosion resistance is significantly lowered at that portion.

Therefore, in the heat exchanger 10 of the present embodiment, as shown in FIG. 13, a spacer is provided between one end of the first plate piece 210a and one end of the second plate piece 210b of each flow path forming plate member 210. 40 are arranged. The spacer 40 is arranged so as to be sandwiched between the bottom surfaces of the cup portions C12a, C13a, and C14a of the first plate piece 210a and the second plate piece 210b.

As shown in FIG. 14, the spacer 40 is made of a plate-shaped member. Through holes 401, 402, and 403 are formed in the spacer 40 at positions corresponding to the first collecting tank space T12, the second distribution tank space T21, and the second collecting tank space T22 of the heat exchange core portion 21, respectively. ..

Similarly, a spacer 41 as shown in FIG. 15 is also arranged between the other end of the first plate piece 210a and the other end of the second plate piece 210b of each flow path forming plate member 210. There is. A through hole 411 is formed in the spacer 41 at a position corresponding to the first distribution tank space T11 of the heat exchange core portion 21. The spacer 41 is formed with a base portion 412 on which a through hole 411 is formed and a protruding portion 413 protruding from the base portion 412 in the plate stacking direction Z. The bottom surface of the base portion 412 of the spacer 41 is joined to the upper surface of the second plate piece 210b by brazing. The upper surface of the protruding portion 413 is joined to the lower surface of the turning portion W122 of the first plate piece 210a by brazing. Therefore, the spacer 41 is arranged so as to be sandwiched between the other end of the first plate piece 210a and the other end of the second plate piece 210b.

According to the heat exchanger 10 of the present embodiment described above, the actions and effects shown in (9) below can be further obtained.
(9) Spacers 40 and 41 are arranged between both ends of the first plate piece 210a and both ends of the second plate piece 210b, respectively. As a result, it is possible to avoid direct contact between both ends of the first plate piece 210a and both ends of the second plate piece 210b, so that the above-mentioned phenomenon of local concentration of zinc is less likely to occur. .. Therefore, it is possible to avoid a decrease in the corrosion resistance of the heat exchange core portion 21.

<Fourth Embodiment>
Next, a fourth embodiment of the heat exchanger 10 will be described. Hereinafter, the differences from the heat exchanger 10 of the third embodiment will be mainly described.
As shown in FIG. 16, in the first plate piece 210a of the heat exchanger 10 of the present embodiment, cup portions C15a and C16a are further formed in a portion where the turning portion W122 is formed. Through holes 218a and 219a are formed in the cup portions C15a and C16a, respectively. As shown in FIG. 17, the second plate piece 210b is further formed with cup portions C15b and C16b at positions facing the turning portion W12. Through holes 218b and 219b are formed in the cup portions C15b and C16b, respectively. The cup portions C15a and C16a of the first plate piece 210a are formed so as to project in the plate stacking direction Z toward the adjacent flow path forming plate member 210, and the second plate of the adjacent flow path forming plate member 210 is formed. It is joined to the cup portions C15b and C16b of the piece 210b, respectively. The through hole 218a formed in the cup portion C15a of the first plate piece 210a communicates with the through hole 218b formed in the cup portion C15b of the second plate piece 210b of the adjacent flow path forming plate member 210. Similarly, the through hole 219a formed in the cup portion C16a of the first plate piece 210a communicates with the through hole 219b formed in the cup portion C16b of the second plate piece 210b of the adjacent flow path forming plate member 210. There is. As shown in FIG. 18, through holes 414 are formed in the spacer 41 at positions corresponding to the through holes 218a and 218b of the plate pieces 210a and 210b, and the through holes 219a of the plate pieces 210a and 210b are formed. A through hole 415 is formed at a position corresponding to 219b.

In the present embodiment, the cup portions C15a and C15b correspond to the cup portions C13a and C13b corresponding to the second inflow portion and the cup portions facing each other in the heat exchange portion longitudinal direction X. Further, the cup portions C16a and C16b correspond to the cup portions C14a and C14b corresponding to the second outflow portion and the cup portions facing each other in the heat exchange portion longitudinal direction X.

