Heat exchanger

Abstract

To provide a heat exchanger which has improved uniformity when distributing a two phase fluid which has flowed in a tank into a plurality of stacked fluid flow passages.SOLUTION: A heat exchanger 1 includes: a plurality of refrigerant flow passages 21; and a refrigerant inflow tank 30. The plurality of refrigerant flow passages 21 are stacked in a predetermined stacking direction Z, and a refrigerant including a gas phase and a liquid phase flows. The refrigerant inflow tank 30 extends in the stacking direction of the plurality of refrigerant flow passages 21, and is connected to the plurality of refrigerant flow passages 21. On an inflow port part 35 side of a distribution space SD in the refrigerant inflow tank 30, a fluid distribution part 100 including a first circulation hole 102 and a second circulation hole 104 is arranged. The first circulation hole 102 is arranged at a central part 101 constituted by a predetermined range centered around a center point C in a cross-sectional shape of the distribution space SD, in the fluid distribution part 100. The second circulation hole 104 is arranged at a peripheral part 103 comprising a region between an internal wall surface of the distribution space SD and the central part 101, in the fluid distribution part 100.SELECTED DRAWING: Figure 7

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger having a tank into which a fluid having a gas phase and a liquid phase flows, and a plurality of fluid flow paths arranged in a stack. [Background technology]

[0002] Conventionally, a heat exchanger is configured with a tank that distributes and collects a refrigerant, and multiple refrigerant flow paths through which the refrigerant flows from the tank, and the multiple refrigerant flow paths are stacked in a predetermined direction in which the tank extends. In such a heat exchanger, in order to improve the heat exchange performance, the temperature distribution in the multiple refrigerant flow paths that are stacked is important, and in order to achieve this, it is desirable to distribute the fluid uniformly to each fluid flow path when distributing the fluid from the tank to the multiple fluid flow paths.

[0003] However, in reality, when fluid flows inside the tank toward multiple fluid flow paths arranged in a stacked configuration, the fluid may be affected by inertial forces acting on the fluid, resulting in uneven distribution of the fluid.

[0004] 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 distribution of the fluid to each fluid flow path closer to a uniform state. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Patent Publication No. 2021-25764 Summary of the Invention [Problem to be solved by the invention]

[0006] In a heat exchanger, the total number of fluid flow paths arranged in a stack may increase, or the manner in which the fluid flows into the tank may change. Depending on the manner of such changes, it is expected that the technology of Patent Document 1 may not be able to achieve uniform distribution of the fluid to each fluid flow path.

[0007] For example, if the total number of stacked fluid flow paths is increased, the tank will extend along the stacking direction, and it is expected that even if a swirl component is imparted by a swirl vane disposed at the inlet of the tank, the flow of the fluid flowing in from the inlet will not reach the fluid flow paths disposed downstream.

[0008] Furthermore, when the connection mode of the supply flow path of the fluid connected to the inlet of the tank is changed and the tank is connected from the side, the inertia acting on the fluid flowing in from the inlet differs before and after the change in the path of the supply flow path.Even if the flow of the fluid is biased toward the inlet side due to the action of inertial force, the refrigerant flows in biased toward the inlet side due to the inertia, so 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.

[0009] 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 a plurality of fluid flow paths that are arranged in a stacked manner. [Means for solving the problem]

[0010] A heat exchanger according to one aspect of the present disclosure is a heat exchanger having a plurality of fluid flow paths (21) and a tank (30, 70, 80). 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 (SD) for distributing a fluid to the plurality of fluid flow paths, and an inlet portion (35) through which the fluid flows into the inside of the distribution space. A fluid distribution portion (100) for controlling the flow of the fluid to the plurality of stacked fluid flow paths is arranged on the inlet portion side of the distribution space in the tank.

[0011] The fluid distribution section has a first through hole (102) and a second through hole (104). The first through 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 through hole guides the fluid to a plurality of fluid flow paths connected to the distribution space at an upstream portion of the distribution space in the flow direction of the fluid. The first through hole is disposed in a central portion (101) of the fluid distribution section that is formed of a predetermined range centered on a center point (C) in the cross-sectional shape of the distribution space. The second through hole is disposed in a peripheral portion (103) of the fluid distribution section that is formed of a region between the inner wall surface of the distribution space and the central portion.

[0012] Therefore, according to the heat exchanger according to one aspect of the present disclosure, the fluid flowing into the distribution space of the tank can be distributed to a plurality of fluid flow paths arranged in the stacking direction through the fluid distribution section. A first circulation hole is formed in the center of the fluid distribution section, and the fluid can be guided to a plurality of fluid flow paths connected to a downstream portion of the distribution space in the flow direction by passing through the first circulation hole. In addition, a second circulation hole is formed in the periphery of the fluid distribution section, and the fluid can be guided to a plurality of fluid flow paths connected to the distribution space in the upstream portion of the flow direction by passing through the second circulation hole. In other words, the heat exchanger can improve the uniformity of the distribution of the fluid to the plurality of fluid flow paths connected to the distribution space by causing the fluid to flow out to the distribution space through the first circulation hole and the second circulation hole of the fluid distribution section.

