Heat exchanger

Abstract

A heat exchanger according to the present invention has a plurality of fluid channels (21) and a tank (30, 70, 80). The plurality of fluid channels are stacked in a prescribed stacking direction and circulate a fluid that includes a gas phase and a liquid phase. The tank has a distribution space (SD) for distributing fluid to the plurality of fluid channels and an inflow opening (35) that allows fluid to flow into the distribution space. A fluid distribution part (100) for controlling the flow of fluid into the plurality of stacked fluid channels is provided on the inflow opening side of the distribution space of the tank. The fluid distribution part has a first circulation hole (102) and a second circulation hole (104). The first circulation hole is at a center part (101) of the fluid distribution part that is formed in a prescribed range that is centered on the center point (C) of a cross-section of the distribution space. The second circulation hole is at a peripheral part (103) of the fluid distribution part that is a region between the center part and an inside wall surface of the distribution space.

Description

heat exchanger CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Patent Application No. 2023-142197 filed on September 1, 2023, the contents of which are incorporated herein by reference.

[0002] The present disclosure relates to a heat exchanger having a tank into which a fluid containing a gas phase and a liquid phase flows, and a plurality of fluid flow paths arranged in a stack.

[0003] Conventionally, heat exchangers are configured with a tank that distributes and collects refrigerant and multiple refrigerant flow paths through which refrigerant flows from the tank, and the multiple refrigerant flow paths are stacked in a predetermined direction along the length of the tank. In such heat exchangers, temperature distribution in the multiple stacked refrigerant flow paths is important to improve heat exchange performance. To achieve this, it is desirable to distribute fluid uniformly among the multiple fluid flow paths when distributing the fluid from the tank to the multiple fluid flow paths.

[0004] However, in reality, when fluid flows within the tank toward the multiple fluid flow paths arranged in a stacked configuration, it is sometimes affected by inertial forces acting on the fluid, resulting in uneven distribution of the fluid.

[0005] A known technique relating to this point is described in Patent Document 1. The heat exchanger described in Patent Document 1 employs a configuration in which swirl vanes are arranged at the inlet of the tank in order to distribute the refrigerant evenly to each refrigerant flow path. In Patent Document 1, when the fluid flows into the tank, the swirl vanes impart a swirling component to the fluid flow, dispersing the two-phase fluid and bringing the fluid distribution to each fluid flow path closer to a uniform state.

[0006] Japanese Patent Application Laid-Open No. 2021-25764

[0007] In a heat exchanger, the total number of stacked fluid flow paths may increase, or the fluid inflow pattern into the tank may change. Depending on the manner of these changes, the technology of Patent Document 1 may not be able to achieve uniform distribution of fluid to each fluid flow path.

[0008] For example, if the total number of stacked fluid flow paths increases, the tank will extend along the stacking direction, and even if a swirl component is imparted by a swirl vane disposed at the inlet of the tank, it is expected that the flow of fluid flowing in from the inlet will not reach the fluid flow paths disposed downstream.

[0009] Furthermore, if the connection mode of the fluid supply flow path connected to the tank inlet is changed and the tank is connected from the side, the inertia acting on the fluid flowing in from the inlet will be different before and after the change in the supply flow path.Even if the fluid flow is biased toward the inlet due to the action of inertial force, the refrigerant will flow biased toward the inlet due to that inertia, and it is expected that the distribution of the fluid to each fluid flow path will be biased even if a swirl component is imparted to the fluid flow by swirl vanes.

[0010] In view of the above, an object of the present disclosure is to provide a heat exchanger that improves uniformity when distributing a two-phase fluid that has flowed into a tank to multiple fluid flow paths that are arranged in a stacked configuration.

[0011] A heat exchanger according to one aspect of the present disclosure is a heat exchanger having a plurality of fluid flow paths and a tank. The plurality of fluid flow paths are stacked in a predetermined stacking direction, and a fluid including a gas phase and a liquid phase flows through the plurality of fluid flow paths. The tank extends in the stacking direction of the plurality of fluid flow paths and is connected to the plurality of fluid flow paths. The tank has a distribution space for distributing fluid to the plurality of fluid flow paths and an inlet portion through which the fluid flows into the distribution space. A fluid distribution portion is arranged on the side of the inlet portion of the distribution space in the tank for controlling the flow of fluid to the plurality of stacked fluid flow paths.

[0012] The fluid distribution section has a first communication hole and a second communication hole. The first communication hole guides the fluid to a plurality of fluid flow paths connected to a downstream portion of the distribution space in the flow direction of the fluid. The second communication hole guides the fluid to a plurality of fluid flow paths connected to the distribution space in an upstream portion of the distribution space in the flow direction of the fluid. The first communication hole is arranged in a central portion of the fluid distribution section that is defined by a predetermined range centered on the center point of the cross-sectional shape of the distribution space. The second communication hole is arranged in a peripheral portion of the fluid distribution section that is defined by the region between the inner wall surface of the distribution space and the central portion.

[0013] Therefore, according to one aspect of the present disclosure, a heat exchanger can distribute fluid flowing into a distribution space of a tank to multiple fluid flow paths arranged in the stacking direction via a fluid distribution section. A first communication hole is formed in the center of the fluid distribution section, and by passing through the first communication hole, the fluid can be guided to multiple fluid flow paths connected to a downstream portion of the distribution space in the flow direction of the fluid. Furthermore, a second communication hole is formed in the periphery of the fluid distribution section, and by passing through the second communication hole, the fluid can be guided to multiple fluid flow paths connected to the distribution space in an upstream portion of the flow direction. In other words, by allowing the fluid to flow out into the distribution space via the first communication hole and the second communication hole of the fluid distribution section, the heat exchanger can improve the uniformity of fluid distribution to multiple fluid flow paths connected to the distribution space.

[0014] The above and other objects, features, and advantages of the present disclosure will become more apparent from the following detailed description taken in conjunction with the accompanying drawings.

[0023] Fig. 1 is a front view of a heat exchanger according to a first embodiment.

[0024] Fig. 2 is a plan view of a heat exchanger according to the first embodiment.

[0025] Fig. 3 is an explanatory diagram showing a refrigerant distribution structure in a heat exchanger.

[0026] Fig. 4 is a cross-sectional view of a refrigerant inlet tank of a heat exchanger according to the first embodiment.

[0027] Fig. 5 is a plan view of a fluid distribution section according to the first embodiment.

[0028] Fig. 6 is a graph showing refrigerant distribution characteristics by the fluid distribution section according to the first embodiment.

[0029] Fig. 7 is an explanatory diagram showing a refrigerant distribution mode by the fluid distribution section according to the first embodiment.

[0030] Fig. 8 is a plan view of a fluid distribution section of a heat exchanger according to a second embodiment.

[0031] Fig. 9 is a cross-sectional view of a fluid distribution section of a heat exchanger according to a third embodiment.

[0032] Fig. 10 is a cross-sectional view of a fluid distribution section of a heat exchanger according to a fourth embodiment.

[0033] Fig. 11 is an explanatory diagram showing the arrangement of a fluid distribution section in a heat exchanger according to a fifth embodiment.

[0034] Fig. 12 is a cross-sectional view of a fluid distribution section of a heat exchanger according to a sixth embodiment.

[0035] Fig. 13 is a cross-sectional view of a fluid distribution section of a heat exchanger according to a seventh embodiment.

[0036] Fig. 14 is a plan view of a fluid distribution section of a heat exchanger according to an eighth embodiment.

[0015] Hereinafter, several embodiments for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, parts corresponding to matters described in the preceding embodiment may be assigned the same reference numerals, and duplicate descriptions may be omitted. In each embodiment, when only a part of the configuration is described, other previously described embodiments may be applied to the other parts of the configuration. In addition to combinations of parts that are specifically specified as being combinable in each embodiment, it is also possible to partially combine embodiments even if not specified, as long as there is no particular problem with the combination.

[0016] (First embodiment) A first embodiment of the present disclosure will be described with reference to Figures 1 to 7. To facilitate understanding of the description, the same components in the drawings will be denoted by the same reference numerals as much as possible, and duplicate descriptions will be omitted.

