Heat exchanger

Abstract

To provide a heat exchanger that can be easily produced.SOLUTION: A heat exchanger is equipped with a header that has a header opening through which a heat medium flows in or discharges out, and a header channel in which the heat medium circulates, and three or more pipes disposed at intervals in an extending direction of the header channel, projects out into the header channel at one end and connected to the header so as to communicate with the header channel, and having the same pipe diameter. The three or more branch pipes are provided so that the flow resistance of the heat medium between each of the three or more branch pipes and the header channel gradually increases from the branch pipe apart from the header opening of the three or more branch pipes toward the branch pipe close to the header opening of the three or more branch pipes.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger. [Background technology]

[0002] There is a heat exchanger that includes a header provided on the inlet side and an outlet side of the heat medium, and a plurality of branch pipes provided in parallel between the inlet side header and the outlet side header. In such a heat exchanger, the flow rate of the heat medium flowing through the branch pipes that are connected to the headers at a position close to the header opening tends to be higher than that of the branch pipes that are connected to the headers at a position away from the header opening through which the heat medium flows in or out. In contrast, Patent Document 1 discloses a heat exchanger that includes a header into which a refrigerant flows in from one longitudinal direction, and a number of heat transfer tubes that are connected in sequence along the longitudinal direction of the header, in which the cross-sectional area of ​​the refrigerant passages in the multiple heat transfer tubes gradually increases from one longitudinal end side to the other longitudinal end side of the header so that the refrigerant flows approximately evenly within the multiple heat transfer tubes. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 3284904 Summary of the Invention [Problem to be solved by the invention]

[0004] However, in the heat exchanger described in Patent Document 1, in order to make the cross-sectional areas of the refrigerant passages of the heat transfer tubes connected to the header different, it is necessary to prepare multiple types of heat transfer tubes with different diameters. Also, in order to connect the heat transfer tubes to the header, it is necessary to form multiple types of holes with different diameters according to the diameters of the heat transfer tubes. When manufacturing the heat exchanger, it is necessary to assemble the multiple types of heat transfer tubes with different diameters in the correct positions so that the cross-sectional areas of the refrigerant passages in the multiple heat transfer tubes gradually increase from one end side to the other end side in the longitudinal direction of the header, which causes a problem that the manufacturing is time-consuming.

[0005] The present disclosure has been made to solve the above-mentioned problems, and has an object to provide a heat exchanger that is easy to manufacture. [Means for solving the problem]

[0006] In order to solve the above problems, the heat exchanger of the present disclosure comprises a header having a header opening through which a heat medium flows in or out, and a header flow path through which the heat medium flows, and three or more branch pipes having the same pipe diameter, arranged at intervals in the direction in which the header flow path extends, one end of which protrudes into the header flow path and is connected to the header so as to communicate with the header flow path, and the three or more branch pipes are arranged such that the flow resistance of the heat medium between each of the three or more branch pipes and the header flow path gradually increases from a branch pipe among the three or more branch pipes that is farther from the header opening to a branch pipe among the three or more branch pipes that is closer to the header opening. Effect of the Invention

[0007] According to the heat exchanger of the present disclosure, it is possible to provide a heat exchanger that is easy to manufacture. [Brief description of the drawings]

[0008] [Figure 1] FIG. 1 is a diagram showing a schematic configuration of a heat exchanger according to an embodiment of the present disclosure. [Diagram 2] 4 is a cross-sectional view showing a connection portion between a header and a plurality of branch pipes in the heat exchanger according to the first embodiment of the present disclosure. FIG. [Diagram 3] 11 is a cross-sectional view showing a joint between a header and a plurality of branch pipes according to a first modified example of the first embodiment of the present disclosure. FIG. [Figure 4] 13 is a cross-sectional view showing an arrangement of a plurality of branch pipes relative to a header according to a second modified example of the first embodiment of the present disclosure, as viewed from the extension direction of a flow path within the header. FIG. [Diagram 5] FIG. 5 is a cross-sectional view taken along the line II in FIG. [Figure 6]11 is a cross-sectional view showing a connection portion between a header and a plurality of branch pipes according to a second embodiment of the present disclosure. FIG. [Figure 7A] 7 is a diagram showing a connection portion between a header and a first branch pipe according to a second embodiment of the present disclosure, and is a cross-sectional view taken along line II-II in FIG. 6. [Figure 7B] 7 is a diagram showing a connection portion between a header and a second branch pipe according to a second embodiment of the present disclosure, and is a cross-sectional view taken along line III-III in FIG. 6. [Figure 7C] 7 is a diagram showing a connection portion between a header and a third branch pipe according to a second embodiment of the present disclosure, and is a cross-sectional view taken along line IV-IV in FIG. 6. [Figure 7D] 7 is a diagram showing a connection portion between a header and a fourth branch pipe according to a second embodiment of the present disclosure, and is a cross-sectional view taken along the line VV in FIG. 6. FIG. [Figure 8] 13 is a cross-sectional view showing a connection portion between a header and a plurality of branch pipes according to a modified example of the second embodiment of the disclosure. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] Hereinafter, a heat exchanger according to an embodiment of the present disclosure will be described with reference to FIGS.

[0010] First Embodiment (Heat exchanger configuration) As shown in FIG. 1, the heat exchanger 10A includes an inlet header 20A, an outlet header 20B, and a plurality of branch pipes . In the heat exchanger 10A, the heat medium flows from an inlet header 20A through a plurality of branch pipes 40 to an outlet header 20B. In this embodiment, the heat transfer medium is a liquid. In this embodiment, the heat medium is water. The heat medium is not limited to water, but may be an antifreeze liquid. The heat medium flowing through the heat exchanger 10A is heated or cooled.

[0011] For example, when the heat exchanger 10A in this embodiment is a gas cooler, heat exchange is performed between a heat medium (water) flowing through the multiple branch pipes 40 and a gas flowing outside the multiple branch pipes 40, so that the heat exchanger 10A cools the gas, while the heat medium flowing through the heat exchanger 10A is heated. For example, when the heat exchanger 10A in this embodiment is a gas heater, heat exchange is performed between a heat medium (water) flowing through the multiple branch pipes 40 and a gas flowing outside the multiple branch pipes 40, so that the heat exchanger 10A heats the gas, while the heat medium flowing through the heat exchanger 10A is cooled.