[0013] In addition, the reference symbols in parentheses for each means described in this column and in the claims indicate the correspondence with the specific means described in the embodiments described later. [Brief description of the drawings]

[0014] [Figure 1] FIG. 2 is a front view of the heat exchanger according to the first embodiment. [Diagram 2] FIG. 2 is a plan view of the heat exchanger according to the first embodiment. [Diagram 3] FIG. 4 is an explanatory diagram showing a refrigerant distribution structure in a heat exchanger. [Figure 4] 2 is a cross-sectional view showing a refrigerant inlet tank of the heat exchanger according to the first embodiment. FIG. [Diagram 5] FIG. 2 is a plan view showing the configuration of a fluid distribution section according to the first embodiment. [Figure 6] 4 is a graph showing refrigerant distribution characteristics by the fluid distribution portion according to the first embodiment. [Figure 7] FIG. 3 is an explanatory diagram showing a distribution mode of a refrigerant by a fluid distribution portion of the first embodiment. [Figure 8] FIG. 11 is a plan view showing the configuration of a fluid distribution section of a heat exchanger according to a second embodiment. [Figure 9] FIG. 11 is a cross-sectional view showing a fluid distribution section of a heat exchanger according to a third embodiment. [Figure 10] FIG. 11 is a cross-sectional view showing a fluid distribution section of a heat exchanger according to a fourth embodiment. [Figure 11] FIG. 13 is an explanatory diagram showing the arrangement of a fluid distribution section in a heat exchanger according to a fifth embodiment. [Figure 12] FIG. 13 is a cross-sectional view showing a fluid distribution section of a heat exchanger according to a sixth embodiment. [Figure 13] FIG. 13 is a cross-sectional view showing a fluid distribution section of a heat exchanger according to a seventh embodiment. [Figure 14] FIG. 13 is a plan view showing a fluid distribution section of a heat exchanger according to an eighth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0015] Hereinafter, a number of embodiments for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, the same reference numerals may be used to designate parts corresponding to matters described in the preceding embodiment, and duplicated descriptions may be omitted. In each embodiment, when only a part of the configuration is described, other embodiments described previously may be applied to the other parts of the configuration. In addition to combinations of parts that are specifically indicated as being possible in each embodiment, it is also possible to partially combine embodiments even if not indicated, 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 each drawing are denoted by the same reference numerals as much as possible, and duplicated description 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 system mounted on a vehicle and the cooling water.

[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 constituted by some 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 part 20 of the heat exchanger 1 is formed to have a substantially rectangular cross-sectional shape perpendicular to the stacking direction Z. Hereinafter, the longitudinal direction and the lateral direction of the heat exchange core part 20 are 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 diagonally opposite corners of the four corners of the plate members 10. 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 refrigerant in two phases, gas and liquid, circulating through the refrigeration cycle flows in. 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 that are stacked in the Z-axis direction in the heat exchange core section 20. Therefore, the internal space of the refrigerant inlet tank 30 is configured 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 that has flowed through the multiple refrigerant flow paths 21 that constitute the heat exchange core section 20 flows. 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 cooling water inlet tank 50 is a storage section into which the cooling water circulating through the cooling water circuit flows in. The cooling water inlet tank 50 has a cylindrical internal space extending in the Z-axis direction, similar to the refrigerant inlet tank 30. A plurality of cooling water flow paths stacked in the Z-axis direction in the heat exchange core section 20 are connected to the internal space of the cooling water inlet tank 50. The cooling water that flows into the cooling water inlet tank 50 is distributed to the plurality of cooling water flow paths.

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

[0027] As described above, in the heat exchanger 1 according to the first embodiment, heat exchange is performed 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 of the coolant, and the coolant can be cooled by the heat absorption effect of the refrigerant.

[0028] 3, the heat exchange core portion 20 has 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 periphery 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 burring portion 11A formed by burring. The burring portion 11A forms a circular opening centered on the central axis of the refrigerant inlet tank 30, and is configured by forming the opening edge of the opening to protrude cylindrically in the positive direction of the Z axis. Therefore, the burring portion 11A corresponds to an example of an opening. A protruding portion 11C protruding in the negative direction of the Z axis is formed in a portion of the outer plate 11 corresponding to the base end of the burring portion 11A.