The through hole 218a of the first plate piece 210a, the through hole 218b of the second plate piece 210b, and the through hole 414 of the spacer 41 communicate with each other, so that the intermediate tank space T23 as shown in FIG. 19 has a heat exchange core portion. It is formed inside 21. Further, the through hole 219a of the first plate piece 210a, the through hole 219b of the second plate piece 210b, and the through hole 415 of the spacer 41 communicate with each other, so that the intermediate tank space T24 as shown in FIG. 19 exchanges heat. It is formed inside the core portion 21. The low temperature side flow paths W12 of each flow path forming plate member 210 communicate with each other through the intermediate tank spaces T23 and T24. In the present embodiment, the intermediate tank spaces T23 and T24 correspond to the communication portions formed between the second distribution tank space T21 and the second collecting tank space T22 in the low temperature side flow path W12.

According to the heat exchanger 10 of the present embodiment described above, the actions and effects shown in the following (10) to (12) can be further obtained.
(10) In the low temperature side flow path W12 formed in a U shape, the flow of the cooling water tends to stagnate at the turning portion W122, and the air contained in the cooling water tends to accumulate in that portion. If air accumulates in the turning portion W122, there is a concern that the heat exchange performance with the intake air may be significantly deteriorated in that portion. In this regard, in the heat exchanger 10 of the present embodiment, since the intermediate tank spaces T23 and T24 are formed in the turning portion W122, the cooling water passes through the intermediate tank spaces T23 and T24 in the turning portion of each flow path forming plate member 210. It will flow between W122. As a result, stagnation is less likely to occur in the cooling water flowing through the turning portion W122, so that air is less likely to accumulate in the turning portion W122. Therefore, it is possible to avoid deterioration of the heat exchange performance of the heat exchanger 10.

(11) In the portion of each flow path forming plate member 210 where the turning portion W12 is formed, the cup portions C15a and C16a of the flow path forming plate member 210 are the cup portions C15b and C16b of the adjacent flow path forming plate member 210. It is joined to. As a result, the strength in the plate stacking direction Z is ensured particularly in the portion of the flow path forming plate member 210 where the turning portion W12 is arranged, as compared with the structure in which the cup portions C15a, C16a, C15b, and C16b are not provided. Can be done. A compressive force is applied to the heat exchanger 10 in the plate stacking direction Z in order to bring the parts into close contact with each other in the brazing process at the time of manufacture. If the strength in the plate stacking direction Z can be ensured in the heat exchanger 10, it is possible to prevent the heat exchanger 10 from being deformed when a compressive force is applied to the heat exchanger 10 in the brazing step. can.

(12) The end portion E12 of the flow path forming plate member 210 is provided with cup portions C15a and C15b at positions facing the cup portions C13a and C13b in the heat exchange portion longitudinal direction X, and in the heat exchange portion longitudinal direction X. Cup portions C16a and C16b are provided at positions facing the cup portions C14a and C14b. As a result, the spacer 41 as shown in FIG. 18 can be used. The spacer 41 shown in FIG. 18 has the same shape as the spacer 40 shown in FIG. That is, since the spacers 40 and 41 arranged at both ends E11 and E12 of the heat exchange unit 20 can be shared, the manufacturing cost can be reduced.

(Modification example)
Next, a modification of the heat exchanger 10 of the fourth embodiment will be described.
The heat exchanger 10 may have a structure that does not have intermediate tank spaces T23 and T24. Specifically, the through holes 218a and 219a may not be formed in the cup portions C15a and C16a of the first plate piece 210a of the fourth embodiment. Similarly, through holes 218b and 219b may not be formed in the cup portions C15b and C16b of the second plate piece 210b. Even with such a structure, it is possible to exert the actions and effects shown in the above (11) and (12).