[0012] The heat medium flows into the inlet header 20A from the outside of the heat exchanger 10A through a supply pipe (not shown). The inlet side header 20A has a header body 21A and a curved pipe portion 22A. The header body 21A is made of a tube that extends linearly in one direction. One end of the curved pipe portion 22A is connected to one end of the header body 21A. The other end of the header body 21A is closed. The curved pipe portion 22A is curved, for example, in a U-shape. The other end of the curved pipe portion 22A is connected to a supply pipe. The other end of the curved pipe portion 22A is formed with a header opening 23A into which the heat medium flows from the supply piping.

[0013] The inlet side header 20A has a header flow path 24A, through which a heat medium flows, inside a header main body 21A and a curved pipe portion 22A. In the inlet header 20A, the heat medium supplied from an external supply pipe flows into the header flow path 24A from the header opening 23A. The heat medium that has flowed into the header flow passage 24A of the inlet header 20A branches into a plurality of branch pipes 40 and flows therethrough.

[0014] The heat transfer medium flows into the outlet header 20B via a plurality of branch pipes 40. The outlet header 20B discharges the heat medium to a discharge pipe (not shown) outside the heat exchanger 10A. The outlet side header 20B has a header body 21B and a curved pipe portion 22B. The header body 21B is made of a tube that extends linearly in one direction. One end of the curved pipe portion 22B is connected to one end of the header body 21B. The other end of the header body 21B is closed. The curved pipe portion 22B is curved, for example, in a U-shape. The other end of the curved pipe portion 22B is connected to a discharge pipe. The other end of the curved pipe portion 22B is formed with a header opening 23B through which the heat medium flows out to the discharge piping.

[0015] The outlet header 20B has a header flow path 24B, through which the heat medium flows, inside a header main body 21B and a curved pipe portion 22B. In the outlet header 20B, the heat medium that has passed through a plurality of branch pipes 40 flows into a header flow path 24B. The outlet header 20B discharges the heat medium that has flowed into the header flow passage 24B from a header opening 23B to an external discharge piping.

[0016] The branch pipes 40 are provided between the inlet header 20A and the outlet header 20B. The branch pipes 40 are arranged in parallel between the inlet header 20A and the outlet header 20B. The branch pipes 40 are arranged at intervals in the extension direction of the header flow path 24A of the header body 21A of the inlet side header 20A and the header flow path 24B of the header body 21B of the outlet side header 20B.

[0017] Three or more branch pipes 40 are provided. In this embodiment, for example, four branch pipes 40 are provided. The number of branch pipes 40 is not limited to four, but may be three, or five or more. In this embodiment, the multiple branch pipes 40 include a first branch pipe 40A, a second branch pipe 40B, a third branch pipe 40C, and a fourth branch pipe 40D. First branch pipe 40A, second branch pipe 40B, third branch pipe 40C, and fourth branch pipe 40D have the same pipe diameter.

[0018] Each of the multiple branch pipes 40 (first branch pipe 40A, second branch pipe 40B, third branch pipe 40C, fourth branch pipe 40D) is arranged at intervals in the direction in which the header flow paths 24A and 24B extend relative to the inlet side header 20A and the outlet side header 20B. Each of the multiple branch pipes 40 (first branch pipe 40A, second branch pipe 40B, third branch pipe 40C, fourth branch pipe 40D) has one end in its extension direction joined to the inlet header 20A by brazing, welding, or the like. Each of the multiple branch pipes 40 (first branch pipe 40A, second branch pipe 40B, third branch pipe 40C, fourth branch pipe 40D) has the other end in the extension direction joined to the outlet header 20B by brazing, welding, or the like.

[0019] The heat medium flows into the flow passages formed inside each of the branch pipes 40 from the header flow passage 24A of the inlet header 20A. The heat medium that has flowed into the flow passages formed inside each of the branch pipes 40 flows out into the header flow passage 24B of the outlet header 20B. In each of the branch pipes 40, heat exchange takes place between the heat medium flowing through the internal flow path and the gas flowing outside the branch pipe 40. In this embodiment, a gas pipe (not shown) through which gas flows is wound in a spiral shape around the outer circumferential surface of each of the branch pipes 40. In each of the branch pipes 40, heat exchange takes place between the heat medium flowing through the internal flow passage and the gas flowing through the gas pipe wrapped around the outer circumferential surface of the branch pipe 40. The gas does not have to flow through the gas pipe wrapped around the outer circumferential surface of the branch pipe 40. For example, the gas may flow through the space outside each branch pipe 40, come into contact with the outer circumferential surface of each branch pipe 40, and exchange heat with the heat medium flowing through each branch pipe 40.

[0020] The multiple (three or more) branch pipes 40 are arranged such that the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24A gradually increases from the branch pipe 40 farther away from the header opening 23A to the branch pipe 40 closer to the header opening 23A, with respect to the path along the header flow path 24A. Specifically, among the multiple branch pipes 40, with respect to the path along the header flow path 24A, the first branch pipe 40A that is closest to the header opening 23A has the longest protrusion length La1 into the header flow path 24A. Hereinafter, "close to the header opening 23A" simply means close to the header opening 23A with respect to the path along the header flow path 24A. Moreover, hereinafter, simply saying "away from the header opening 23A" means away from the header opening 23A with respect to the path along the header flow passage 24A.

[0021] As shown in FIG. 2, in this embodiment, each of the multiple branch pipes 40 (first branch pipe 40A, second branch pipe 40B, third branch pipe 40C, fourth branch pipe 40D) has one end 401a, 401b, 401c, 401d protruding into the header flow path 24A of the inlet side header 20A. Each of the ends 401a, 401b, 401c, and 401d protrudes into the header flow path 24A of the inlet side header 20A in the direction in which the first branch pipe 40A, the second branch pipe 40B, the third branch pipe 40C, and the fourth branch pipe 40D extend, i.e., along the radial direction of the header body 21A of the inlet side header 20A.