[0031] The inner plate 12, like the outer plate 11, is a plate-like member having a substantially rectangular cross-sectional shape perpendicular to the stacking direction Z. The inner plate 12 is disposed inside the protruding portion 11B of the outer plate 11 and between adjacent outer plates 11, and is 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 direction of the Z axis 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 direction of the Z axis 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 cooling water flow path. For example, offset fins can be used as the coolant fins 21F and the cooling water fins. The coolant fins 21F increase the heat transfer area for the coolant flowing through the coolant flow path 21. The cooling water fins increase the heat transfer area for the cooling water flowing through the cooling water flow path.

[0034] The inner plate 12 is provided with a burring portion 12A formed by burring processing at a portion corresponding to the burring portion 11A of the outer plate 11. The burring portion 12A forms a circular opening centered on the central axis of the refrigerant inflow tank 30, and is configured by forming the opening edge of the opening to protrude cylindrically in the negative direction of the Z axis. The burring portion 12A corresponds to an example of an opening, similar to the burring portion 11A. A protrusion 12C protruding in the positive direction of the Z axis is formed at the base end of the burring portion 12A in 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 portion 11A of the outer plate 11 and the burring portion 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 portion 35 is disposed in the positive direction of the Z axis of the burring portion 11A and the burring portion 12A. The inlet portion 35 according to the first embodiment includes an inlet for allowing the refrigerant including gas and liquid phases to flow from the refrigeration cycle into the internal space of the refrigerant inlet tank 30, and has a connector member 36. The connector member 36 is a connector that is connected to the refrigeration cycle and connects the refrigerant inlet pipe for supplying the refrigerant including gas and liquid phases to the inlet. Therefore, the inlet portion 35 is located at the most upstream portion of the internal space of the refrigerant inlet tank 30 in the direction of refrigerant flow.

[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] In addition, the protruding portion 11C of the outer plate 11 and the protruding portion 12C of the inner plate 12 are joined to each other to separate the cooling water flow path and 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 disposed at a predetermined interval. In other words, the coolant flow path 21 formed between the outer plate 11 and the inner plate 12 communicates with each other via a 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 to flow into multiple refrigerant flow paths 21.

[0041] 3 and 4, the refrigerant inlet tank 30 has a communication part 37, and the cylindrical part of the burring part 11A and the cylindrical part of the burring part 12A form a peripheral wall 38 of the refrigerant inlet tank 30. Therefore, the communication part 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 of the first embodiment, the refrigerant that has flowed into the refrigerant inlet tank 30 can be discharged into each refrigerant flow path 21 through the communicating portion 37 formed around the entire circumference of the refrigerant inlet tank 30.

[0043] Here, let us consider a case where the communication part 37 is formed in a part of the circumferential direction of the refrigerant inlet tank 30 having a cylindrical internal space. In the flow of the refrigerant flowing through the refrigerant inlet tank 30, in the part where the communication part 37 is formed, it is considered that the refrigerant flows out to the refrigerant flow path 21 via the communication part 37. On the other hand, in the flow of the refrigerant flowing through the part where the communication part 37 is not formed, it flows through a position away from the communication part 37 and is considered to be in an environment where it is easier for the refrigerant to flow downstream, so it is considered that the refrigerant flows directly 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, which is likely to impair control over the distribution of refrigerant to the multiple refrigerant flow paths 21.

[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 the refrigerant inside the refrigerant inlet tank 30. As a result, the heat exchanger 1 can suppress the occurrence of a circulating flow of the refrigerant in the internal space of the refrigerant inlet tank 30, and ensure the controllability of the distribution of the refrigerant to the multiple refrigerant flow paths 21.

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

[0047] The fluid distribution part 100 is located on the inlet part 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, since the fluid distribution part 100 is formed on the top plate 13, the number of parts can be reduced compared to the case where the fluid distribution part 100 is configured as a separate member.

[0048] The fluid distribution part 100 corresponds to a cross-sectional shape perpendicular to the Z axis of the distribution space SD of the refrigerant inflow tank 30, and is formed into a circle 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 inflow tank 30 (i.e., the opening diameter of the burring parts 11A and 12A).

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

[0050] Here, the central portion 101 of the fluid distribution portion 100 is a portion that is determined centered on a central point C located on the central axis of the distribution space SD. The central portion 101 of the fluid distribution portion 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 portion 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 a 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. 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, as shown in FIG.

[0052] 5, the outer edge of the central portion 101 in 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 in 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 of the refrigerant toward the downstream side in the flow direction in the distribution space SD.

[0054] As described above, since the fluid distribution section 100 is formed in a part of the top plate 13, the first communication hole 102 is configured by forming a punched hole in the thin top plate 13. By configuring the first communication hole 102 with a punched hole, the flow path length as a 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.

[0055] The opening area of ​​the first through hole 102 according to the first embodiment is determined so that an index value γ calculated by Equation 1 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 part 100 in the peripheral part 103 of the fluid distribution part 100. As shown in Fig. 5, six second communication holes 104 are formed in the peripheral part 103 of the fluid distribution part 100 according to the first embodiment. The second communication holes 104 contract the flow of the refrigerant that has flowed into the inlet part 35 of the distribution space SD in the refrigerant inlet tank 30, and guide it to the refrigerant flow path 21 on the upstream side in the flow direction of the distribution space SD.