[0017] In the first embodiment, the heat exchanger according to the present disclosure is applied to an evaporator (so-called chiller) that evaporates a refrigerant by exchanging heat between the refrigerant circulating in the refrigeration cycle of an air conditioning device mounted on a vehicle and the coolant.

[0018] 1 to 4, the heat exchanger 1 according to the first embodiment is configured by stacking a plurality of plate members 10 in the Z-axis direction, and has a heat exchange core 20, a refrigerant inlet tank 30, a refrigerant outlet tank 40, a cooling water inlet tank 50, and a cooling water outlet tank 60. Hereinafter, the Z-axis direction will also be referred to as the "stacking direction Z."

[0019] The heat exchange core portion 20 is formed by a part of a plurality of plate members 10 stacked in the Z-axis direction, and has a plurality of refrigerant flow paths 21 and a plurality of cooling water flow paths (not shown).

[0020] A refrigerant flow path 21 through which a refrigerant flows and a cooling water flow path through which cooling water flows are provided inside each plate member 10. In the heat exchange core 20, the refrigerant flow paths 21 and the cooling water flow paths are alternately arranged along the Z-axis direction. In the heat exchanger 1, a two-phase refrigerant containing a gas phase and a liquid phase flows through the refrigerant flow path 21, which corresponds to an example of a fluid flow path.

[0021] 2, the heat exchange core 20 of the heat exchanger 1 has a substantially rectangular cross section perpendicular to the stacking direction Z. Hereinafter, the longitudinal direction and the lateral direction of the heat exchange core 20 will be referred to as the "X-axis direction" and the "Y-axis direction," respectively.

[0022] A refrigerant inlet tank 30 and a refrigerant outlet tank 40 are provided at two of the four corners of the plate members 10 that are located diagonally opposite each other. A cooling water inlet tank 50 and a cooling water outlet tank 60 are provided at the remaining diagonally opposite corners of the plate members 10.

[0023] The refrigerant inlet tank 30 is a storage section into which the two-phase refrigerant, gas and liquid, circulating through the refrigeration cycle flows. As shown in Fig. 4, the refrigerant inlet tank 30 has a cylindrical internal space extending in the Z-axis direction. The refrigerant that flows into the refrigerant inlet tank 30 is distributed to the multiple refrigerant flow paths 21 stacked in the Z-axis direction in the heat exchange core 20. Therefore, the internal space of the refrigerant inlet tank 30 is formed by a distribution space SD for distributing the refrigerant to the multiple refrigerant flow paths 21, and corresponds to an example of a tank.

[0024] The refrigerant discharge tank 40 is a storage section into which the refrigerant flows after flowing through the multiple refrigerant flow paths 21 that make up the heat exchange core 20. Similar to the refrigerant inlet tank 30, the refrigerant discharge tank 40 has a cylindrical internal space extending in the Z-axis direction. Therefore, the internal space of the refrigerant discharge tank 40 is configured as a collection space SA for collecting the refrigerant that has flowed through the multiple refrigerant flow paths 21. After flowing into the refrigerant discharge tank 40 and collecting therein, the refrigerant is discharged to the outside of the heat exchanger 1. The discharged refrigerant circulates through the refrigeration cycle.

[0025] The coolant inlet tank 50 is a reservoir into which the coolant circulating through the coolant circuit flows. Similar to the refrigerant inlet tank 30, the coolant inlet tank 50 has a cylindrical internal space extending in the Z-axis direction. The internal space of the coolant inlet tank 50 is connected to a plurality of coolant flow paths stacked in the Z-axis direction in the heat exchange core 20. The coolant that flows into the coolant inlet tank 50 is distributed to the plurality of coolant flow paths.

[0026] The coolant discharge tank 60 is a reservoir into which the coolant flows after flowing through the multiple coolant passages that make up the heat exchange core 20. Similar to the refrigerant inlet tank 30, the coolant discharge tank 60 has a cylindrical internal space extending in the Z-axis direction. After flowing through the multiple coolant passages and collecting inside the coolant discharge tank 60, the coolant is discharged to the outside of the heat exchanger 1. The discharged coolant circulates through the coolant circuit.

[0027] As described above, in the heat exchanger 1 according to the first embodiment, heat exchange occurs between the refrigerant flowing through the multiple refrigerant flow paths 21 and the coolant flowing through the multiple coolant flow paths in the heat exchange core 20. As a result, in the heat exchanger 1, the refrigerant evaporates due to the heat possessed by the coolant, and the coolant can be cooled by the heat absorption effect of the refrigerant.

[0028] 3, the heat exchange core 20 includes a plurality of plate members 10, refrigerant fins 21F, and coolant fins (not shown). These members are made of a metal material such as an aluminum alloy.

[0029] The plate member 10 in the first embodiment includes an outer plate 11, an inner plate 12, and a top plate 13. The outer plate 11 is a plate-like member having a substantially rectangular cross section perpendicular to the stacking direction Z. A protruding portion 11B that protrudes in the positive direction of the Z axis is formed on the outer peripheral edge of the outer plate 11. The multiple outer plates 11 are stacked and arranged with the protruding portion 11B facing in the positive direction of the Z axis.

[0030] The outer plate 11 is provided with a burred portion 11A formed by burring. The burred portion 11A forms a circular opening centered on the central axis of the refrigerant inlet tank 30, and the opening edge of the opening is formed to protrude cylindrically in the positive direction of the Z axis. Therefore, the burred portion 11A corresponds to an example of an opening. A protrusion 11C protruding in the negative direction of the Z axis is formed at the base end of the outer plate 11 corresponding to the burred portion 11A.

[0031] Similar to the outer plates 11, the inner plates 12 are plate-like members each having a substantially rectangular cross section perpendicular to the stacking direction Z. The inner plates 12 are disposed inside the protruding portions 11B of the outer plates 11 and between adjacent outer plates 11, and are joined to each other by brazing.

[0032] The inner plate 12 divides the space formed between two adjacent outer plates 11 into independent refrigerant flow paths 21 and cooling water paths that are not connected to each other. More specifically, the gap formed between the inner plate 12 and the outer plate 11 adjacent to the inner plate 12 in the negative Z-axis direction constitutes the refrigerant flow path 21. Also, the gap formed between the inner plate 12 and the outer plate 11 adjacent to the inner plate 12 in the positive Z-axis direction constitutes the cooling water flow path.

[0033] Coolant fins 21F are arranged in the coolant flow path 21. Coolant fins are also arranged in the coolant flow path. Offset fins, for example, can be used as the coolant fins 21F and the coolant fins. The coolant fins 21F increase the heat transfer area for the coolant flowing through the coolant flow path 21. The coolant fins increase the heat transfer area for the coolant flowing through the coolant flow path.

[0034] The inner plate 12 has a burred portion 12A formed by burring at a portion corresponding to the burred portion 11A of the outer plate 11. The burred portion 12A forms a circular opening centered on the central axis of the refrigerant inlet tank 30, and the opening edge of the opening is formed to protrude cylindrically in the negative direction of the Z axis. The burred portion 12A, like the burred portion 11A, is an example of an opening. A protrusion 12C protruding in the positive direction of the Z axis is formed at the base end of the burred portion 12A on the inner plate 12.

[0035] The protruding portion 12C of the inner plate 12 is joined by brazing to the protruding portion 11C of the outer plate 11 adjacent in the positive direction of the Z axis. As a result, the burring portions 11A of the outer plate 11 and the burring portions 12A of the inner plate 12 are arranged side by side in the Z axis direction. In other words, the burring portions 11A of the multiple outer plates 11 and the burring portions 12A of the multiple inner plates 12 form a refrigerant inlet tank 30 having a cylindrical internal space.

[0036] An inlet port 35 is disposed in the positive direction of the Z axis from the burring portions 11A and 12A. The inlet port 35 according to the first embodiment includes an inlet for allowing refrigerant, including gas and liquid phases, to flow from the refrigeration cycle into the interior space of the refrigerant inlet tank 30, and has a connector member 36. The connector member 36 is connected to the refrigeration cycle and serves as a connector for connecting a refrigerant inlet pipe for supplying refrigerant, including gas and liquid phases, to the inlet port. Therefore, the inlet port 35 is located at the most upstream position in the refrigerant flow direction within the interior space of the refrigerant inlet tank 30.