<Fifth Embodiment>
Next, a fifth embodiment of the heat exchanger 10 will be described. Hereinafter, the differences from the heat exchanger 10 of the fourth embodiment will be mainly described.
As shown in FIG. 20, a communication passage 613 is further formed in the upper duct plate member 61 of the heat exchange unit 20 of the present embodiment. The communication passage 613 is formed so as to extend from the upper end portion of the second distribution tank space T21 in the longitudinal direction X of the heat exchange portion. The upper end of the second distribution tank space T21 is connected to one end of the communication passage 613. A second inflow pipe 25a is connected to the other end of the communication passage 613. In the present embodiment, the second distribution tank space T21 corresponds to a specific tank space.

According to the heat exchanger 10 of the present embodiment described above, the actions and effects shown in (13) below can be further obtained.
(13) In the heat exchanger 10 of the present embodiment, the second inflow pipe 25a and the second distribution tank space T21 can be arranged at positions shifted from each other in the plate stacking direction Z. Therefore, since the degree of freedom in arranging the second inflow pipe 25a can be improved, it is possible to easily secure a space for the hose attached to the second inflow pipe 25a.

<Sixth Embodiment>
Next, a sixth embodiment of the heat exchanger 10 will be described. Hereinafter, the differences from the heat exchanger 10 of the fifth embodiment will be mainly described.
When the slits S11 and S12 as shown in FIGS. 3 and 4 are formed in the flow path forming plate member 210, the first plate piece 210a and the second plate piece 210b do not come into contact with each other at that portion. As a result, the contact points between the first plate piece 210a and the second plate piece 210b are reduced. In the heat exchanger 10 in which the parts are joined by brazing, each part is brazed by the contact point between the first plate piece 210a and the second plate piece 210b as the starting point of brazing. However, when the contact points between the first plate piece 210a and the second plate piece 210b are reduced due to the formation of the slits S11 and S12, the points serving as the starting point of brazing are reduced. This causes an unbrazed portion to be generated in the inner portion of the heat exchange portion 20. In order to improve this, in the heat exchanger 10 of the present embodiment, the flow path forming plate member 210 has a structure as shown in FIGS. 21 and 22.

As shown in FIG. 22, in the flow path forming plate member 210 of the present embodiment, an erection portion 50 is formed between the high temperature side region A1 and the low temperature side region A2. The erection portion 50 is a portion provided between the plurality of slits S1 in the flow path forming plate member 210 as shown in FIG. 21. As shown in FIG. 22, the erection portion 50 is formed with a claw portion 51 so as to be bent in the plate stacking direction Z. The claw portion 51 is formed so as to be bent in the direction in which the recesses R11 and R12 protrude in the first plate piece 210a, in other words, in the height direction of the respective flow paths W11 and W12. As shown in FIG. 23, the claw portion 51 is formed by double bending the erection portion 50a of the first plate piece 210a and the erection portion 50b of the second plate piece 210b.

According to the heat exchanger 10 of the present embodiment described above, the actions and effects shown in the following (14) to (17) can be further obtained.
(14) Since the erection portion 50a of the first plate piece 210a and the erection portion 50b of the second plate piece 210b can be more reliably brought into contact with each other at the claw portion 51 of the flow path forming plate member 210, brazing is performed at that location. The starting point of is easily provided. Therefore, even when a plurality of slits S1 are formed in the flow path forming plate member 210, the brazing property can be ensured.

(15) As described above, a sacrificial layer may be provided on the inner surface of each of the plate pieces 210a and 210b in order to ensure corrosiveness to cooling water. On the other hand, the outer surface of each plate piece 210a, 210b is usually not provided with a sacrificial layer. The "inner surface" here is the surface of the plate pieces 210a and 210b in the thickness direction that the cooling water comes into contact with. On the other hand, the "outer surface" is the surface of each of the plate pieces 210a and 210b in the thickness direction that the intake air comes into contact with. When the erection portions 50a and 50b are bent in such plate pieces 210a and 210b, if the inner surface and the outer surface of the erection portions 50a and 50b come into contact with each other, the sacrificial layer on the inner surface of the erection portions 50a and 50b comes into contact with the outer surface. , The corrosion resistance of the outer surfaces of the erection portions 50a and 50b is lowered. In this regard, in the heat exchanger 10 of the present embodiment, as shown in FIG. 23, the erection portion 50a of the first plate piece 210a and the erection portion 50b of the second plate piece 210b are doubly bent to form a claw portion. Since the 51 is formed, it is possible to avoid contact between the inner surface and the outer surface of the erection portions 50a and 50b. Therefore, it is possible to avoid a decrease in corrosion resistance of the outer surfaces of the erection portions 50a and 50b as described above.