[0057] Like the first communication holes 102, each of the second communication holes 104 is formed by forming a punched hole in the thin top plate 13. By forming the second communication holes 104 by punched holes, the flow path length as a 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 of the second through holes 104 is disposed 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 portion 100. In this case, the center position of each of the second through holes 104 in the fluid distribution portion 100 and the center point C are referred to as a second through 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 sending the refrigerant by the fluid distribution part 100 to the downstream side in the flow direction in the distribution space SD.

[0061]

number

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

[0064] In the second term of the above formula 1, Aa+Ab is used. Aa+Ab means the total opening area in the fluid distribution section 100. At means the cross-sectional area of ​​the distribution space SD in the refrigerant inflow tank 30, and corresponds to the area of ​​the fluid distribution section 100 itself. In the first embodiment, the diameter of the refrigerant inflow 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. In addition, 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 circulation hole 102 and the second circulation hole 104.

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

[0066] When the index value γ is experimentally calculated based on the above-mentioned formula 1, it is found to have the characteristics shown in Fig. 6. Note that the performance ratio in Fig. 6 indicates the degree of bias when distributing the fluid to the multiple refrigerant flow paths 21 arranged in a stacked configuration, and the more evenly the fluid is distributed to the multiple 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 FIG. 6, for the fluid distribution section 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 arranged in a stack 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 flow of the refrigerant by the fluid distribution section 100 is mostly directed upstream in the flow direction in the distribution space SD. The distribution of the refrigerant to the multiple refrigerant flow paths 21 constituting the heat exchange core section 20 becomes uneven, and the temperature distribution of the heat exchange core section 20 becomes poor, which is thought to result in a decrease in the heat exchange performance of the heat exchanger 1.

[0069] Moreover, 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 the fluid distribution section 100 having an index value γ greater than 1.1 is used, the flow of the refrigerant by the fluid distribution section 100 is directed mostly downstream in the flow direction in the distribution space SD. In this case as well, the distribution of the refrigerant to the multiple refrigerant flow paths 21 constituting the heat exchange core section 20 becomes uneven, and the temperature distribution of the heat exchange core section 20 becomes poor, which is thought to result in a decrease in the heat exchange performance of the heat exchanger 1.

[0070] 6, when the index value γ is 0.4 or more and 1.1 or less, the performance ratio of the fluid distribution section 100 indicates a value of 0.8 to 1.0. When the fluid distribution section 100 having the index value γ in the range of 0.4 to 1.1 is used, the flow of the refrigerant by the fluid distribution section 100 is uniformly guided from the upstream side to the downstream side in the flow direction in the distribution space SD. As a result, the refrigerant can be uniformly distributed to all the refrigerant flow paths 21 connected to the distribution space SD, and the temperature distribution of the heat exchange core section 20 is also uniform, so that the deterioration of the heat exchange performance of the heat exchanger 1 can be suppressed.

[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 of the refrigerant toward the downstream side in the flow direction in the distribution space SD.

[0072] Therefore, according to the heat exchanger 1 according to the first embodiment, as shown in Fig. 7, the two-phase refrigerant can be caused 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 part 100. This allows the two-phase refrigerant to be distributed to the refrigerant flow path 21 connected to the downstream side in the flow direction among the multiple refrigerant flow paths 21 arranged in a stack in the distribution space SD.

[0073] Moreover, the second communication holes 104 contract the flow of the refrigerant on the radially outer side of the distribution space SD (i.e., the inner wall surface side of the refrigerant inlet tank 30) and guide it to the refrigerant flow path 21 on the upstream side in the flow direction in the distribution space SD. This makes it possible to distribute the two-phase refrigerant to the refrigerant flow path 21 connected to 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 circulation holes 102 and the second circulation holes 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 a cylindrical portion of the burring portion 11A and a cylindrical portion of the burring portion 12A. The communication portion 37 is formed by a 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] For this reason, each communication part 37 of the refrigerant inlet tank 30 is connected to the refrigerant flow passage 21 around the entire circumference of the refrigerant inlet tank 30. Therefore, when flowing from the refrigerant inlet tank 30 into the refrigerant flow passage 21, the two-phase refrigerant flows radially around the entire circumference of the distribution space SD and flows into the refrigerant flow passage 21. As a result, according to the heat exchanger 1, the flow of the two-phase refrigerant can be caused to flow into each refrigerant flow passage 21 without being biased inside the distribution space SD, and the effect of the flow of the two-phase refrigerant in 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 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 satisfies a predetermined numerical condition. The index value γ indicates the distribution characteristic of the refrigerant to the multiple refrigerant flow paths 21 arranged in a stacked manner in the distribution space SD, and a range of the index value γ of 0.4 to 1.1 indicates a state in which the refrigerant is distributed uniformly to the multiple refrigerant flow paths 21.