[0037] The cylindrical portion of the burring portion 11A of the outer plate 11 and the cylindrical portion of the burring portion 12A of the inner plate 12 form a peripheral wall 38 of the refrigerant inlet tank 30.

[0038] The protruding portion 11C of the outer plate 11 and the protruding portion 12C of the inner plate 12 are joined together to separate the cooling water flow path from the refrigerant inlet tank 30. Therefore, the refrigerant flowing through the refrigerant inlet tank 30 does not flow into the cooling water flow path.

[0039] 3 and 4, the tip of the cylindrical portion of the burring portion 11A of the outer plate 11 and the tip of the cylindrical portion of the burring portion 12A of the inner plate 12 are arranged with a predetermined gap between them. In other words, the refrigerant flow path 21 formed between the outer plate 11 and the inner plate 12 communicates with each other via the gap between the tip of the cylindrical portion of the burring portion 11A and the tip of the cylindrical portion of the burring portion 12A.

[0040] The gap between the tip of the cylindrical portion of burring portion 11A and the tip of the cylindrical portion of burring portion 12A constitutes a communication portion 37 in refrigerant inlet tank 30. Communication portion 37 is a portion that distributes the refrigerant that has flowed into refrigerant inlet tank 30 into multiple refrigerant flow paths 21.

[0041] 3 and 4, the refrigerant inlet tank 30 has a communication section 37, and the cylindrical section of the burring section 11A and the cylindrical section of the burring section 12A form a peripheral wall 38 of the refrigerant inlet tank 30. Therefore, the communication section 37 of the refrigerant inlet tank 30 communicates with the refrigerant flow path 21 around the entire circumference of the refrigerant inlet tank 30.

[0042] Therefore, in the refrigerant inlet tank 30 of the heat exchanger 1 according to the first embodiment, the refrigerant that has flowed into the interior of the refrigerant inlet tank 30 can be discharged into each refrigerant flow path 21 through a communication portion 37 formed around the entire circumference of the refrigerant inlet tank 30.

[0043] Here, consider a case where the refrigerant inlet tank 30, which has a cylindrical internal space, has the communication part 37 formed in a portion of the circumferential direction. In the flow of refrigerant flowing through the refrigerant inlet tank 30, in the portion where the communication part 37 is formed, it is thought that the refrigerant flows through the communication part 37 and into the refrigerant flow path 21. On the other hand, in the portion where the communication part 37 is not formed, the refrigerant flows through a position away from the communication part 37, which is thought to be in an environment where the refrigerant is more likely to flow downstream, and therefore it is thought that the refrigerant continues to flow downstream through the internal space of the refrigerant inlet tank 30.

[0044] If the presence or absence of a circumferential communication portion 37 causes an imbalance in the flow of refrigerant inside the refrigerant inlet tank 30, a circulating flow of refrigerant will occur in the internal space of the refrigerant inlet tank 30, and it is expected that the controllability of the distribution of refrigerant to the multiple refrigerant flow paths 21 will be impaired.

[0045] In this regard, when a configuration in which the communication portion 37 is formed around the entire circumference of the refrigerant inlet tank 30 is adopted, as in the refrigerant inlet tank 30 of the heat exchanger 1, there is no bias in the flow of refrigerant inside the refrigerant inlet tank 30. This prevents the refrigerant from circulating in the internal space of the refrigerant inlet tank 30, and ensures controllability regarding the distribution of refrigerant to the multiple refrigerant flow paths 21.

[0046] The top plate 13 is disposed at the position furthest in the positive Z-axis direction among the plurality of plate members 10 constituting the heat exchange core 20. As shown in Fig. 4, the top plate 13 has a fluid distribution section 100 at a position on the Z-axis of the refrigerant inlet tank 30 (i.e., burring sections 11A and 12A).

[0047] The fluid distribution part 100 is located on the inlet port 35 side of the distribution space SD of the refrigerant inlet tank 30, and is formed to evenly distribute the refrigerant that has flowed into the distribution space SD to the multiple refrigerant flow paths 21 connected to the distribution space SD. As described above, because the fluid distribution part 100 is formed on the top plate 13, the number of parts can be reduced compared to when the fluid distribution part 100 is configured as a separate member.

[0048] The fluid distribution part 100 corresponds to the cross-sectional shape perpendicular to the Z axis of the distribution space SD of the refrigerant inlet tank 30, and is formed in a circular shape with the central axis of the distribution space SD as the center point C. Therefore, the outer diameter dimension of the fluid distribution part 100 corresponds to the tank diameter D, which is the diameter of the distribution space SD in the refrigerant inlet tank 30 (i.e., the opening diameter of the burring parts 11A and 12A).

[0049] 4 and 5 , the fluid distribution unit 100 has one first through hole 102 and multiple second through holes 104. The first through hole 102 is located in a central portion 101 of the fluid distribution unit 100 and guides the refrigerant toward multiple refrigerant flow paths 21 connected downstream in the refrigerant flow direction in the distribution space SD extending in the Z-axis direction. The second through hole 104 is located in a peripheral portion 103 of the fluid distribution unit 100 and guides the refrigerant toward the refrigerant flow path 21 connected upstream in the refrigerant flow direction in the distribution space SD, among the multiple refrigerant flow paths 21 stacked in the stacking direction Z.

[0050] Here, the central portion 101 of the fluid distribution unit 100 is a portion defined around a central point C located on the central axis of the distribution space SD. The central portion 101 of the fluid distribution unit 100 according to the first embodiment is a circular region having a diameter dimension that is 1 / 3 of the tank diameter D, which is the outer diameter dimension of the fluid distribution unit 100, and centered on the central point C.

[0051] The peripheral portion 103 of the fluid distribution portion 100 is disposed so as to surround the periphery of the central portion 101 within the fluid distribution portion 100, and is the region between the inner wall surface of the distribution space SD (i.e., the outer edge of the fluid distribution portion 100) and the central portion 101 in the fluid distribution portion 100. As shown in Fig. 5 , the peripheral portion 103 according to the first embodiment is an annular region formed within the circular fluid distribution portion 100 between the outer edge of the central portion 101 and the outer edge of the fluid distribution portion 100 itself.

[0052] 5, the outer edge of the central portion 101 of the fluid distribution portion 100 is shown as a reference line L. The reference line L can also be said to be the boundary line between the central portion 101 and the peripheral portion 103 of the fluid distribution portion 100.

[0053] 5, the first communication hole 102 is opened in a circular shape centered on a central point C in the central portion 101 of the fluid distribution portion 100. The first communication hole 102 contracts the flow of the refrigerant that has flowed into the inlet portion 35 of the distribution space SD in the refrigerant inlet tank 30, thereby increasing the flow velocity toward the downstream side in the flow direction in the distribution space SD.

[0054] As described above, the fluid distribution section 100 is formed in a part of the top plate 13, and therefore the first flow holes 102 are configured by forming punched holes in the thin top plate 13. By configuring the first flow holes 102 with punched holes, the flow path length as a flow contraction section can be shortened to a length equivalent to the thickness of the top plate 13, and the pressure loss caused by the fluid distribution section 100 can be reduced.

[0055] The opening area of ​​the first through hole 102 according to the first embodiment is determined so that the index value γ calculated by Equation 1, which will be described later, satisfies a predetermined numerical condition. The opening area of ​​the first through hole 102 is referred to as a first through hole area Aa.

[0056] On the other hand, the second communication holes 104 are evenly arranged at predetermined intervals in the circumferential direction of the fluid distribution section 100 in the peripheral section 103 of the fluid distribution section 100. As shown in Fig. 5, six second communication holes 104 are formed in the peripheral section 103 of the fluid distribution section 100 according to the first embodiment. The second communication holes 104 contract the flow of the refrigerant that has flowed into the inlet section 35 of the distribution space SD in the refrigerant inlet tank 30, and guide it to the refrigerant flow path 21 upstream in the flow direction of the distribution space SD.