(16) The claw portion 51 is formed so as to be bent in the height direction of each of the flow paths W11 and W12. As a result, it is possible to prevent the claw portion 51 from protruding from the flow path forming plate member 210 in the plate stacking direction Z, so that the claw portion 51 is less likely to come into contact with other parts, for example, when manufacturing the heat exchanger 10. Therefore, the claw portion 51 is less likely to be damaged.

(17) As shown in FIG. 21, if all of the plurality of claws 51 are bent in one direction of the plate stacking direction Z, the claws 51 can be easily formed, so that the heat exchanger 10 can be formed. Manufacturability can be improved.
<7th Embodiment>
Next, a seventh embodiment of the heat exchanger 10 will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.

As shown in FIG. 24, a plurality of protrusions 70 are formed in the high temperature side flow path W11 of the first plate piece 210a of the present embodiment in place of the high temperature side inner fins 216.
According to the heat exchanger 10 of the present embodiment described above, the actions and effects shown in (18) below can be obtained.

(18) Since the inner fin 216 is not arranged in the high temperature side flow path W11, the water flow resistance of the high temperature side flow path W11 can be reduced. Further, by eliminating the inner fin 216, the heat transfer area for the cooling water is reduced, but in the heat exchanger 10 of the present embodiment, the heat is promoted by promoting the turbulent flow of the cooling water by the plurality of protruding portions 70. The transmission rate can be increased.

<8th Embodiment>
Next, an eighth embodiment of the heat exchanger 10 will be described.
The heat exchanger 10 of each embodiment can be used as a heat exchanger that exchanges heat between the supercharged intake air supplied to the internal combustion engine of the vehicle and the cooling water. Instead, for example, a fuel cell. It can also be used as a heat exchanger that exchanges heat between the supercharged intake air supplied to the engine and the cooling water. The fuel cell to which the heat exchanger 10 of each embodiment is applicable is not limited to the fuel cell mounted on the vehicle, and may be a fuel cell mounted on a vehicle other than the vehicle. As an example, the configuration when the heat exchanger 10 of each embodiment is mounted on the fuel cell vehicle will be described below.

As shown in FIG. 25, the fuel cell vehicle has an intake passage 82 for supplying supercharged intake air to the fuel cell stack 81 and an exhaust passage 83 for discharging the exhaust gas of the fuel cell stack 81 to the outside. Is provided. A heat exchanger 10 is provided in the intake passage 82. The heat exchanger 10 cools the supercharged intake air by exchanging heat between the supercharged intake air flowing through the intake air passage 82 and the cooling water.

The heat exchanger 10 includes a high temperature side heat exchange unit 20A and a low temperature side heat exchange unit 20B. In the intake passage 82, the high temperature side heat exchange section 20A is arranged on the upstream side in the air flow direction with respect to the low temperature side heat exchange section 20B. The high temperature side heat exchange unit 20A corresponds to a portion where the high temperature side flow path W11 is formed in the heat exchange unit 20 of the heat exchanger 10 of each embodiment. Cooling water flows into the high temperature side heat exchange section 20A through the first inflow pipe 24a. Further, the cooling water that has flowed through the high temperature side heat exchange unit 20A is discharged through the first outflow pipe 24b. The low temperature side heat exchange unit 20B corresponds to a portion where the low temperature side flow path W12 is formed in the heat exchange unit 20 of the heat exchanger 10 of each embodiment. Cooling water flows into the low temperature side heat exchange section 20B through the second inflow pipe 25a. Further, the cooling water that has flowed through the low temperature side heat exchange section 20B is discharged through the second outflow pipe 25b.