[0022] The multiple branch pipes 40 are provided such that the projection length La into the header flow passage 24A gradually increases from the branch pipe 40 farther from the header opening 23A toward the branch pipe 40 closer to the header opening 23A. Of the multiple branch pipes 40, the fourth branch pipe 40D, which is the furthest from the header opening 23A, has the shortest protruding length La4 into the header flow passage 24A. From the fourth branch pipe 40D, which is the furthest from the header opening 23A, toward the first branch pipe 40A, which is the closest to the header opening 23A, the protruding length La4 of the fourth branch pipe 40D, the protruding length La3 of the third branch pipe 40C, the protruding length La2 of the second branch pipe 40B, and the protruding length La1 of the first branch pipe 40A gradually increase (La4 <La3<La2<La1)。

[0023] Further, in each of the branch pipes 40, a gap Ga is formed between one end 401a to 401d and the inner circumferential surface of the header body 21A that faces the one end 401a to 401d with a gap therebetween. The heat exchanger 10A has a gap Ga4 between one end 401d of the fourth branch pipe 40D and the inner circumferential surface of the header body 21A. The heat exchanger 10A has a gap Ga3 between one end 401c of the third branch pipe 40C and the inner circumferential surface of the header body 21A. In the heat exchanger 10A, a gap Ga2 is provided between one end 401b of the second branch pipe 40B and the inner circumferential surface of the header body 21A. In the heat exchanger 10A, a gap Ga1 is provided between one end 401a of the first branch pipe 40A and the inner circumferential surface of the header body 21A. This gap Ga becomes gradually smaller from the fourth branch pipe 40D, which is the farthest from the header opening 23A, toward the first branch pipe 40A, which is the closest to the header opening 23A. That is, the gaps Ga4, Ga3, Ga2, and Ga1 become gradually smaller from the fourth branch pipe 40D, which is the farthest from the header opening 23A, toward the first branch pipe 40A, which is the closest to the header opening 23A.

[0024] Each of the branch pipes 40 has an opening 42A that faces the direction in which the branch pipe 40 extends and communicates with the header flow passage 24A. In each of the branch pipes 40, the heat medium flows between each of the branch pipes 40 and the header flow path 24A through the opening 42A. In each of the branch pipes 40, the heat medium flowing through the header flow passage 24A flows into the branch pipe 40 through the opening 42A.

[0025] At this time, the branch pipe 40 closer to the header opening 23A has a greater protruding length La of the branch pipe 40 into the header flow path 24A and a smaller gap Ga, so that the heat medium flowing through the header flow path 24A is less likely to flow into the branch pipe 40 through the opening 42A. Specifically, among the multiple branch pipes 40, one end 401a of the first branch pipe 40A has the longest protruding length La and the smallest gap Ga. That is, the first branch pipe 40A has a structure in which the heat medium is less likely to flow in from the header flow path 24A than the other branch pipes 40. As a result, of the flow resistances of the heat medium between the multiple branch pipes 40 and the header flow path 24A, the flow resistance of the heat medium between the first branch pipe 40A and the header flow path 24A is the largest. On the other hand, among the multiple branch pipes 40, one end 401d of the fourth branch pipe 40D has the smallest protruding length La and the largest gap Ga. That is, the fourth branch pipe 40D has a structure that makes it easier for the heat medium to flow from the header flow path 24A into the fourth branch pipe 40D compared to the other branch pipes 40. As a result, of the flow resistances of the heat medium between the multiple branch pipes 40 and the header flow path 24A, the flow resistance of the heat medium between the fourth branch pipe 40D and the header flow path 24A is the smallest. Furthermore, from one end 401d of the fourth branch pipe 40D, which has the shortest protruding length La4, to one end 401a of the first branch pipe 40A, which has the longest protruding length La1, the flow resistance of the heat medium in the header flow path 24A gradually increases in the order of one end 401d of the fourth branch pipe 40D, one end 401c of the third branch pipe 40C, one end 401b of the second branch pipe 40B, and one end 401a of the first branch pipe 40A. For this reason, the branch pipe 40 located farther from the header opening 23A has a smaller protruding length La of the branch pipe 40 into the header flow path 24A, so that the flow resistance is smaller, and the gap Ga is larger, so that the heat transfer medium flowing through the header flow path 24A is more likely to flow into the branch pipe 40 through the opening 42A.

[0026] In this manner, by making the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24A different among the multiple branch pipes 40, the flow rate of the liquid medium can be made uniform. This improves the heat exchange efficiency in the heat exchanger 10A. Also, the improved heat exchange efficiency in the heat exchanger 10A allows the heat exchanger 10A to be made smaller and less costly. Furthermore, compared to a case where the flow rate of the heat medium in the branch pipes is higher closer to the header opening, which makes the branch pipes more susceptible to corrosion, the heat exchanger 10A can reduce the flow rate of the heat medium in the branch pipes 40 closer to the header opening 23A by making the flow rate of the liquid medium uniform among the multiple branch pipes 40. As a result, corrosion of the branch pipes 40 in the heat exchanger 10A is suppressed.

[0027] (Action and Effects) According to this embodiment, in the heat exchanger 10A, the three or more branch pipes 40 connected to the inlet side header 20A at intervals in the direction in which the header flow path 24A extends are such that the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24A gradually decreases from the branch pipe 40 farthest from the header opening 23A to the branch pipe 40 closest to the header opening 23A. As a result, the flow resistance of the heat medium between the branch pipe 40 and the header flow path 24A is greater for the branch pipe 40 closer to the header opening 23A than for the branch pipe 40 farther from the header opening 23A, making it more difficult for the heat medium to flow from the header flow path 24A into the branch pipe 40. Conversely, the flow resistance of the heat medium between the branch pipe 40 and the header flow path 24A is smaller in the branch pipe 40 that is farther away from the header opening 23A than in the branch pipe 40 that is closer to the header opening 23A, and therefore, the heat medium is more likely to flow from the header flow path 24A into the branch pipe 40. In this manner, the flow rate of the heat medium among the plurality of branch pipes 40 can be made uniform. In this case, since the three or more branch pipes 40 have the same pipe diameter, it is not necessary to prepare a plurality of types of branch pipes 40, and it is sufficient to connect a plurality of branch pipes 40 of the same type to the inlet header 20A. As a result, it is possible to provide a heat exchanger 10A that is easy to manufacture.

[0028] According to one example of this embodiment, three or more branch pipes 40 are provided such that the projection length La into the header flow path 24A gradually increases from the branch pipe 40 farthest from the header opening 23A to the branch pipe 40 closer to the header opening 23A. The greater the projection length La of the branch pipe 40 into the header flow path 24A, the smaller the gap Ga becomes, and the greater the flow resistance of the heat medium becomes. In this way, by providing three or more branch pipes 40, the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24A can be gradually increased from the branch pipe 40 farther away from the header opening 23A to the branch pipe 40 closer to the header opening 23A.

[0029] According to one example of the present embodiment, by adjusting the protrusion length La into the header flow path 24A, the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24A can be gradually increased from the branch pipe 40 away from the header opening 23A to the branch pipe 40 closer to the header opening 23A. Therefore, it is possible to provide the heat exchanger 10A that is easy to manufacture.