[0057] Like the first flow holes 102, each second flow hole 104 is formed by forming a punched hole in the thin top plate 13. By forming the second flow holes 104 using punched holes, the flow path length as the flow contraction section can be shortened to the thickness of the top plate 13, and the pressure loss caused by the fluid distribution section 100 can be reduced.

[0058] Each second flow hole 104 is arranged at a predetermined distance from the central axis (i.e., center point C) of the distribution space SD in the peripheral portion 103 of the fluid distribution section 100. In this case, the center position of each second flow hole 104 in the fluid distribution section 100 and the center point C are referred to as a second flow hole position d.

[0059] In the first embodiment, the opening area of ​​the first flow hole 102, the opening area of ​​each second flow hole 104, and the arrangement of each second flow hole 104 in the fluid distribution section 100 are determined so that the index value γ calculated by Equation 1 described below satisfies specified numerical conditions.

[0060] As described above, in the first embodiment, in order to evenly distribute the refrigerant including the gas phase and the liquid phase to the multiple refrigerant flow paths 21 connected to the distribution space SD, the details of the first circulation holes 102 and the second circulation holes 104 are determined using the index value γ calculated by the following mathematical formula 1. A larger index value γ indicates a stronger effect of the fluid distribution part 100 to send the refrigerant downstream in the flow direction in the distribution space SD.

[0061]

[0062] where Aa is the opening area of ​​the first flow hole 102, Ab is the total opening area of ​​the second flow holes 104, D is the diameter of the distribution space SD of the tank, and d is the position of the second flow hole 104 in the cross section of the distribution space of the tank.

[0063] The first term of the above mathematical formula 1 uses the opening area of ​​the first flow holes 102 / the total opening area of ​​the second flow holes 104. The second flow hole area Ab is determined by adding up the opening areas of the second flow holes 104. As a result, with respect to the flow rate of refrigerant passing through the fluid distribution section 100, the larger the value of the first term of mathematical formula 1, the greater the flow rate of refrigerant passing through the central section 101 compared to the peripheral section 103.

[0064] The second term of the above formula 1 uses Aa + Ab. Aa + Ab means the total opening area of ​​the fluid distribution section 100. At means the cross-sectional area of ​​the distribution space SD in the refrigerant inlet tank 30, and corresponds to the area of ​​the fluid distribution section 100 itself. In the first embodiment, the diameter of the refrigerant inlet tank 30 is the tank diameter D, and the cross-sectional shape of the distribution space SD is circular, so the tank cross-sectional area At can be derived using the tank diameter D. The larger the value of the second term of the above formula 1, the greater the flow velocity of the refrigerant passing through the first flow hole 102 and the second flow hole 104.

[0065] The third term in the above formula 1 uses (D-d). As described above, (D-d) is the diameter of the distribution space SD of the tank, and d indicates the position of the second communication holes 104 in the cross section of the distribution space SD of the tank. Therefore, the larger the value of the third term in formula 1, the closer the multiple second communication holes 104 are positioned to the center 101 of the fluid distribution section 100.

[0066] When the index value γ is experimentally calculated based on the above-described mathematical formula 1, it is found to have the characteristics shown in Fig. 6. The performance ratio in Fig. 6 indicates the degree of bias when distributing the fluid to the plurality of refrigerant flow paths 21 arranged in a stack, and the more evenly the fluid is distributed to the plurality of refrigerant flow paths 21, the closer to 1 the value is, with the maximum value of the performance ratio being 1.

[0067] As shown in Figure 6, for the fluid distribution unit 100 according to the first embodiment, the refrigerant distribution characteristics using the index value γ indicate that when the value of the index value γ is within a certain range, the refrigerant can be uniformly distributed to the multiple refrigerant flow paths 21 stacked and arranged in the distribution space SD.

[0068] Specifically, when the index value γ is less than 0.4, the performance ratio of the fluid distribution section 100 is less than 0.8. When a fluid distribution section 100 with an index value γ of less than 0.4 is used, the refrigerant flow by the fluid distribution section 100 is directed mostly upstream in the flow direction in the distribution space SD. This results in uneven distribution of the refrigerant to the multiple refrigerant flow paths 21 that make up the heat exchange core section 20, which deteriorates the temperature distribution in the heat exchange core section 20, and is thought to result in a decrease in the heat exchange performance of the heat exchanger 1.

[0069] Furthermore, even when the index value γ is greater than 1.1, the performance ratio of the fluid distribution section 100 is less than 0.8. When a fluid distribution section 100 with an index value γ greater than 1.1 is used, the refrigerant flow by the fluid distribution section 100 is directed mostly downstream in the flow direction in the distribution space SD. In this case, too, the refrigerant is unevenly distributed to the multiple refrigerant flow paths 21 that make up the heat exchange core section 20, which deteriorates the temperature distribution in the heat exchange core section 20 and is therefore thought to reduce the heat exchange performance of the heat exchanger 1.

[0070] As shown in Figure 6, when the index value γ is 0.4 or more and 1.1 or less, the performance ratio of the fluid distribution unit 100 is 0.8 to 1.0. When the index value γ is in the range of 0.4 to 1.1, the refrigerant flow by the fluid distribution unit 100 is uniformly guided from the upstream side to the downstream side in the flow direction in the distribution space SD. This allows the refrigerant to be uniformly distributed to all refrigerant flow paths 21 connected to the distribution space SD, and the temperature distribution of the heat exchange core unit 20 is also uniform, thereby suppressing a decrease in the heat exchange performance of the heat exchanger 1.

[0071] As described above, in the heat exchanger 1 according to the first embodiment, one first through hole 102 is formed in the central portion 101 of the fluid distribution section 100, and six second through holes 104 are evenly arranged in the circumferential direction in the peripheral portion 103 of the fluid distribution section 100. The first through hole 102 contracts the flow of the refrigerant in the central portion of the distribution space SD, thereby increasing the flow velocity toward the downstream side in the flow direction in the distribution space SD.

[0072] 7, the heat exchanger 1 according to the first embodiment allows the two-phase refrigerant to flow to the downstream side in the flow direction in the distribution space SD through the first flow holes 102 of the fluid distribution section 100. This allows the two-phase refrigerant to be distributed to the refrigerant flow path 21 connected downstream in the flow direction among the multiple refrigerant flow paths 21 stacked and arranged in the distribution space SD.

[0073] Furthermore, the second flow holes 104 contract the flow of the refrigerant on the radially outer side of the distribution space SD (i.e., on the inner wall surface side of the refrigerant inlet tank 30) and guide it to the refrigerant flow paths 21 on the upstream side in the flow direction in the distribution space SD. This allows the two-phase refrigerant to be distributed to the refrigerant flow paths 21 connected on the upstream side in the flow direction among the multiple refrigerant flow paths 21 stacked and arranged in the distribution space SD.

[0074] That is, according to the heat exchanger 1 of the first embodiment, the refrigerant can be evenly distributed to the multiple refrigerant flow paths 21 stacked in the distribution space SD by utilizing the first and second flow holes 102 and 104 of the fluid distribution section 100. As a result, the heat exchanger 1 can achieve a uniform temperature distribution in the heat exchange core section 20, and can suppress a decrease in the heat exchange performance of the heat exchanger 1.

[0075] 3 and 4, the peripheral wall 38 of the refrigerant inlet tank 30 according to the first embodiment is formed by the cylindrical portion of the burring portion 11A and the cylindrical portion of the burring portion 12A. The communication portion 37 is formed by the gap between the tip of the cylindrical portion of the burring portion 11A and the tip of the cylindrical portion of the burring portion 12A.

[0076] As a result, each communication portion 37 of the refrigerant inlet tank 30 is connected to a corresponding refrigerant flow path 21 around the entire circumference of the refrigerant inlet tank 30. Therefore, when the two-phase refrigerant flows from the refrigerant inlet tank 30 into the refrigerant flow path 21, the two-phase refrigerant flows radially around the entire circumference of the distribution space SD and into the refrigerant flow path 21. As a result, according to the heat exchanger 1, the two-phase refrigerant can flow into each refrigerant flow path 21 without any deviation in the flow of the two-phase refrigerant inside the distribution space SD, and the impact of the flow of the two-phase refrigerant within the distribution space SD on uniform distribution can be suppressed.