[0078] In other words, in the heat exchanger 1 of the first embodiment, the details of the first circulation hole 102 and the multiple second circulation holes 104 are determined so that the index value γ calculated by formula 1 is in the range of 0.4 to 1.1, thereby making it possible to evenly distribute the refrigerant to the multiple 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 section 35 of the refrigerant inlet tank 30 formed by the distribution space SD. Therefore, the heat exchanger 1 can distribute the refrigerant evenly to all the refrigerant flow paths 21 connected to the refrigerant inlet tank 30, and can uniform the temperature distribution of the heat exchange core section 20 and suppress deterioration of the heat exchange performance.

[0080] As described above, in the heat exchanger 1 of 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 in the circumferential direction 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 arranged in a stack in the distribution space SD by utilizing the first circulation holes 102 and the second circulation holes 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 communicates with the refrigerant flow paths 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 paths 21, the two-phase refrigerant flows radially around the entire circumference of the distribution space SD and flows into the refrigerant flow paths 21. As a result, according to the heat exchanger 1, the flow of the two-phase refrigerant can flow into each refrigerant flow path 21 without being biased inside the distribution space SD, and the effect of the flow of the two-phase refrigerant in the distribution space SD on uniform distribution can be suppressed.

[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 multiple second through holes 104 are appropriately determined, and uniform distribution of the refrigerant to the multiple refrigerant flow paths 21 in the distribution space SD can be realized.

[0084] 4 and 7, the inside of the refrigerant inlet tank 30 is configured as a distribution space SD to which all the refrigerant flow paths 21 constituting the heat exchange core section 20 and arranged in a stacked manner are connected. The fluid distribution section 100 is disposed on the inlet section 35 side of the refrigerant inlet tank 30, and the inlet section 35 is located at the most upstream part in the direction of fluid flow inside the refrigerant inlet tank 30. Therefore, according to the heat exchanger 1 according to the first embodiment, the refrigerant can be evenly distributed from the refrigerant inlet tank 30 to all the refrigerant flow paths 21 constituting the heat exchange core section 20, and a decrease in the heat exchange efficiency of the heat exchanger 1 can be suppressed.

[0085] Second embodiment Next, a second embodiment different from the above-mentioned 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 through holes 102 and the second through holes 104 in the fluid distribution section 100 are different from those of the above-mentioned first embodiment. Other configurations (e.g., the heat exchange core section 20, etc.) in the heat exchanger 1 according to the second embodiment are similar to those of the above-mentioned first embodiment, so repeated description will be omitted.

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

[0087] Moreover, twelve second through holes 104 are formed in the peripheral portion 103 of the fluid distribution portion 100 according to the second embodiment. The second through 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 through holes 104 according to the second embodiment are composed of six second through holes arranged in the peripheral portion 103 so that the distance from the center point C is a predetermined distance, and six second through holes arranged so that the distance from the center point C is even. The six second through holes 104 that are the same distance from the center point C are all arranged evenly in the circumferential direction at a predetermined interval in the peripheral portion 103.

[0088] In the fluid distribution section 100 according to the second embodiment, each of the first communication holes 102 contracts the flow of the refrigerant in the central portion of the distribution space SD, increasing the flow velocity in the distribution space SD toward the downstream side in the flow direction, as in the first embodiment. Also, each of the second communication holes 104 according to the second embodiment contracts the flow of the refrigerant on the radially outer side of the distribution space SD (i.e., the inner wall surface side of the refrigerant inlet tank 30) and guides 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 circulation holes 102 and the second circulation holes 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 state 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 uniformly distribute the refrigerant to the refrigerant flow paths 21 arranged in a stacked manner 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, it is possible to obtain the same functional effects as those of the above-mentioned embodiment due to the common configuration and operation.

[0092] Third embodiment Next, a third embodiment different from the above-mentioned embodiment will be described with reference to Fig. 9. In the heat exchanger 1 according to the third embodiment, the connection mode of the refrigerant inlet pipe 35A to the inlet portion 35 is different from that of the above-mentioned embodiment. Other configurations (e.g., the heat exchange core portion 20, etc.) in the heat exchanger 1 according to the third embodiment are similar to those of the above-mentioned embodiment, so repeated description will be omitted.

[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 portion 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 the upstream side of the inlet portion 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 portion 35 of the heat exchanger 1 according to the third embodiment. Therefore, in the third embodiment, the refrigerant flows inside the refrigerant inlet pipe 35A along a direction perpendicular to the Z axis, and then flows along the Z axis direction from just upstream of the inlet portion 35. Therefore, in the second embodiment, the refrigerant flows along the Z axis direction from the inlet portion 35 to the inside of the distribution space SD.