[0030] According to one example of this embodiment, in each of the three or more branch pipes 40, the heat medium flows between each branch pipe 40 and the header flow path 24A through the opening 42A facing in the direction in which the branch pipe 40 extends. With this configuration, the greater the protruding length La of the branch pipe 40 into the header flow path 24A, the smaller the distance between the opening 42A and the inner surface of the header body 21A over the entire opening 42A, making it more difficult for the heat medium to flow over the entire opening 42A. Therefore, the flow resistance of the heat refrigerant can be easily adjusted by changing the protrusion length La.

[0031] According to one example of the present embodiment, the heat medium is a liquid. In this case, the flow resistance of the heat medium between each branch pipe 40 and the header flow path 24A gradually decreases from the branch pipe 40 farther from the header opening 23A toward the branch pipe 40 closer to the header opening 23A, so that the flow rate of the heat medium can be more effectively uniformed among the multiple branch pipes 40.

[0032] (First Modification of the First Embodiment) In the first embodiment, the branch pipes 40 are arranged so that the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24A of the inlet header 20A gradually increases from the branch pipe 40 farther from the header opening 23A toward the branch pipe 40 closer to the header opening 23A. In contrast, as a first modified example, as shown in Fig. 3, the branch pipes 40 of the heat exchanger 10B may be arranged so that the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24B of the outlet header 20B gradually increases along the path of the header flow path 24B from the branch pipe 40 farther from the header opening 23B toward the branch pipe 40 closer to the header opening 23B. Hereinafter, "close to the header opening 23B" simply means close to the header opening 23B with respect to a path along the header flow path 24B. Moreover, hereinafter, simply saying "away from the header opening 23B" means away from the header opening 23B with respect to a path along the header flow passage 24B.

[0033] In this first modified example, each of the multiple branch pipes 40 (first branch pipe 40A, second branch pipe 40B, third branch pipe 40C, fourth branch pipe 40D) has its other end (one end) 402a, 402b, 402c, 402d protruding into the header flow path 24B of the outlet side header 20B. Each of the other ends 402a, 402b, 402c, and 402d protrudes into the header flow path 24B of the outlet side header 20B in the direction in which the first branch pipe 40A, the second branch pipe 40B, the third branch pipe 40C, and the fourth branch pipe 40D extend, i.e., along the radial direction of the header body 21B of the outlet side header 20B.

[0034] In this first modified example, the multiple branch pipes 40 are arranged so that the protruding length Lb into the header flow path 24B gradually increases from the branch pipe 40 away from the header opening 23B to the branch pipe 40 closer to the header opening 23B. From the fourth branch pipe 40D, which is the furthest from the header opening 23B, toward the first branch pipe 40A, which is the closest to the header opening 23B, the protruding length Lb4 of the fourth branch pipe 40D, the protruding length Lb3 of the third branch pipe 40C, the protruding length Lb2 of the second branch pipe 40B, and the protruding length Lb1 of the first branch pipe 40A gradually increase (Lb4 <Lb3<Lb2<Lb1)。

[0035] According to the configuration of the first modified example, similarly to the first embodiment described above, the flow resistance of the heat medium between the branch pipe 40 and the header flow path 24B is greater for the branch pipe 40 closer to the header opening 23B than for the branch pipe 40 farther from the header opening 23B, so that the heat medium is less likely to flow out from the branch pipe 40 to the header flow path 24B. Conversely, the flow resistance of the heat medium between the branch pipe 40 and the header flow path 24B is smaller for the branch pipe 40 farther from the header opening 23B than for the branch pipe 40 closer to the header opening 23B, so that the heat medium is more likely to flow out from the branch pipe 40 to the header flow path 24B. In this way, the flow rate of the heat medium can be made uniform among the multiple branch pipes 40. In this case, since the three or more branch pipes 40 have the same pipe diameter, it is not necessary to prepare a plurality of types of branch pipes 40, and it is sufficient to connect a plurality of branch pipes 40 of the same type to the inlet header 20A. As a result, it is possible to provide a heat exchanger 10A that is easy to manufacture.

[0036] (Second Modification of the First Embodiment) As shown in Figures 4 and 5, as a second modified example, in a heat exchanger 10C, multiple branch pipes 40 may be connected to the inlet side header 20A from different directions in the circumferential direction Dc about an axis along the extension direction of the header flow path 24A. As shown in Figure 4, in this second modified example, the first branch pipe 40A, the second branch pipe 40B, the third branch pipe 40C, and the fourth branch pipe 40D are connected to each other from different directions in the circumferential direction Dc of the inlet side header 20A when viewed from the direction in which the header flow path 24A extends. The first branch pipe 40A, the second branch pipe 40B, the third branch pipe 40C, and the fourth branch pipe 40D are connected from directions different by 90° in the circumferential direction Dc of the inlet header 20A when viewed from the direction in which the header flow passage 24A extends. In this second modified example, the second branch pipe 40B is connected to the first branch pipe 40A from a direction shifted by 90° to one side in the circumferential direction Dc of the inlet header 20A. The third branch pipe 40C is connected to the second branch pipe 40B from a direction shifted by 90° to one side in the circumferential direction Dc of the inlet header 20A. The fourth branch pipe 40D is connected to the third branch pipe 40C from a direction shifted by 90° to one side in the circumferential direction Dc of the inlet header 20A.

[0037] According to the configuration of the second modified example, the multiple branch pipes 40 are connected to the inlet header 20A from different directions in the circumferential direction Dc around the axis of the header flow passage 24A, so that the influence of the branch pipe 40 located upstream in the flow direction of the heat medium in the header flow passage 24A on the flow resistance can be suppressed from extending to other branch pipes 40 located downstream in the flow direction. This makes it possible to more effectively equalize the flow rate of the heat medium among the multiple branch pipes 40.

[0038] Second Embodiment (Heat exchanger configuration) As shown in FIG. 1, the heat exchanger 10D includes an inlet header 20A, an outlet header 20B, and a plurality of branch pipes . Three or more branch pipes 40 are provided. In this embodiment, for example, four branch pipes 40 are provided. In this embodiment, the multiple branch pipes 40 include a first branch pipe 40P, a second branch pipe 40Q, a third branch pipe 40R, and a fourth branch pipe 40S. The first branch pipe 40P, the second branch pipe 40Q, the third branch pipe 40R, and the fourth branch pipe 40S have the same pipe diameter.