[0077] In the fluid distribution section 100 of the heat exchanger 1 according to the first embodiment, the opening area of ​​the first through holes 102, the opening area of ​​each second through hole 104, and the arrangement of each second through hole 104 in the fluid distribution section 100 are determined so that the index value γ satisfies a predetermined numerical condition. The index value γ indicates the refrigerant distribution characteristics for the multiple refrigerant flow paths 21 stacked in the distribution space SD, and a value of γ in the range of 0.4 to 1.1 indicates a state in which the refrigerant is uniformly distributed to the multiple refrigerant flow paths 21.

[0078] In other words, in the heat exchanger 1 according to the first embodiment, the details of the first circulation hole 102 and the plurality of second circulation holes 104 are determined so that the index value γ calculated by Equation 1 is in the range of 0.4 to 1.1, thereby enabling the refrigerant to be evenly distributed to the plurality of refrigerant flow paths 21 in the distribution space SD.

[0079] 4 and 7, in the heat exchanger 1 according to the first embodiment, the fluid distribution section 100 is disposed at the inlet port 35 of the refrigerant inlet tank 30, which is formed by the distribution space SD. Therefore, the heat exchanger 1 can distribute the refrigerant evenly to all of the refrigerant flow paths 21 connected to the refrigerant inlet tank 30, thereby achieving a uniform temperature distribution in the heat exchange core section 20 and preventing a decrease in heat exchange performance.

[0080] As described above, in the heat exchanger 1 according to the first embodiment, one first flow hole 102 is formed in the central portion 101 of the fluid distribution section 100, and six second flow holes 104 are evenly arranged circumferentially in the peripheral portion 103 of the fluid distribution section 100.

[0081] According to the heat exchanger 1 of the first embodiment, the refrigerant can be evenly distributed to the multiple refrigerant flow paths 21 stacked in the distribution space SD by utilizing the first and second flow holes 102 and 104 of the fluid distribution section 100. As a result, the heat exchanger 1 can achieve a uniform temperature distribution in the heat exchange core section 20, and can suppress a decrease in the heat exchange performance of the heat exchanger 1.

[0082] 3 and 4 , each communication portion 37 of the refrigerant inlet tank 30 is connected to a corresponding refrigerant flow path 21 around the entire circumference of the refrigerant inlet tank 30. Therefore, when the two-phase refrigerant flows from the refrigerant inlet tank 30 into the refrigerant flow path 21, the two-phase refrigerant flows radially around the entire circumference of the distribution space SD and then flows into the refrigerant flow path 21. As a result, the heat exchanger 1 allows the two-phase refrigerant to flow into each refrigerant flow path 21 without bias within the distribution space SD, thereby minimizing the impact of the flow of the two-phase refrigerant within the distribution space SD on uniform distribution.

[0083] In the heat exchanger 1 according to the first embodiment, the opening area of ​​the first through holes 102, the opening area of ​​each of the second through holes 104, and the arrangement of each of the second through holes 104 in the fluid distribution section 100 are determined so that the index value γ calculated by Equation 1 is in the range of 0.4 to 1.1. As a result, according to the heat exchanger 1 according to the first embodiment, the details of the first through holes 102 and the plurality of second through holes 104 are appropriately determined, and uniform distribution of the refrigerant to the plurality of refrigerant flow paths 21 in the distribution space SD can be achieved.

[0084] 4 and 7 , the interior of the refrigerant inlet tank 30 is configured as a distribution space SD that connects all of the stacked refrigerant flow paths 21 that make up the heat exchange core 20. The fluid distribution section 100 is located on the inlet 35 side of the refrigerant inlet tank 30, and the inlet 35 is located at the most upstream position in the direction of fluid flow within the refrigerant inlet tank 30. Therefore, with the heat exchanger 1 according to the first embodiment, the refrigerant can be evenly distributed from the refrigerant inlet tank 30 to all of the refrigerant flow paths 21 that make up the heat exchange core 20, thereby preventing a decrease in the heat exchange efficiency of the heat exchanger 1.

[0085] Second Embodiment Next, a second embodiment, which differs from the above-described embodiment, will be described with reference to Fig. 8. In the heat exchanger 1 according to the second embodiment, the number and arrangement of the first flow holes 102 and the second flow holes 104 in the fluid distribution section 100 differ from those of the first embodiment. Other components of the heat exchanger 1 according to the second embodiment (e.g., the heat exchange core section 20, etc.) are the same as those of the first embodiment, and therefore will not be described again.

[0086] 8, three first through holes 102 are formed in the central portion 101 of the fluid distribution portion 100 according to the second embodiment. The first through holes 102 according to the first embodiment are arranged on the center point C of the fluid distribution portion 100, whereas the first through holes 102 according to the second embodiment are arranged evenly in the circumferential direction at a predetermined distance from the center point C of the fluid distribution portion 100.

[0087] Furthermore, twelve second flow holes 104 are formed in the peripheral portion 103 of the fluid distribution portion 100 according to the second embodiment. The second flow holes 104 according to the first embodiment are arranged evenly in the circumferential direction in the peripheral portion 103 so that the distance from the center point C is a predetermined distance. On the other hand, the second flow holes 104 according to the second embodiment are configured such that six second flow holes 104 are arranged so that the distance from the center point C is a predetermined distance in the peripheral portion 103, and six second flow holes 104 are arranged so that the distance from the center point C is evenly greater. The six second flow holes 104 that are the same distance from the center point C are all arranged evenly in the circumferential direction at predetermined intervals in the peripheral portion 103.

[0088] In the fluid distribution section 100 according to the second embodiment, the first communication holes 102, like those in the first embodiment, contract the refrigerant flow in the central portion of the distribution space SD, thereby increasing the flow velocity toward the downstream side in the flow direction in the distribution space SD. Furthermore, the second communication holes 104 according to the second embodiment contract the refrigerant flow on the radially outer side of the distribution space SD (i.e., on the inner wall surface side of the refrigerant inlet tank 30) and guide the refrigerant to the refrigerant flow path 21 on the upstream side in the flow direction in the distribution space SD.

[0089] Therefore, according to the heat exchanger 1 of the second embodiment, the refrigerant can be evenly distributed to the multiple refrigerant flow paths 21 stacked in the distribution space SD by utilizing the first and second flow holes 102 and 104 of the fluid distribution section 100. As a result, the heat exchanger 1 can achieve a uniform temperature distribution in the heat exchange core section 20, and can suppress a decrease in the heat exchange performance of the heat exchanger 1.

[0090] Furthermore, in the fluid distribution section 100 according to the second embodiment, by increasing the numbers of the first through holes 102 and the second through holes 104 and setting a plurality of distance patterns between the center point C and the second through holes 104, it becomes possible to control the flow pattern of the contracted refrigerant in detail. As a result, according to the heat exchanger 1 according to the second embodiment, by using the fluid distribution section 100, it is possible to more accurately and uniformly distribute the refrigerant to the refrigerant flow paths 21 arranged in a stack in the distribution space SD.

[0091] As described above, according to the heat exchanger 1 of the second embodiment, even if the number and arrangement of the first flow holes 102 and the second flow holes 104 in the fluid distribution section 100 are different, the same functional effects as those of the above-mentioned embodiment can be obtained from the same configuration and operation.

[0092] Third Embodiment Next, a third embodiment, which differs from the above-described embodiment, will be described with reference to Fig. 9. In the heat exchanger 1 according to the third embodiment, the connection of the refrigerant inlet pipe 35A to the inlet port 35 differs from that of the above-described embodiment. Other components of the heat exchanger 1 according to the third embodiment (e.g., the heat exchange core 20) are the same as those of the above-described embodiment, and therefore will not be described again.

[0093] 4 and 7 , in the heat exchanger 1 according to the first embodiment, a refrigerant pipe is connected to the connector member 36 of the inlet port 35 of the refrigerant inlet tank 30 so as to extend along the Z-axis direction. Therefore, in the first embodiment, the refrigerant flows along the Z-axis direction from upstream of the inlet port 35 in the refrigerant flow direction to the inside of the distribution space SD.