The fuel cell vehicle is equipped with a cooling circuit 90 for circulating cooling water in the heat exchanger 10. The cooling circuit 90 is composed of a high temperature side cooling circuit 100 and a low temperature side cooling circuit 110.
The high temperature side cooling circuit 100 includes a high temperature side radiator 101, a pump 102, a fuel cell stack 81, and a high temperature side heat exchange unit 20A. High temperature side cooling water circulates in these elements. The high temperature side radiator 101 cools the high temperature side cooling water by exchanging heat between the high temperature side cooling water flowing inside the radiator 101 and the air flowing outside the high temperature side cooling water. The pump 102 sucks in and discharges the high-temperature side cooling water cooled by the high-temperature side radiator 101. The fuel cell stack 81 and the high temperature side heat exchange unit 20A are connected in parallel to the pump 102. Therefore, the high-temperature side cooling water discharged from the pump 102 is supplied to the fuel cell stack 81 and the high-temperature side heat exchange unit 20A, respectively. The fuel cell stack 81 is cooled by absorbing its heat by the high-temperature side cooling water. The high temperature side heat exchange unit 20A cools the supercharged intake air by exchanging heat between the high temperature side cooling water flowing inside the high temperature side cooling water and the supercharged intake air flowing through the intake passage 82. The high-temperature side cooling water discharged from the fuel cell stack 81 and the high-temperature side heat exchange unit 20A, respectively, merges and is supplied to the high-temperature side radiator 101 to be cooled again.

The low temperature side cooling circuit 110 includes a low temperature side radiator 111, a pump 112, and a low temperature side heat exchange unit 20B. Cooling water on the low temperature side circulates in these elements. The low temperature side radiator 111 cools the low temperature side cooling water by exchanging heat between the low temperature side cooling water flowing inside the radiator 111 and the air flowing outside the low temperature side cooling water. The pump 112 sucks in and discharges the low temperature side cooling water cooled by the low temperature side radiator 111. The low temperature side cooling water discharged from the pump 112 flows into the low temperature side heat exchange unit 20B. The low temperature side heat exchange unit 20B cools the supercharged intake air by exchanging heat between the low temperature side cooling water flowing inside the low temperature side cooling water and the supercharged intake air flowing through the intake passage 82. The low temperature side cooling water discharged from the low temperature side heat exchange unit 20B is supplied to the low temperature side radiator 111 and is cooled again.

In this cooling circuit 90, the temperature of the high temperature side cooling water supplied to the high temperature side heat exchange unit 20A through the high temperature side cooling circuit 100 is higher than the temperature of the low temperature side cooling water supplied to the low temperature side heat exchange unit 20B through the low temperature side cooling circuit 110. The temperature of the water is lower. Therefore, after the rough heat of the supercharged intake air flowing through the intake passage 82 is removed by the high temperature side heat exchange unit 20A, the heat of the supercharged intake air from which the rough heat is removed is further removed by the low temperature side heat exchange unit 20B. Will be. As a result, the supercharged intake air can be efficiently cooled, so that the oxygen density in the air supplied to the fuel cell stack 81 can be increased. As a result, the power generation performance of the fuel cell stack 81 can be improved.

On the other hand, in the fuel cell stack 81, if there is a variation in the oxygen concentration in the air supplied inside the fuel cell stack 81, there is a concern that the power generation performance may deteriorate as a result of the concentration overvoltage occurring in the power generation reaction in the fuel cell. In this respect, in the heat exchanger 10 of the present embodiment, the low temperature side cooling water flows in the low temperature side heat exchange unit 20B arranged on the outlet side of the supercharged intake air in a U-turn shape or in a countercurrent form. , The temperature of the supercharged intake air that has passed through the heat exchanger 10 can be easily made uniform, and the oxygen concentration thereof can also be made uniform. As a result, the concentration overvoltage is less likely to occur in the fuel cell stack 81, so that the power generation performance of the fuel cell stack 81 can be improved.