[0039] Each of the multiple branch pipes 40 (first branch pipe 40P, second branch pipe 40Q, third branch pipe 40R, fourth branch pipe 40S) is arranged at intervals in the direction in which the header flow paths 24A and 24B extend relative to the inlet side header 20A and the outlet side header 20B. Each of the multiple branch pipes 40 (first branch pipe 40P, second branch pipe 40Q, third branch pipe 40R, fourth branch pipe 40S) has one end in its extension direction joined to the inlet header 20A by brazing, welding, or the like. Each of the multiple branch pipes 40 (first branch pipe 40P, second branch pipe 40Q, third branch pipe 40R, fourth branch pipe 40S) has the other end in the extension direction joined to the outlet header 20B by brazing, welding, or the like.

[0040] The multiple (three or more) branch pipes 40 are arranged so that the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24A gradually increases from the branch pipe 40 farther away from the header opening 23A to the branch pipe 40 closer to the header opening 23A. As shown in FIG. 6, each of the branch pipes 40 has an opening 45A that faces the direction in which the branch pipe 40 extends and communicates with the header flow passage 24A. In this embodiment, multiple (three or more) branch pipes 40 are arranged such that the area of ​​the opening 45A communicating with the header flow path 24A of the branch pipe 40 gradually decreases from the branch pipe 40 farther away from the header opening 23A to the branch pipe 40 closer to the header opening 23A.

[0041] Each of the branch pipes 40 has an inclined surface 47A at the tip of the branch pipe 40 protruding into the header flow path 24A. The inclined surface 47A is inclined with respect to the direction in which the branch pipe 40 extends. In this embodiment, the inclined surface 47A is inclined away from the header opening 23A as it protrudes into the header flow path 24A. The multiple branch pipes 40 are arranged so that the inclination angle θa of the inclined surface 47A relative to the direction in which each branch pipe 40 extends gradually increases from the branch pipe 40 farther away from the header opening 23A toward the branch pipe 40 closer to the header opening 23A. Of the inclined surfaces 47A of the multiple branch pipes 40, the inclined surface 47A of the fourth branch pipe 40S has an inclination angle θa4 with respect to the direction in which the fourth branch pipe 40S extends. Of the inclined surfaces 47A of the multiple branch pipes 40, the inclined surface 47A of the third branch pipe 40R has an inclination angle θa3 with respect to the direction in which the third branch pipe 40R extends. Of the inclined surfaces 47A of the multiple branch pipes 40, the inclined surface 47A of the second branch pipe 40Q has an inclination angle θa2 with respect to the direction in which the second branch pipe 40Q extends. Of the inclined surfaces 47A of the multiple branch pipes 40, the inclined surface 47A of the first branch pipe 40P has an inclination angle θa1 with respect to the direction in which the first branch pipe 40P extends.

[0042] Specifically, among the multiple branch pipes 40, the inclination angle θa1 of the inclined surface 47A of the first branch pipe 40P that is closest to the header opening 23A is the largest. Of the multiple branch pipes 40, the inclination angle θa4 of the inclined surface 47A of the fourth branch pipe 40S, which is the farthest from the header opening 23A, is the smallest. The inclination angles θa4, θa3, θa2, and θa1 gradually increase from the fourth branch pipe 40S, which is the farthest from the header opening 23A, to the first branch pipe 40P, which is the closest to the header opening 23A (θa4<θa3<θa2<θa1).

[0043] As shown in FIGS. 7A to 7D, in each of the branch pipes 40, an opening 45A is formed in an inclined surface 47A. In each of the branch pipes 40, the opening 45A opens into the inclined surface 47A, and thus has an elliptical shape when viewed from the direction in which the header flow path 24A extends. The multiple branch pipes 40 are provided such that the opening dimension Xa in the major axis direction of the opening 45A gradually decreases from the branch pipe 40 farthest from the header opening 23A toward the branch pipe 40 closer to the header opening 23A. Among the openings 45A of the multiple branch pipes 40, the opening 45A of the fourth branch pipe 40S has an opening dimension Xa4. Among the openings 45A of the multiple branch pipes 40, the opening 45A of the third branch pipe 40R has an opening dimension Xa3. Among the openings 45A of the multiple branch pipes 40, the opening 45A of the second branch pipe 40Q has an opening dimension Xa2. Among the openings 45A of the multiple branch pipes 40, the opening 45A of the first branch pipe 40P has an opening dimension Xa1. From the fourth branch pipe 40S, which is the farthest from the header opening 23A, to the first branch pipe 40P, which is the closest to the header opening 23A, the opening dimensions Xa4, Xa3, Xa2, and Xa1 gradually become smaller (Xa4>Xa3>Xa2>Xa1).

[0044] In this embodiment, the area of ​​the opening 45A communicating with the header flow path 24A of the branch pipes 40 gradually decreases from the branch pipe 40 farthest from the header opening 23A to the branch pipe 40 closest to the header opening 23A, so that the flow resistance of the heat medium between each branch pipe 40 and the header flow path 24A increases with the branch pipe 40 being closer to the header opening 23A. In this manner, the flow rate of the liquid medium is made uniform among the plurality of branch pipes 40. This improves the heat exchange efficiency in the heat exchanger 10D. Furthermore, the heat exchange efficiency in the heat exchanger 10D is improved, which allows the heat exchanger 10D to be made more compact and less expensive. By making the flow rate of the liquid medium uniform among the plurality of branch pipes 40, the flow rate of the heat medium in the branch pipe 40 close to the header opening 23A can be reduced, and as a result, corrosion of the branch pipe 40 can also be suppressed.

[0045] (Action and Effects) According to this embodiment, in the heat exchanger 10D, the three or more branch pipes 40 connected to the inlet side header 20A at intervals in the direction in which the header flow path 24A extends are such that the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24A gradually decreases from the branch pipe 40 farthest from the header opening 23A to the branch pipe 40 closest to the header opening 23A. As a result, the flow resistance of the heat medium between the branch pipe 40 and the header flow path 24A is greater for the branch pipe 40 closer to the header opening 23A than for the branch pipe 40 farther from the header opening 23A, making it more difficult for the heat medium to flow from the header flow path 24A into the branch pipe 40. Conversely, the flow resistance of the heat medium between the branch pipe 40 and the header flow path 24A is smaller in the branch pipe 40 that is farther away from the header opening 23A than in the branch pipe 40 that is closer to the header opening 23A, and therefore, the heat medium is more likely to flow from the header flow path 24A into the branch pipe 40. In this manner, the flow rate of the heat medium among the plurality of branch pipes 40 can be made uniform. In this case, since the three or more branch pipes 40 have the same pipe diameter, it is not necessary to prepare a plurality of types of branch pipes 40, and it is sufficient to connect a plurality of branch pipes 40 of the same type to the inlet header 20A. As a result, it is possible to provide a heat exchanger 10D that is easy to manufacture.