[0094] 9, a refrigerant inlet pipe 35A extending along one surface of the heat exchange core 20 on the positive side of the Z axis is connected to the inlet port 35 of the heat exchanger 1 according to the third embodiment. Therefore, in the third embodiment, the refrigerant flows through the refrigerant inlet pipe 35A in a direction perpendicular to the Z axis, and then flows along the Z axis direction from just upstream of the inlet port 35. Therefore, in the second embodiment, the refrigerant flows along the Z axis direction from the inlet port 35 to the inside of the distribution space SD.

[0095] The fluid distribution unit 100 according to the third embodiment is attached to the inlet port 35 of the refrigerant inlet tank 30, which is formed by the distribution space SD. Therefore, in the heat exchanger 1 according to the third embodiment, the refrigerant can be evenly distributed to the multiple refrigerant flow paths 21 by using the first circulation holes 102 and the second circulation holes 104 of the fluid distribution unit 100.

[0096] As described above, according to the heat exchanger 1 of the third embodiment, even if the manner in which fluid is supplied to the tank is changed, the effects achieved by the configuration and operation common to the above-mentioned embodiments can be obtained.

[0097] Fourth Embodiment Next, a fourth embodiment, which differs from the above-described embodiments, will be described with reference to Fig. 10. In the heat exchanger 1 according to the fourth embodiment, the arrangement of the fluid distribution section 100 in the inlet section 35 differs from that of the above-described embodiments. Other components of the heat exchanger 1 according to the fourth embodiment (e.g., the outer plate 11, the inner plate 12, etc.) are the same as those of the above-described embodiments, and therefore will not be described again.

[0098] In the above-described embodiments, the fluid distribution section 100 is configured as a part of the top plate 13 and is disposed at the inlet portion 35 of the distribution space SD. As shown in Fig. 10, the fluid distribution section 100 according to the fourth embodiment is configured as a single member formed separately from the top plate 13, and has a first communication hole 102 and a second communication hole 104, similar to the above-described embodiments.

[0099] The fluid distribution unit 100 according to the fourth embodiment is attached to the inside of the connector member 36 attached to the inlet portion 35. Specifically, the fluid distribution unit 100 according to the fourth embodiment contracts the flow of refrigerant flowing from the refrigerant inlet pipe 35A toward the inlet of the refrigerant inlet tank 30 inside the refrigerant flow path formed in the connector member 36. That is, the fluid distribution unit 100 according to the fourth embodiment contracts the flow of refrigerant flowing toward the inside of the distribution space SD via the connector member 36 and the inlet, by using the first flow hole 102 and the second flow hole 104.

[0100] Therefore, in the heat exchanger 1 according to the fourth embodiment, by utilizing the first flow hole 102 and the second flow hole 104 of the fluid distribution section 100, the refrigerant can be evenly distributed to the multiple refrigerant flow paths 21 connected to the distribution space SD.

[0101] As described above, according to the heat exchanger 1 of the fourth embodiment, even when the fluid distribution section 100 is arranged in the connector member 36 of the inlet section 35, the same effects as those of the above-mentioned embodiments can be obtained from the same configuration and operation.

[0102] 10 , in the heat exchanger 1 according to the fourth embodiment, the fluid distribution section 100 is disposed in a connector member 36 located upstream in the flow direction from the inlet of the refrigerant inlet tank 30. That is, the fluid distribution section 100 is not limited to being attached to the inlet of the distribution space SD, and may also be disposed upstream in the flow direction from the inlet of the distribution space SD.

[0103] Fifth Embodiment Next, a fifth embodiment, which differs from the above-described embodiments, will be described with reference to Fig. 11. The heat exchanger 1 according to the fifth embodiment differs from the above-described embodiments in the way fluid flows inside the heat exchanger 1. Other configurations of the heat exchanger 1 according to the fifth embodiment (e.g., the refrigerant flow path 21, etc.) are the same as those of the above-described embodiments, and therefore will not be described again.

[0104] In the heat exchanger 1 according to the embodiment described above, when the refrigerant flows into the refrigerant inlet tank 30, it flows toward the refrigerant discharge tank 40 via the refrigerant flow path 21. Then, the refrigerant that flows into the collection space SA of the refrigerant discharge tank 40 flows out of the heat exchanger 1 and circulates through the refrigeration cycle.

[0105] The heat exchanger 1 according to the fifth embodiment employs a flow pattern of refrigerant different from that described in the above embodiment, such as a so-called "folded-back" flow pattern. When the folded-back flow pattern is employed, the heat exchanger 1 according to the fifth embodiment achieves uniform distribution of refrigerant among the multiple refrigerant flow paths 21.

[0106] First, the configuration related to the refrigerant flow in the heat exchanger 1 according to the fifth embodiment will be described with reference to the drawings. As in the above-described embodiments, the heat exchanger 1 according to the fifth embodiment is configured by stacking a plurality of plate members 10 in the Z-axis direction, and has a plurality of refrigerant flow paths 21, a first refrigerant tank 70, and a second refrigerant tank 80. The first refrigerant tank 70 is a storage section into which two-phase refrigerant flows from the refrigeration cycle, and corresponds to an example of a tank.

[0107] In the fifth embodiment, the first refrigerant tank 70 is arranged in the same manner as the refrigerant inlet tank 30 in the above-described embodiment. Unlike the refrigerant inlet tank 30 in the above-described embodiment, the first refrigerant tank 70 is partitioned into two at the middle section in the Z-axis direction, and is configured with a distribution space SD and a collection space SA.

[0108] The second refrigerant tank 80 is disposed opposite the first refrigerant tank 70 via the plurality of refrigerant flow paths 21, and is a storage section into which the refrigerant flows after flowing through the plurality of refrigerant flow paths 21. Unlike the refrigerant discharge tank 40 of the above-described embodiment, which is configured with a collection space SA, the second refrigerant tank 80 is configured with a collection space SA and a distribution space SD.

[0109] Therefore, the refrigerant flows through the distribution space SD of the first refrigerant tank 70, the plurality of refrigerant flow paths 21 constituting the upper portion of the heat exchange core unit 20, the collection space SA of the second refrigerant tank 80, and the distribution space SD of the second refrigerant tank 80 in that order. When the refrigerant flows into the distribution space SD of the second refrigerant tank 80, the refrigerant flows through the plurality of refrigerant flow paths 21 constituting the lower portion of the heat exchange core unit 20 and the collection space SA of the first refrigerant tank 70, and is discharged to the outside of the heat exchanger 1 through the discharge port 75. Therefore, in the fifth embodiment, the second refrigerant tank 80 also corresponds to an example of a tank.

[0110] In other words, in a folded-back type heat exchanger 1 such as the heat exchanger 1 according to the fifth embodiment, the refrigerant is collected and distributed inside the second refrigerant tank 80, and the flow of the refrigerant is folded back toward the first refrigerant tank 70.

[0111] Here, let us consider a case where the fluid distribution unit 100 is disposed on the inlet side of the tank, as in the above-described embodiment. As shown in Fig. 11, the distribution space SD of the first refrigerant tank 70 is disposed downstream in the refrigerant flow direction from the inlet of the first refrigerant tank 70. Therefore, based on the same theory as in the above-described embodiment, the fluid distribution unit 100 can evenly distribute the refrigerant to the multiple refrigerant flow paths 21 connected to the distribution space SD of the first refrigerant tank 70.

[0112] The structure corresponding to the inlet of the second refrigerant tank 80 is considered to be a connection portion with the multiple refrigerant flow paths 21 extending from the distribution space SD of the first refrigerant tank 70. The collection space SA of the second refrigerant tank 80 is located downstream in the flow direction of this connection portion. In the second refrigerant tank 80, the distribution space SD is located downstream in the flow direction of the collection space SA. Therefore, even if the fluid distribution unit 100 is located at the inlet of the second refrigerant tank 80, the effect of refrigerant contraction caused by the first flow holes 102 and the second flow holes 104 does not sufficiently reach the distribution space SD, and uniform distribution of the refrigerant to the multiple refrigerant flow paths 21 of the second refrigerant tank 80 cannot be ensured.