<Other Embodiments>
In addition, each embodiment can also be implemented in the following embodiments.
-In the heat exchanger 10 of the third embodiment, the spacers 40 and 41 may be composed of a plurality of spacer pieces made of separate bodies. For example, the spacer 40 may be composed of three parts: a spacer piece on which the through hole 401 is formed, a spacer piece on which the through hole 402 is formed, and a spacer piece on which the through hole 403 is formed. According to such a configuration, the spacer pieces can be arranged only at the necessary positions of the heat exchange section 20, so that the materials required for the spacers 40 and 41 can be reduced.

The heat exchanger 10 of the fifth embodiment is not limited to a structure in which a communication passage 613 is formed with respect to the second inflow pipe 25a, and a communication portion is formed with other pipes 24a, 24b, 25b. It may have a structure that is present.
-The positions of the pipes 24a, 24b, 25a, and 25b can be changed as appropriate. In short, one end E11 of the heat exchange section 20 is provided with the first pipe of one of the first inflow pipe 24a and the first outflow pipe 24b, the second inflow pipe 25a, and the second outflow pipe 25b. I just need to be there. Further, the other end E12 of the heat exchange unit 20 may be provided with the other first pipe of the first inflow pipe 24a and the first outflow pipe 24b. Further, two of the first pipe, the second inflow pipe 25a, and the second outflow pipe 25b are provided on one outer surface of the plate stacking direction Z at one end E11 of the heat exchange portion 20. Just do it. Further, on the other outer surface of the plate stacking direction Z at one end E11 of the heat exchange section 20, the remaining one of the one first pipe, the second inflow pipe 25a, and the second outflow pipe 25b is provided. It suffices if it is done.

As shown in FIG. 26, even if the first outflow pipe 24b, the second inflow pipe 25a, and the second outflow pipe 25b are provided on the upper surface 20a of the plate stacking direction Z at one end E11 of the heat exchange portion 20. good.
-The present disclosure is not limited to the above specific examples. Specific examples described above with appropriate design changes by those skilled in the art are also included in the scope of the present disclosure as long as they have the features of the present disclosure. Each element included in each of the above-mentioned specific examples, and their arrangement, conditions, shape, and the like are not limited to those illustrated, and can be changed as appropriate. The combinations of the elements included in each of the above-mentioned specific examples can be appropriately changed as long as there is no technical contradiction.

Claims (10)