[0046] Furthermore, according to one example of this embodiment, the area of ​​the opening 45A communicating with the header flow path 24A of the branch pipe 40 gradually decreases from the branch pipe 40 farthest from the header opening 23A to the branch pipe 40 closer to the header opening 23A, so that the flow resistance of the heat medium between each branch pipe 40 and the header flow path 24A increases with the branch pipe 40 being closer to the header opening 23A. Therefore, by arranging the multiple branch pipes 40 so that the area of ​​the opening 45A gradually decreases from the branch pipe 40 farthest from the header opening 23A to the branch pipe 40 closer to the header opening 23A, the flow resistance of the heat medium between each branch pipe 40 and the header flow path 24A can be gradually increased from the branch pipe 40 farthest from the header opening 23A to the branch pipe 40 closer to the header opening 23A.

[0047] Furthermore, according to one example of this embodiment, by adjusting the area of ​​the opening 45A communicating with the header flow path 24A, the flow resistance of the heat medium between each of the branch pipes 40 and the header flow path 24A can be gradually increased from the branch pipe 40 away from the header opening 23A toward the branch pipe 40 closer to the header opening 23A. Therefore, it is possible to provide the heat exchanger 10D that is easy to manufacture.

[0048] Furthermore, according to this example of the present embodiment, the inclination angle θa of the inclined surface 47A at the tip of the branch pipe 40 gradually increases from the branch pipe 40 farther away from the header opening 23A toward the branch pipe 40 closer to the header opening 23A. As a result, in multiple branch pipes 40 having the same pipe diameter, the area of ​​the opening 45A communicating with the header flow path 24A of the branch pipe 40 can be gradually reduced from the branch pipe 40 farthest from the header opening 23A to the branch pipe 40 closer to the header opening 23A. In this way, by using branch pipes 40 having the same internal pipe system while varying the inclination angle θa of the inclined surface 47A, a heat exchanger 10D can be provided in which the area of ​​the opening 45A communicating with the header flow path 24A of the branch pipe 40 is gradually reduced from the branch pipe 40 away from the header opening 23A to the branch pipe 40 closer to the header opening 23A.

[0049] (Modification of the second embodiment) In the second embodiment, the areas of the openings 45A in the header flow passage 24A of the inlet side header 20A are made different in the multiple branch pipes 40. In this case, the branch pipes 40 are arranged so that the flow resistance of the heat medium between each of the branch pipes 40 and the header flow passage 24A of the inlet side header 20A gradually increases from the branch pipe 40 farther away from the header opening 23A toward the branch pipe 40 closer to the header opening 23A. In contrast to this, as a modified example, the areas of the openings 45B in the header flow passage 24B of the outlet header 20B may be made different in the multiple branch pipes 40 of the heat exchanger 10E as shown in Fig. 8. In this case, the flow resistance of the heat medium between each of the branch pipes 40 and the header flow passage 24B of the outlet header 20B may be gradually increased from the branch pipe 40 farther away from the header opening 23B toward the branch pipe 40 closer to the header opening 23B.

[0050] In this modification, each of the multiple branch pipes 40 has an inclined surface 47B at the tip of the branch pipe 40 that protrudes into the header flow path 24B. The inclined surface 47B is inclined with respect to the direction in which the branch pipe 40 extends. In this modification, the inclined surface 47B is inclined away from the header opening 23B as it protrudes into the header flow path 24B. The multiple (three or more) branch pipes 40 are arranged so that the inclination angle θb of the inclined surface 47B relative to the extension direction of each branch pipe 40 gradually increases from the branch pipe 40 farther away from the header opening 23B toward the branch pipe 40 closer to the header opening 23B.

[0051] In this modification, in each of the multiple branch pipes 40, the opening 45B is formed in the inclined surface 47B. The multiple branch pipes 40 are provided such that the opening dimension in the major axis direction of the opening 45B gradually decreases from the branch pipe 40 farthest from the header opening 23B toward the branch pipe 40 closer to the header opening 23B.

[0052] In this modified example, the area of ​​the opening 45B communicating with the header flow path 24B of the branch pipes 40 gradually decreases from the branch pipe 40 farthest from the header opening 23B to the branch pipe 40 closest to the header opening 23B, so that the flow resistance of the heat medium between each branch pipe 40 and the header flow path 24B increases with the branch pipe 40 being closer to the header opening 23B.

[0053] According to the configuration of this modified example, the flow rate of the heat medium can be made uniform among the plurality of branch pipes 40, similarly to the second embodiment. In this case, since the three or more branch pipes 40 have the same pipe diameter, it is not necessary to prepare a plurality of types of branch pipes 40, and it is sufficient to connect a plurality of branch pipes 40 of the same type to the outlet header 20B. As a result, it is possible to provide the heat exchanger 10E that is easy to manufacture.

[0054] (Other Modifications of the Embodiments) In the above first embodiment, among the protruding lengths La, Lb of the multiple branch pipes 40, the protruding lengths La, Lb of the first branch pipe 40A are the longest, but the heat exchangers 10A, 10B may be configured in any manner as long as the gap between the first branch pipe 40A, which is closest to the header openings 23A, 23B, and the inner surface of the header body 21A, 21B is the smallest among the gaps between the multiple branch pipes 40 and the inner surfaces of the header bodies 21A, 21B. As a modified example, in the heat exchanger 10A, the projection length La of the first branch pipe 40A closest to the header opening 23A may be 0, that is, the first branch pipe 40A may not project into the header flow path 24A. As another modified example, in the heat exchanger 10B, the projection length Lb of the first branch pipe 40A closest to the header opening 23B may be 0, that is, the first branch pipe 40A may not project into the header flow path 24B.

[0055] In the second embodiment described above, the inclined surfaces 47A, 47B and the openings 45A, 45B face the header openings 23A, 23B with respect to the paths along the header flow paths 24A, 24B, but this is not limiting. As a modified example, the inclined surface 47A and the opening 45A may face in a direction different from the header opening 23A side with respect to the path along the header flow path 24A, for example, facing away from the header opening 23A with respect to the path along the header flow path 24A. As another modified example, the inclined surface 47B and the opening 45B may face in a direction different from the header opening 23B side with respect to the path along the header flow path 24B, for example, toward the side away from the header opening 23B with respect to the path along the header flow path 24B.