[0095] The fluid distribution part 100 according to the third embodiment is attached to the inlet part 35 of the refrigerant inlet tank 30 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 hole 102 and the second circulation hole 104 of the fluid distribution part 100.

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

[0097] (Fourth embodiment) Next, a fourth embodiment different 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 is different from that of the above-described embodiments. Other configurations (e.g., the outer plate 11, the inner plate 12, etc.) in the heat exchanger 1 according to the fourth embodiment are similar to those of the above-described embodiments, and therefore will not be described again.

[0098] In the above-described embodiment, the fluid distribution part 100 is configured as a part of the top plate 13, and is disposed at the inlet part 35 of the distribution space SD. As shown in Fig. 10, the fluid distribution part 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 embodiment.

[0099] The fluid distribution unit 100 according to the fourth embodiment is attached inside 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 the refrigerant from the refrigerant inlet pipe 35A to 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 the refrigerant toward the inside of the distribution space SD via the connector member 36 and the inlet, by the first circulation hole 102 and the second circulation hole 104.

[0100] Therefore, in the heat exchanger 1 of 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, it is possible to obtain the same functional effects as those of the above-mentioned embodiments due to the 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 be disposed upstream in the flow direction from the inlet of the distribution space SD.

[0103] Fifth embodiment Next, a fifth embodiment different from the above-described embodiments will be described with reference to Fig. 11. In the heat exchanger 1 according to the fifth embodiment, the fluid circulation system inside the heat exchanger 1 is different from that of the above-described embodiments. Other configurations (e.g., refrigerant flow path 21, etc.) in the heat exchanger 1 according to the fifth embodiment are similar to 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 flow of the refrigerant in the heat exchanger may be different from that described in the above embodiment, and is known as a turn-around type. The heat exchanger 1 according to the fifth embodiment realizes uniform distribution of the refrigerant to the multiple refrigerant flow paths 21 when the turn-around type is adopted.

[0106] First, the configuration related to the flow of refrigerant 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 the two-phase refrigerant that flows in from the refrigeration cycle flows, and corresponds to an example of a tank.

[0107] In the fifth embodiment, the first refrigerant tank 70 is arranged similarly to 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 part in the Z-axis direction, and is composed of a distribution space SD and a collection space SA.

[0108] The second refrigerant tank 80 is disposed at a position facing the first refrigerant tank 70 via the multiple refrigerant flow paths 21, and is a storage section into which the refrigerant that has flowed through the multiple refrigerant flow paths 21 flows. The second refrigerant tank 80 is configured with a collection space SA and a distribution space SD, unlike the refrigerant discharge tank 40 of the above-mentioned embodiment that is configured with a collection space SA.

[0109] Therefore, the flow of refrigerant in the heat exchanger 1 according to the fifth embodiment is in the order of the distribution space SD of the first refrigerant tank 70, the multiple refrigerant flow paths 21 constituting the upper part 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. When the refrigerant flows into the distribution space SD of the second refrigerant tank 80, the refrigerant flows in the order of the multiple refrigerant flow paths 21 constituting the lower part 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 from 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 of the fifth embodiment, refrigerant is collected and distributed inside the second refrigerant tank 80, and the flow of refrigerant is folded back toward the first refrigerant tank 70.

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

[0112] The configuration corresponding to the inlet of the second refrigerant tank 80 is considered to be a connection part 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 arranged downstream in the flow direction of this connection part. In the second refrigerant tank 80, the distribution space SD is arranged downstream in the flow direction of the collection space SA. Therefore, even if the fluid distribution part 100 is arranged at the inlet of the second refrigerant tank 80, the effect of the contraction of the refrigerant by the first circulation hole 102 and the second circulation hole 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-mentioned 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 at the inlet section 35 of the first refrigerant tank 70. The fluid distribution section 100 has a first circulation hole 102 and a second circulation hole 104, as in the above-described embodiments. Therefore, in the heat exchanger 1 according to the fifth embodiment, the first circulation hole 102 and the second circulation hole 104 of the fluid distribution section 100 can be used to uniformly distribute the refrigerant with respect to the refrigerant flow path 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 unit 20 of the heat exchanger 1 according to the fifth embodiment. A tank closing portion 14A is formed at a position of the partition plate 14 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 with respect to the tank closing 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 with respect to the tank closing 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 turn-back type.

[0117] 11, a fluid distribution section 100 is disposed in a 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 communication hole 102 and a second communication hole 104.