[0113] In view of the above points, the heat exchanger 1 of the fifth embodiment is a folded-back type heat exchanger that achieves uniform distribution of refrigerant in multiple refrigerant flow paths 21 in either of a pair of refrigerant tanks (e.g., the first refrigerant tank 70 and the second refrigerant tank 80).

[0114] 11 , in the heat exchanger 1 according to the fifth embodiment, a fluid distribution section 100 is disposed in the inlet section 35 of the first refrigerant tank 70. As in the above-described embodiments, the fluid distribution section 100 has a first flow hole 102 and a second flow hole 104. Therefore, in the heat exchanger 1 according to the fifth embodiment, the first flow hole 102 and the second flow hole 104 of the fluid distribution section 100 can be used to uniformly distribute the refrigerant to the refrigerant flow paths 21 connected to the distribution space SD of the first refrigerant tank 70.

[0115] A partition plate 14 is disposed at a middle position of the heat exchange core 20 of the heat exchanger 1 according to the fifth embodiment. A tank closing portion 14A is formed in the partition plate 14 at a position corresponding to the first refrigerant tank 70. The tank closing portion 14A divides the internal space of the first refrigerant tank 70 into two in the Z-axis direction.

[0116] Of the internal space of the first refrigerant tank 70, the space located in the positive direction of the Z axis relative to the tank closure portion 14A constitutes a distribution space SD of the first refrigerant tank 70. And, of the internal space of the first refrigerant tank 70, the space located in the negative direction of the Z axis relative to the tank closure portion 14A constitutes a collection space SA of the first refrigerant tank 70. As a result, the refrigerant flow in the heat exchanger 1 according to the fifth embodiment is a return type.

[0117] 11 , a fluid distribution section 100 is disposed in the middle section of the second refrigerant tank 80 of the heat exchanger 1 according to the fifth embodiment. The fluid distribution section 100 on the second refrigerant tank 80 side is formed integrally with the above-mentioned partition plate 14. Specifically, the fluid distribution section 100 on the second refrigerant tank 80 side is disposed at a position on the partition plate 14 corresponding to the second refrigerant tank 80, and has a first flow hole 102 and a second flow hole 104.

[0118] Therefore, the fluid distribution unit 100 is disposed at the boundary between the collection space SA and the distribution space SD in the internal space of the second refrigerant tank 80. The boundary between the collection space SA and the distribution space SD in the second refrigerant tank 80 corresponds to the inlet portion 35 of the distribution space SD in the second refrigerant tank 80.

[0119] As a result, when the refrigerant flows from the collection space SA to the distribution space SD in the internal space of the second refrigerant tank 80, it can pass through the fluid distribution part 100 having the first communication holes 102 and the second communication holes 104. As a result, similar to the above-described embodiment, the refrigerant can be evenly distributed to the multiple refrigerant flow paths 21 connected to the distribution space SD of the second refrigerant tank 80 by utilizing the first communication holes 102 and the second communication holes 104 of the fluid distribution part 100.

[0120] As described above, according to the heat exchanger 1 of the fifth embodiment, even if the fluid flow method inside the heat exchanger 1 is changed to a return method, the same effects as those of the above-mentioned embodiments can be obtained from the same configuration and operation.

[0121] That is, according to the heat exchanger 1 of the fifth embodiment, by arranging the fluid distribution section 100 in the middle part of the second refrigerant tank 80 (the boundary between the collection space SA and the distribution space SD), uniform distribution of the refrigerant in each refrigerant flow path 21 in the distribution space SD of the second refrigerant tank 80 can be achieved.

[0122] Sixth Embodiment Next, a sixth embodiment, which differs from the above-described embodiments, will be described with reference to Fig. 12. In the heat exchanger 1 according to the sixth embodiment, the shape of the fluid distribution section 100 differs from that of the above-described embodiments. Other components of the heat exchanger 1 according to the sixth embodiment (e.g., the heat exchange core section 20, etc.) are the same as those of the above-described embodiments, and therefore will not be described again.

[0123] Although the fluid distribution unit 100 according to the embodiment described above is configured using a flat plate member made of a thin plate, the present invention is not limited to this. For example, the central portion 101 and the peripheral portion 103 of the fluid distribution unit 100 may have different positional relationships with respect to the refrigerant flow direction.

[0124] 12, the fluid distribution section 100 may be configured so that the central portion 101 of the fluid distribution section 100 is located downstream in the refrigerant flow direction relative to the peripheral portion 103. By positioning the central portion 101, where the first communication holes 102 are formed, further downstream in the refrigerant flow, it is possible to supply the refrigerant further downstream in the flow direction in the distribution space SD.

[0125] The peripheral portion 103 may also be configured to be inclined so that the closer it is to the center point C of the fluid distribution portion 100, the more downstream in the refrigerant flow direction it is located. This allows the direction of the contracted flow of the second flow holes 104 formed in the peripheral portion 103 to have a component in the direction away from the central axis of the distribution space SD, thereby improving the refrigerant distribution performance to the refrigerant flow paths 21 on the upstream side of the distribution space SD.

[0126] As described above, according to the heat exchanger 1 of the sixth embodiment, even if the shape of the fluid distribution section 100 is changed, the same effects as those of the above-mentioned embodiments can be obtained from the same configuration and operation.

[0127] Seventh Embodiment Next, a seventh embodiment, which differs from the above-described embodiments, will be described with reference to Fig. 13. In the heat exchanger 1 according to the seventh embodiment, the configuration of the opening edges of the first flow holes 102 and the second flow holes 104 in the fluid distribution section 100 differs from that of the above-described embodiments. Other configurations of the heat exchanger 1 according to the seventh embodiment (e.g., the heat exchange core section 20, etc.) are the same as those of the above-described embodiments, and therefore will not be described again.

[0128] In the fluid distribution unit 100 according to the embodiment described above, the first and second flow holes 102, 104 are formed by punching holes in the thin plate member 10. However, the present invention is not limited to this. For example, as shown in Fig. 13, guide protrusions 110 that protrude downstream in the refrigerant flow direction may be formed on the opening edges of the first and second flow holes 102, 104.

[0129] Forming the guide protrusions 110 on the opening edges of the first and second flow holes 102, 104 makes it possible to adjust the direction of contraction of the refrigerant that has flowed through the first and second flow holes 102, 104. As a result, according to the heat exchanger 1 of the seventh embodiment, the first and second flow holes 102, 104 of the fluid distribution section 100 can be used to distribute the refrigerant uniformly with higher precision in the refrigerant flow paths 21 connected to the distribution space SD.

[0130] As described above, according to the heat exchanger 1 of the seventh embodiment, even if the shape of the opening edges of the first flow hole 102 and the second flow hole 104 in the fluid distribution section 100 is changed, the same effects as those of the above-mentioned embodiments can be obtained from the same configuration and operation.

[0131] Eighth Embodiment Next, an eighth embodiment, which differs from the above-described embodiments, will be described with reference to Fig. 14. In the heat exchanger 1 according to the eighth embodiment, the shapes of the first and second flow holes 102 and 104 in the fluid distribution section 100 differ from those in the above-described embodiments. Other configurations of the heat exchanger 1 according to the eighth embodiment (e.g., the heat exchange core section 20, etc.) are the same as those in the above-described embodiments, and therefore will not be described again.

[0132] In the fluid distribution section 100 according to the above embodiment, the opening shapes of the first and second flow holes 102, 104 are circular, but are not limited to this. Various shapes can be adopted for the opening shapes of the first and second flow holes 102, 104 as long as the openings allow refrigerant to flow through the components of the fluid distribution section 100. For example, as shown in FIG. 14 , the opening shapes of the first and second flow holes 102, 104 may be rectangular with rounded corners.

[0133] As described above, according to the heat exchanger 1 of the eighth embodiment, even if the shapes of the first flow hole 102 and the second flow hole 104 in the fluid distribution section 100 are changed, the same effects as those of the above-mentioned embodiments can be obtained from the same configuration and operation.

[0134] The present disclosure is not limited to the above-described embodiments, and various modifications can be made as follows within the scope of the present disclosure.