[0056] In the above second embodiment, among the inclination angles θa, θb of the multiple branch pipes 40, the inclination angles θa, θb of the first branch pipe 40P are the largest, but the inclination angles θa, θb may be any angle as long as the area of ​​the openings 45A, 45B of the first branch pipe 40P closest to the header openings 23A, 23B is the smallest among the areas of the openings 45A, 45B of the multiple branch pipes 40. As a modified example, the inclination angle θa of the inclined surface 47A of the first branch pipe 40P may be 90°. That is, the inclined surface 47A of the first branch pipe 40P may be perpendicular to the extension direction of the branch pipe 40. In this case, the opening 45A of the first branch pipe 40P is a perfect circle. As another modification, the inclination angle θb of the inclined surface 47B of the first branch pipe 40P may be 90°. That is, the inclined surface 47B of the first branch pipe 40P may be perpendicular to the extension direction of the branch pipe 40. In this case, the opening 45B of the first branch pipe 40P is a perfect circle.

[0057] As a further modification, it is also possible to appropriately combine the configurations shown in the first embodiment and the modifications thereof with the configurations shown in the second embodiment and the modifications thereof.

[0058] Although some embodiments of the present disclosure have been described above, these embodiments are presented as examples and are not intended to limit the scope of the disclosure. These embodiments can be implemented in various other forms, and various omissions, substitutions, and modifications can be made without departing from the gist of the disclosure. These embodiments and their modifications are included in the scope of the present disclosure and its equivalents, as well as in the scope and gist of the disclosure.

[0059] <Additional Notes> The heat exchangers 10A to 10E described in each embodiment can be understood, for example, as follows.

[0060] (1) Heat exchangers 10A to 10E according to a first aspect include headers 20A, 20B having header openings 23A, 23B through which a heat medium flows in or out, and header flow paths 24A, 24B through which the heat medium flows, and three or more branch pipes 40 having the same pipe diameter, which are arranged at intervals in a direction in which the header flow paths 24A, 24B extend and are connected to the headers 20A, 20B so that one ends protrude into the header flow paths 24A, 24B and communicate with the header flow paths 24A, 24B, and the three or more branch pipes 40 are arranged such that the flow resistance of the heat medium between each of the three or more branch pipes 40 and the header flow paths 24A, 24B gradually increases from a branch pipe 40 that is farther from the header openings 23A, 23B among the three or more branch pipes 40 toward a branch pipe 40 that is closer to the header openings 23A, 23B among the three or more branch pipes 40.

[0061] According to this embodiment, in heat exchangers 10A to 10E, three or more branch pipes 40 are connected to headers 20A, 20B at intervals in the direction in which header flow paths 24A, 24B extend, and the flow resistance of the heat medium between each of the branch pipes 40 and the header flow paths 24A, 24B gradually decreases from the branch pipe 40 away from the header openings 23A, 23B to the branch pipe 40 closer to the header openings 23A, 23B. As a result, the flow resistance of the heat medium between the branch pipe 40 and the header flow paths 24A, 24B is greater for branch pipes 40 closer to header openings 23A, 23B than for branch pipes 40 farther from header openings 23A, 23B, so that it is more difficult for the heat medium to flow from the header flow paths 24A, 24B into the branch pipes 40 or more difficult for the heat medium to flow out from the branch pipes 40 to the header flow paths 24A, 24B. Conversely, the flow resistance of the heat medium between the branch pipe 40 and the header flow paths 24A, 24B is smaller for branch pipes 40 farther from the header openings 23A, 23B than for branch pipes 40 closer to the header openings 23A, 23B, and therefore the heat medium more easily flows from the header flow paths 24A, 24B into the branch pipe 40 or more easily flows out from the branch pipe 40 to the header flow paths 24A, 24B. In this way, the flow rate of the heat medium can be made uniform among the multiple branch pipes 40. In this case, since the three or more branch pipes 40 have the same pipe diameter, it is not necessary to prepare a plurality of types of branch pipes 40, and it is sufficient to connect a plurality of branch pipes 40 of the same type to the headers 20A, 20B. As a result, it is possible to provide the heat exchangers 10A to 10E that are easy to manufacture.

[0062] (2) Heat exchangers 10A to 10C according to a second aspect are the heat exchangers 10A to 10C of (1), wherein the three or more branch pipes 40 are arranged such that the protruding lengths La, Lb into the header flow paths 24A, 24B gradually increase from the branch pipe 40 away from the header openings 23A, 23B toward the branch pipe 40 closer to the header openings 23A, 23B.

[0063] According to this embodiment, by adjusting the protrusion lengths La, Lb into the header flow paths 24A, 24B, the flow resistance of the heat medium between each of the branch pipes 40 and the header flow paths 24A, 24B can be gradually increased from the branch pipe 40 away from the header openings 23A, 23B toward the branch pipe 40 closer to the header openings 23A, 23B. For this reason, it is possible to provide the heat exchangers 10A to 10C that are easy to manufacture.

[0064] (3) Heat exchangers 10A to 10C according to a third aspect are heat exchangers 10A to 10C according to (2), wherein each of the three or more branch pipes 40 has openings 42A, 42B that face in the direction in which the branch pipe 40 extends and communicate with the header flow paths 24A, 24B.

[0065] According to this embodiment, in each of the three or more branch pipes 40, the heat medium flows between each of the branch pipes 40 and the header channels 24A, 24B through the openings 42A, 42B facing in the direction in which the branch pipe 40 extends. As a result, the greater the protruding lengths La, Lb of the branch pipes 40 into the header flow paths 24A, 24B, the smaller the distance between the openings 42A, 42B and the inner surfaces of the header bodies 21A, 21B throughout the entire openings 42, 42B, making it more difficult for the heat medium to flow throughout the entire openings 42A, 42B. This makes it easier to adjust the flow resistance of the heat refrigerant by adjusting the protrusion lengths La and Lb.

[0066] (4) A heat exchanger 10D, 10E according to a fourth aspect is any one of the heat exchangers 10D, 10E of (1) to (3), in which the three or more branch pipes 40 are arranged such that the area of ​​the openings 45A, 45B communicating with the header flow paths 24A, 24B of the branch pipes 40 gradually decreases from the branch pipe 40 away from the header openings 23A, 23B to the branch pipe 40 closer to the header openings 23A, 23B.

[0067] According to this embodiment, by adjusting the area of ​​the openings 45A, 45B communicating with the header flow paths 24A, 24B, the flow resistance of the heat medium between each of the branch pipes 40 and the header flow paths 24A, 24B can be gradually increased from the branch pipe 40 away from the header openings 23A, 23B toward the branch pipe 40 closer to the header openings 23A, 23B. Therefore, it is possible to provide the heat exchangers 10D and 10E that are easy to manufacture.