[0118] Therefore, the fluid distribution section 100 is disposed at the boundary between the collecting space SA and the distribution space SD in the internal space of the second refrigerant tank 80. The boundary between the collecting space SA and the distribution space SD in the second refrigerant tank 80 corresponds to the inlet section 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, the refrigerant can pass through the fluid distribution part 100 having the first circulation hole 102 and the second circulation hole 104. As a result, similar to the above-mentioned 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 circulation hole 102 and the second circulation hole 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 turn-around method, the same functional effects as those of the above-mentioned embodiments can be obtained from the 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 portion 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 different from the above-mentioned 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 is different from that of the above-mentioned embodiments. Other configurations (e.g., the heat exchange core section 20, etc.) in the heat exchanger 1 according to the sixth embodiment are similar to those of the above-mentioned embodiments, so repeated description will be omitted.

[0123] Although the fluid distribution section 100 according to the embodiment described above is configured by a flat plate member configured by a thin plate, the present invention is not limited to this embodiment. For example, the positional relationship between the central section 101 and the peripheral section 103 of the fluid distribution section 100 in terms of the refrigerant flow direction may be different.

[0124] 12, the fluid distribution part 100 may be configured so that a central part 101 of the fluid distribution part 100 is located downstream in the refrigerant flow direction relative to a peripheral part 103. By positioning the central part 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] Also, the peripheral portion 103 may 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. This allows the direction of the contraction 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 distribution performance of the refrigerant to the refrigerant flow passages 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 functional effects as those of the above-mentioned embodiments can be obtained through the same configuration and operation.

[0127] Seventh embodiment Next, a seventh embodiment different from the above-mentioned 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 through holes 102 and the second through holes 104 in the fluid distribution section 100 is different from that of the above-mentioned embodiments. Other configurations (e.g., the heat exchange core section 20, etc.) in the heat exchanger 1 according to the seventh embodiment are similar to those of the above-mentioned embodiments, so repeated description will be omitted.

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

[0129] By forming the guide protrusions 110 on the opening edges of the first through hole 102 and the second through hole 104, it is possible to adjust the direction of contraction of the refrigerant that has flowed through the first through hole 102 and the second through hole 104. As a result, according to the heat exchanger 1 of the seventh embodiment, the refrigerant can be uniformly distributed with higher accuracy in the refrigerant flow passage 21 connected to the distribution space SD by utilizing the first through hole 102 and the second through hole 104 of the fluid distribution section 100.

[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 through hole 102 and the second through hole 104 in the fluid distribution section 100 is changed, the same functional effects as those of the above-mentioned embodiments can be obtained from the configuration and operation.

[0131] Eighth embodiment Next, an eighth embodiment different from the above-mentioned embodiment will be described with reference to Fig. 14. In the heat exchanger 1 according to the eighth embodiment, the shapes of the first through holes 102 and the second through holes 104 in the fluid distribution section 100 are different from those in the above-mentioned embodiment. Other configurations (e.g., the heat exchange core section 20, etc.) in the heat exchanger 1 according to the eighth embodiment are similar to those in the above-mentioned embodiment, so repeated description will be omitted.

[0132] In the fluid distribution section 100 according to the embodiment described above, the opening shapes of the first through hole 102 and the second through hole 104 are circular, but are not limited to this. As long as the components of the fluid distribution section 100 are opened so that the refrigerant can flow through them, various shapes can be adopted as the opening shapes of the first through hole 102 and the second through hole 104. For example, as shown in FIG. 14, the opening shapes of the first through hole 102 and the second through hole 104 may be rectangular with four 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 functional effects as those of the above-mentioned embodiments can be obtained from the same configuration and operation. (Other embodiments) The present disclosure is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit and scope of the present disclosure.

[0134] (a) In the above-described embodiment, the heat exchanger according to the present disclosure is applied to a chiller that exchanges heat between the refrigerant circulating in the refrigeration cycle and the coolant circulating in the 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 the heat exchanger is a heat exchanger for two-phase fluid including a gas phase and a liquid phase. For example, the heat exchanger according to the present disclosure can be an evaporator that absorbs heat from outside the heat exchanger (for example, air blown into the vehicle cabin) and evaporates the refrigerant circulating in the refrigeration cycle.

[0135] (b) In the above-described embodiment, the heat exchanger 1 is constructed by stacking a plurality of plate members 10 in the stacking direction Z, but the present invention is not limited to this embodiment. The heat exchanger 1 according to the present disclosure can adopt various configurations as long as it has a tank (e.g., refrigerant inlet tank 30, etc.) into which a two-phase fluid flows and a plurality of 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 type configuration. In addition, the center of gravity position related to the cross-sectional shape of the distribution space may be adopted as the center point of the cross-sectional shape of the distribution space.