1. A heat exchanger (10) that exchanges heat between the intake air introduced into an internal combustion engine or a fuel cell and the cooling water of two systems of the first cooling water and the second cooling water.
   A plurality of flow path forming plate members (210) having a first flow path (W11) through which the first cooling water flows and a second flow path (W12) through which the second cooling water flows are stacked and arranged. Heat exchange is performed between the first cooling water and the second cooling water flowing inside the flow path forming plate member and the intake air flowing outside the flow path forming plate member. The heat exchange unit (20) to be performed and
   A first inflow pipe (24a) for allowing the first cooling water to flow into the heat exchange unit,
   A first outflow pipe (24b) that allows the first cooling water to flow out from the heat exchange unit, and
   A second inflow pipe (25a) for allowing the second cooling water to flow into the heat exchange section,
   A second outflow pipe (25b) for draining the second cooling water from the heat exchange unit is provided.
   The direction in which the plurality of flow path forming plate members are stacked and arranged is the plate stacking direction, the direction in which the intake air flows through the heat exchange portion is the intake flow direction, and the direction is orthogonal to both the plate stacking direction and the intake flow direction. When the direction to do is the predetermined direction
   One of the first inflow pipe and the first outflow pipe, the second inflow pipe, and the second outflow pipe are provided at one end of the heat exchange portion in the predetermined direction. Be,
   At the other end of the heat exchange portion in the predetermined direction, the first pipe of the other of the first inflow pipe and the first outflow pipe is provided.
   Two of the one first pipe, the second inflow pipe, and the second outflow pipe are provided on one outer surface in the plate stacking direction at one end of the heat exchange portion.
   The other outer surface in the plate stacking direction at one end of the heat exchange portion is provided with the one first pipe, the second inflow pipe, and the remaining one of the second outflow pipes. Exchanger.
2. A guide unit (30, 31) that guides the introduction of intake air into the heat exchange unit or guides the air that has passed through the heat exchange unit.
   An assembling member (22, 23) that is joined to the heat exchange portion and to which the guide portion is assembled is further provided.
   The heat exchanger according to claim 1, wherein the assembling member is joined to the heat exchange portion by brazing.
3. The heat exchanger according to claim 1 or 2, further comprising a duct case (60) provided so as to surround the outer periphery of the core portion.
4. The duct case is composed of a plurality of duct plate members (61, 62).
   The heat exchanger according to claim 3, wherein at least one of the plurality of duct plate members is formed with a bent portion that comes into surface contact with the assembled member.
5. The first inflow pipe, the first outflow pipe, the second inflow pipe, and the second outflow pipe are provided in the duct case.
   The heat exchange unit includes a first distribution tank space (T11) that distributes the first cooling water flowing into the first inflow pipe to the plurality of flow path forming plate members, and the plurality of flow path forming plate members. A plurality of said flow path forming plate members, the first collecting tank space (T12) that collects the passed first cooling water and guides it to the first outflow pipe, and the second cooling water that flows into the second inflow pipe. A second distribution tank space (T21) that distributes to the second distribution tank space (T22), and a second assembly tank space (T22) that collects the second cooling water that has passed through the plurality of flow path forming plate members and guides the second cooling water to the second outflow pipe. Have,
   One of the first inflow pipe, the first outflow pipe, the second inflow pipe, and the second outflow pipe is designated as a specific pipe.
   When the tank space corresponding to the specific pipe is defined as the specific tank space among the first distribution tank space, the first assembly tank space, the second distribution tank space, and the second assembly tank space.
   The specific pipe is provided at a position deviated from the specific tank space in the plate stacking direction.
   The heat exchanger according to claim 3 or 4, wherein the duct case is formed with a communication passage (613) that connects the specific pipe and the specific tank space.
6. The flow path forming plate member is composed of a first plate piece (210a) and a second plate piece (210b).
   The first flow path and the second flow path are formed between the first plate piece and the second plate piece.
   The heat exchanger according to any one of claims 1 to 5, further comprising a spacer (40, 41) arranged between the end of the first plate piece and the end of the second plate piece.
7. The heat exchanger according to claim 6, wherein the spacer is composed of a plurality of spacer pieces made of separate bodies.
8. The flow path forming plate member includes a first inflow portion (C11a, C11b) that allows the first cooling water to flow into the first flow path, and a first outflow that causes the first cooling water to flow out from the first flow path. Parts (C12a, C12b), a second inflow portion (C13a, C13b) that allows the second cooling water to flow into the second flow path, and a second outflow that causes the second cooling water to flow out from the second flow path. It has a part (C14a, C14b) and
   One of the first inflow portion and the first outflow portion, the second inflow portion, and the second outflow portion are formed at one end of the flow path forming plate member in the predetermined direction.
   At the other end of the flow path forming plate member in the predetermined direction, the other of the first inflow portion and the first outflow portion and the first inflow from the second inflow portion in the second flow path. 2 A turning portion (W122) for turning the flow direction of the cooling water toward the second outflow portion is formed.
   A cup portion (C15a, C16a, C15b, C16b) projecting in the plate stacking direction toward the adjacent flow path forming plate is provided in the portion of the flow path forming plate member where the turning portion is formed. The heat exchanger according to any one of claims 1 to 7.
9. The heat exchanger according to claim 8, wherein the second flow path formed in each of the plurality of flow path forming plate members communicates with each other through communication portions (T23, T24) formed in the cup portion.
10. In the portion of the flow path forming plate member where the turning portion is formed, the cup portion (C15a, C15b) arranged as the cup portion so as to face the second inflow portion in the predetermined direction is used. The heat exchanger according to claim 8 or 9, which is provided with cup portions (C16a, C16b) arranged so as to face the second outflow portion in the predetermined direction.

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