[0068] (5) A fifth aspect of the heat exchanger 10D, 10E is the heat exchanger 10D, 10E of (4), wherein the three or more branch pipes 40 are arranged such that the opening dimension Xa in the longitudinal direction of the openings 45A, 45B gradually decreases from the branch pipe 40 away from the header openings 23A, 23B to the branch pipe 40 closer to the header openings 23A, 23B.

[0069] According to this embodiment, the areas of the openings 45A, 45B communicating with the header channels 24A, 24B can be adjusted by the opening dimension Xa in the major axis direction. Therefore, it is possible to provide the heat exchangers 10D and 10E that are easy to manufacture.

[0070] (6) A heat exchanger 10D, 10E according to a sixth aspect is the heat exchanger 10D, 10E according to (4) or (5), wherein the three or more branch pipes 40 each have an opening 45A, 45B formed on an inclined surface that is inclined with respect to the extension direction of the branch pipe 40 at the tip of the branch pipe 40 protruding into the header flow paths 24A, 24B, and the three or more branch pipes 40 are arranged such that the inclination angle of the inclined surface with respect to the extension direction of each branch pipe 40 gradually increases from the branch pipe 40 away from the header openings 23A, 23B toward the branch pipe 40 closer to the header openings 23A, 23B.

[0071] According to this embodiment, the inclination angle of the inclined surface at the tip of branch pipe 40 gradually increases from branch pipe 40 farther from header openings 23A, 23B toward branch pipe 40 closer to header openings 23A, 23B. As a result, in three or more branch pipes 40 having the same pipe diameter, the area of ​​the openings 45A, 45B communicating with the header flow paths 24A, 24B of the branch pipe 40 can be gradually reduced from the branch pipe 40 farthest from the header openings 23A, 23B to the branch pipe 40 closer to the header openings 23A, 23B. In this way, by using branch pipes 40 having the same internal pipe system but varying the inclination angles of the inclined surfaces, it is possible to provide heat exchangers 10D, 10E in which the area of ​​openings 45A, 45B communicating with the header flow paths 24A, 24B of the branch pipe 40 is gradually reduced from the branch pipe 40 away from the header openings 23A, 23B toward the branch pipe 40 closer to the header openings 23A, 23B.

[0072] (7) The heat exchangers 10A to 10E according to a seventh aspect are any one of the heat exchangers 10A to 10E according to (1) to (6), in which the heat medium is liquid. Examples of liquids include water and antifreeze.

[0073] According to the present embodiment, when the heat medium is liquid, the flow resistance of the heat medium between each of the branch pipes 40 and the header flow paths 24A, 24B gradually decreases from the branch pipes 40 away from the header openings 23A, 23B to the branch pipes 40 closer to the header openings 23A, 23B, thereby making it possible to more effectively equalize the flow rate of the heat medium among the multiple branch pipes 40.

[0074] (8) A heat exchanger 10C according to an eighth aspect is any one of the heat exchangers 10C (1) to (7), in which the three or more branch pipes 40 are connected to the headers 20A, 20B from different directions in a circumferential direction Dc about an axis along the extension direction of the header flow paths 24A, 24B.

[0075] According to the present embodiment, three or more branch pipes 40 are connected to the headers 20A, 20B from different directions in the circumferential direction Dc around the axis of the header flow paths 24A, 24B, thereby making it possible to prevent the effect of the branch pipe 40 located upstream in the flow direction of the heat medium in the header flow paths 24A, 24B on the flow resistance from extending to other branch pipes 40 located downstream in the flow direction. This also makes it possible to more effectively equalize the flow rate of the heat medium among the multiple branch pipes 40. [Explanation of symbols]

[0076] 10A~10E…Heat exchanger 20A…Inlet side header (Header) 20B…Outlet side header (Header) 21A, 21B...Header body 22A, 22B...Bent pipe section 23A, 23B...Header opening 24A, 24B...Header flow passage 40…Branch pipe 40A, 40P…first branch pipe 40B, 40Q...Second branch pipe 40C, 40R…Third branch pipe 40D, 40S...Fourth branch pipe 42A, 42B…Aperture 45A, 45B…Aperture 47A, 47B…Slanted surface 401a~401d...One end 402a~402d...other end Dc…Circumferential direction Ga, Ga1a~Ga4...Gap La, La1~La4, Lb, Lb1~Lb4...Protrusion length Xa, Xa1 to Xa4...Opening dimensions θa, θa1~θa4, θb...Inclination angle

Claims

1. a header having a header opening through which the heat medium flows in or out and a header flow path through which the heat medium flows; three or more branch pipes having the same pipe diameter, the branch pipes being arranged at intervals in a direction in which the header flow path extends, one ends of the branch pipes being connected to the header so as to protrude into the header flow path and communicate with the header flow path, The three or more branch pipes are provided such that a flow resistance of the heat medium between each of the three or more branch pipes and the header flow path gradually increases from a branch pipe farther from the header opening among the three or more branch pipes toward a branch pipe closer to the header opening among the three or more branch pipes. heat exchanger.

2. The three or more branch pipes are provided such that the protruding lengths into the header flow passage gradually increase from the branch pipes farther from the header opening toward the branch pipes closer to the header opening.

2. The heat exchanger of claim 1.

3. Each of the three or more branch pipes has an opening that faces the direction in which the branch pipe extends and communicates with the header flow path.

3. The heat exchanger of claim 2.

4. The three or more branch pipes are provided such that the area of ​​the opening of each of the branch pipes communicating with the header flow passage gradually decreases from the branch pipe farther from the header opening to the branch pipe closer to the header opening.

3. A heat exchanger according to claim 1 or 2.

5. The three or more branch pipes are provided such that the opening dimensions in the major axis direction of the openings are gradually reduced from the branch pipe farther from the header opening to the branch pipe closer to the header opening.

5. The heat exchanger of claim 4.

6. Each of the three or more branch pipes has an opening formed on an inclined surface that is inclined with respect to a direction in which the branch pipe extends at a tip end portion of the branch pipe that protrudes into the header flow path, The three or more branch pipes are provided such that the inclination angle of the inclined surface with respect to the direction in which each branch pipe extends gradually increases from the branch pipe farther from the header opening toward the branch pipe closer to the header opening.

5. The heat exchanger of claim 4.

7. The heat transfer medium is a liquid. A heat exchanger according to any one of claims 1 to 3.

8. The three or more branch pipes are connected to the header from different directions in a circumferential direction around an axis along a direction in which the header flow passage extends. A heat exchanger according to any one of claims 1 to 3.

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