[0136] The features of the heat exchanger disclosed in this specification are as follows: (Item 1) A plurality of fluid flow paths (21) arranged in a stacked manner in a predetermined stacking direction, through which a fluid including a gas phase and a liquid phase flows; 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, 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 the fluid flows into the distribution space, a fluid distribution section (100) for controlling a flow of fluid through the plurality of fluid flow paths arranged in a stack is disposed on the inlet side of the distribution space in the tank; The fluid distribution section includes: a first flow hole (102) for guiding a fluid to a plurality of fluid flow paths connected to a downstream portion of the distribution space in a flow direction of the fluid; a second flow hole (104) for guiding a fluid to a plurality of fluid flow paths connected to the distribution space at an upstream portion in a flow direction of the fluid flowing through the distribution space, The first flow hole is disposed in a central portion (101) of the fluid distribution portion that is configured within a predetermined range centered on a center point (C) in a cross-sectional shape of the distribution space, The second flow hole is disposed in a peripheral portion (103) of the fluid distribution portion, the peripheral portion being an area between an inner wall surface of the distribution space and the central portion. (Item 2) the plurality of fluid flow paths and the tank in the heat exchanger are configured by joining plate members (10) formed in a plate shape in a state where the plate members are stacked in the stacking direction, The fluid flow path is defined between adjacent plate members arranged in a stacked manner, The distribution space of the tank extends in the stacking direction by using openings (11A, 12A) formed at predetermined positions in the plate members, 2. The heat exchanger according to claim 1, wherein a communication portion (37) that communicates the distribution space of the tank with each of the fluid flow paths is formed around the entire circumference of the tank. (Item 3) The first flow hole is formed in the central portion of the fluid distribution section at a central position in a cross-sectional shape of the distribution space, The second flow holes are formed in a plurality of locations in the peripheral portion of the fluid distribution portion, the plurality of locations being spaced a predetermined distance (d) from the center point, 3. The heat exchanger according to item 1 or 2, wherein 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 mathematical formula 1 is greater than 0.4 and smaller than 1.1.

[0137]

number

[0138] In the formula 1, Aa is the opening area of ​​the first through hole, Ab is the total opening area of ​​the second through 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 through hole in the cross section of the distribution space of the tank. (Item 4) The inside of the tank is configured by the distribution space (SD) which targets all of the fluid flow paths arranged in a stacked manner, 4. The heat exchanger according to any one of items 1 to 3, wherein the fluid distribution section is disposed in the inlet section located at the most upstream part in the direction of fluid flow inside the tank. (Item 5) 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, 5. The heat exchanger according to item 4, wherein the fluid distribution portion is disposed in a fluid flow path in the connector member. (Item 6) The tank has 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 flowed through the collection space, 4. The heat exchanger according to any one of items 1 to 3, wherein the fluid distribution section is disposed at the inlet section through which the fluid flowing out of the collection space flows into the distribution space. [Explanation of symbols]

[0139] 1 heat exchanger 21 Coolant flow path 30 Refrigerant inlet tank 35 Inlet section 100 Fluid distribution section 101 Central part 102 1st circulation hole 103 Periphery 104 2nd circulation hole SD distribution space

Claims

1. a plurality of fluid flow paths (21) arranged in a stacked manner in a predetermined stacking direction, through which a fluid including a gas phase and a liquid phase flows; 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, 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 the fluid flows into the distribution space, a fluid distribution section (100) for controlling the flow of fluid through the plurality of fluid flow paths arranged in a stack is arranged on the side of the inlet section of the distribution space in the tank; The fluid distribution section a first flow hole (102) for guiding fluid to a plurality of fluid flow paths connected to a downstream portion of the distribution space in the direction of flow of the fluid; and second flow holes (104) that guide fluid to the plurality of fluid flow paths connected to the distribution space at an upstream portion 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 (101) being configured within a predetermined range centered on a center point (C) in the cross-sectional shape of the distribution space, The second flow holes are arranged in a peripheral portion (103) of the fluid distribution section, the peripheral portion being a region between the inner wall surface of the distribution space and the central portion, The distribution space of the tank is formed by joining plate members (10) that are stacked in the stacking direction, the fluid flow path is defined 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 member, A heat exchanger in which a communication section (37) that communicates the distribution space of the tank with each of the fluid flow paths is formed around the entire circumference of the tank.

2. the first communication hole is formed in the central portion of the fluid distribution section at a central position in a cross-sectional shape of the distribution space, a plurality of second communication holes are formed in the peripheral portion of the fluid distribution portion at a predetermined distance (d) from the center point; 2. The heat exchanger according to claim 1, wherein the first flow hole and the plurality of second flow 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. [Equation 1] In Equation 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.

3. The inside of the tank is configured by the distribution space (SD) that targets all of the fluid flow paths arranged in a stack, 3. The heat exchanger according to claim 1, wherein the fluid distribution section is disposed at the inlet section located at the most upstream position in the direction of fluid flow inside the tank.

4. A connector member (36) is attached to the inlet port of the tank for connecting a supply pipe for supplying a fluid into the tank, 4. The heat exchanger according to claim 3, wherein the fluid distribution portion is disposed within a fluid flow path in the connector member.

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