[0135] In the above-described embodiment, the heat exchanger according to the present disclosure is applied to a chiller that exchanges heat between a refrigerant circulating through a refrigeration cycle and a coolant circulating through a coolant circuit, but the present disclosure is not limited to this embodiment. The technology according to the present disclosure can be applied to various heat exchangers as long as they are heat exchangers that handle two-phase fluids including gas and liquid phases. For example, the heat exchanger according to the present disclosure can be used as an evaporator that absorbs heat from outside the heat exchanger (e.g., air blown into a vehicle cabin) and evaporates the refrigerant circulating through a refrigeration cycle.

[0136] Furthermore, in the above-described embodiment, the heat exchanger 1 is configured by stacking multiple plate members 10 in the stacking direction Z, but this is not limited to this configuration. The heat exchanger 1 according to the present disclosure can adopt various configurations as long as it has a tank (e.g., a refrigerant inlet tank 30, etc.) into which a two-phase fluid flows and multiple refrigerant flow paths 21 connected to the distribution space SD of the tank and stacked in the stacking direction Z. For example, the technology according to the present disclosure may be applied to a heat exchanger adopting a tank-and-tube configuration. Furthermore, the center of gravity of the cross-sectional shape of the distribution space may be used as the center point of the cross-sectional shape of the distribution space.

[0137] The heat exchanger disclosed in this specification has the following features: (Item 1) A heat exchanger having a plurality of fluid flow paths (21) stacked in a predetermined stacking direction, through which a fluid including a gas phase and a liquid phase flows, and a tank (30, 70, 80) extending in the stacking direction of the plurality of fluid flow paths and connected to the plurality of fluid flow paths, wherein the tank has a distribution space (SD) for distributing a fluid to the plurality of fluid flow paths and an inlet section (35) through which a fluid flows into the distribution space, and a fluid distribution section (100) for controlling the flow of a fluid to the plurality of stacked fluid flow paths is arranged on the side of the inlet section of the distribution space in the tank, and the fluid distribution section has: a first communication hole (102) for guiding a fluid to the plurality of fluid flow paths connected to the distribution space at a portion downstream in the flow direction of the fluid flowing through the distribution space; and a second communication hole (104) for guiding a fluid to the plurality of fluid flow paths connected to the distribution space at a portion upstream in the flow direction of the fluid flowing through the distribution space. 1. A heat exchanger according to claim 1, wherein the first flow holes are arranged in a central portion (101) of the fluid distribution section that is configured within a predetermined range centered on a center point (C) of the cross-sectional shape of the distribution space, and the second flow holes are arranged in a peripheral portion (103) of the fluid distribution section that is configured within an area between an inner wall surface of the distribution space and the central portion. (Item 2) A heat exchanger according to claim 1, wherein the plurality of fluid flow paths and the tank in the heat exchanger are configured by joining plate-shaped plate members (10) that are stacked in the stacking direction, the fluid flow paths are configured between adjacent plate members that are stacked, the distribution space of the tank extends in the stacking direction using openings (11A, 12A) formed at predetermined positions in the plate members, and communication portions (37) that communicate the distribution space of the tank with each of the fluid flow paths are formed around the entire circumference of the tank.(Item 3) The heat exchanger according to item 1 or 2, wherein the first circulation hole is formed in the central portion of the fluid distribution section at a central position of a cross-sectional shape of the distribution space, and the second circulation holes are formed in the peripheral portion of the fluid distribution section at a predetermined distance (d) from the central point, and the first circulation hole and the second circulation holes in the fluid distribution section are formed so that an index value (γ) derived by the following mathematical formula 1 is greater than 0.4 and less than 1.1.

[0138]

[0139] where, in Equation 1, Aa is the opening area of ​​the first flow hole, Ab is the total opening area of ​​the second flow holes, and At is the cross-sectional area of ​​the distribution space of the tank. D is the diameter of the distribution space of the tank, and d is the position of the second flow hole in the cross section of the distribution space of the tank. (Item 4) The heat exchanger according to any one of Items 1 to 3, wherein the interior of the tank is formed by the distribution space (SD) serving all of the fluid flow paths arranged in a stack, and the fluid distribution unit is disposed in the inlet unit located at the most upstream part in the fluid flow direction inside the tank. (Item 5) The heat exchanger according to Item 4, wherein a connector member (36) for connecting a supply pipe for supplying fluid into the tank is attached to the inlet unit of the tank, and the fluid distribution unit is disposed in the fluid flow path of the connector member. (Item 6) The heat exchanger according to any one of Items 1 to 3, wherein the tank has an interior including a collection space (SA) for collecting fluids that have flowed through the plurality of fluid flow paths, and a distribution space (SD) for the fluid that has circulated through the collection space, and the fluid distribution section is disposed at the inlet section through which the fluid that has flowed out of the collection space flows into the distribution space.

[0140] Although the present disclosure has been described with reference to the embodiments, it is understood that the present disclosure is not limited to the embodiments or structures. The present disclosure also encompasses various modifications and equivalent modifications. In addition, various combinations and forms, including only one element, more than one element, or less than one element, are also within the scope and spirit of the present disclosure.

Claims

1. A heat exchanger having a plurality of fluid flow paths (21) stacked in a predetermined stacking direction, through which a fluid including a gas phase and a liquid phase flows, and a tank (30, 70, 80) extending in the stacking direction of the plurality of fluid flow paths and connected to the plurality of fluid flow paths, wherein the tank has a distribution space (SD) for distributing a fluid to the plurality of fluid flow paths, and an inlet portion (35) through which a fluid flows into the inside of the distribution space, and a fluid distribution portion (100) for controlling a flow of a fluid to the plurality of stacked fluid flow paths is arranged on the side of the inlet portion of the distribution space in the tank, and the fluid distribution portion has a first circulation hole (102) for guiding a fluid to the plurality of fluid flow paths connected to a portion downstream in the flow direction of the fluid flowing through the distribution space, and a second circulation hole (104) for guiding a fluid to the plurality of fluid flow paths connected to the distribution space at a portion upstream in the flow direction of the fluid flowing through the distribution space, The first flow hole is arranged in a central portion (101) of the fluid distribution section, the central portion being defined by a predetermined range centered on a center point (C) in the cross-sectional shape of the distribution space, and the second flow hole is arranged in a peripheral portion (103) of the fluid distribution section, the peripheral portion being defined by a region between an inner wall surface of the distribution space and the central portion.

2. A heat exchanger as described in claim 1, wherein the plurality of fluid flow paths and the tank in the heat exchanger are formed by stacking and joining plate members (10) formed in a plate shape in the stacking direction, the fluid flow paths are formed between adjacent plate members arranged in a stacked manner, the distribution space of the tank extends in the stacking direction using openings (11A, 12A) formed at predetermined positions in the plate members, and communication portions (37) connecting the distribution space of the tank with each of the fluid flow paths are formed around the entire circumference of the tank.

3. The heat exchanger of claim 1, wherein the first through hole is formed in the central portion of the fluid distribution section at a central position of the cross-sectional shape of the distribution space, and the second through holes are formed in a plurality of portions in the peripheral portion of the fluid distribution section at a predetermined distance (d) from the central point, and the first through hole and the plurality of second through holes in the fluid distribution section are formed so that an index value (γ) derived by the following formula 1 is greater than 0.4 and smaller than 1.

1. In the formula 1, Aa is the opening area of ​​the first flow hole, Ab is the total opening area of ​​the second flow holes, At is the cross-sectional area of ​​the distribution space of the tank, D is the diameter of the distribution space of the tank, and d is the position of the second flow hole in the cross section of the distribution space of the tank.

4. A heat exchanger as described in any one of claims 1 to 3, wherein the inside of the tank is constituted by a distribution space (SD) which covers all of the fluid flow paths arranged in a stacked manner, and the fluid distribution section is arranged at the inlet section which is located at the most upstream part in the direction of fluid flow inside the tank.

5. A heat exchanger as described in claim 4, wherein a connector member (36) for connecting a supply pipe for supplying a fluid into the tank is attached to the inlet portion of the tank, and the fluid distribution portion is disposed within the fluid flow path in the connector member.

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