Heat exchanger

Abstract

This heat exchanger has a plurality of refrigerant channels (11), a first tank (20, 20A), and a second tank (20, 20B), and is used in a heat-absorbing state, in which heat is absorbed from an object of heat exchange to the refrigerant, and a heat-dissipating state, in which heat present in the refrigerant is dissipated to the object of heat exchange. A distribution space (DS) and an aggregation space (AS) are formed inside the first and second tanks. A refrigerant distribution member (50) is disposed in the distribution space of at least one of the first and second tanks. The refrigerant distribution member has an opening part (52) and a refrigerant guide part (53). The opening part is disposed in the central portion of the distribution space in a cross section perpendicular to the stacking direction and allows a flow of the refrigerant in the stacking direction in the heat-absorbing and heat-dissipating states. The refrigerant guide part is disposed around the opening part and along the inner wall surface of at least one of the first and second tanks and imparts horizontal inertia to the flow of the refrigerant.

Description

heat exchanger CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Patent Application No. 2024-010037 filed on January 26, 2024, the contents of which are incorporated herein by reference.

[0002] The present disclosure relates to a heat exchanger that is used in a heat release state in which heat is released from a refrigerant through heat exchange, and in a heat absorption state in which heat is absorbed by the refrigerant through heat exchange.

[0003] In a conventional heat exchanger for a refrigeration cycle or the like, heat exchange performance is improved by evenly distributing a refrigerant to a plurality of refrigerant flow paths. For example, Patent Document 1 discloses a technique for achieving even distribution of a refrigerant to a plurality of refrigerant flow paths.

[0004] In the technology described in Patent Document 1, a refrigerant tank of a heat exchanger used as an evaporator in a refrigeration cycle is provided with a swirl vane as a swirl structure that imparts a swirl component to the refrigerant flow passing through the inlet. By imparting a swirl component to the refrigerant flow, the distribution performance when distributing the refrigerant from inside the refrigerant tank to multiple refrigerant flow paths is improved, and uniform distribution to each refrigerant flow path is achieved.

[0005] Japanese Patent Application Laid-Open No. 2021-025764

[0006] The technology described in Patent Document 1 is generally intended for application to an evaporator located immediately downstream of a pressure reduction unit such as an expansion valve. Because the evaporator is located immediately downstream of the pressure reduction unit, the refrigerant flowing into the refrigerant tank is in the form of an atomized flow, in which the liquid refrigerant exists as a mist in the gas refrigerant flow. Patent Document 1 can be said to be a technology based on the assumption that the refrigerant flows in as an atomized flow.

[0007] On the other hand, in a refrigeration cycle, a single heat exchanger may be configured to function as either a condenser that releases heat from the refrigerant through heat exchange to condense the refrigerant, or an evaporator that absorbs heat from the refrigerant through heat exchange to evaporate the refrigerant, by switching the circuit configuration. An example of a heat exchanger used in this manner is an outdoor heat exchanger.

[0008] In the case of a heat exchanger that functions as a condenser or an evaporator depending on the switching of the circuit configuration, it is not necessarily positioned immediately downstream of the pressure reduction section in the refrigeration cycle, and it is possible that the state of the refrigerant flowing into the heat exchanger will change.

[0009] In such a case, the state of the refrigerant flowing into the refrigerant tank of the heat exchanger (e.g., the ratio of liquid-phase refrigerant to gas-phase refrigerant) may change from the atomized flow state described above, and the refrigerant may flow in an annular flow state. Here, annular flow means a state in which the liquid-phase refrigerant flows in an annular shape along the inner wall surface of the refrigerant tank, and the gas-phase refrigerant flows in the central part away from the inner wall surface.

[0010] Consider the case where the technology described in Patent Document 1 is applied to a heat exchanger in an environment where the refrigerant flows into the refrigerant tank in a circular flow state. The liquid refrigerant, which is mist-like in the case of atomized flow, flows in a circular pattern along the inner wall surface of the refrigerant tank in the case of circular flow. Therefore, the technology of Patent Document 1, in which swirl vanes are arranged in the center of the refrigerant tank, is unable to sufficiently improve the distribution performance to each refrigerant flow path.

[0011] Furthermore, in the technology of Patent Document 1, the swirl vanes are arranged in the center of the refrigerant tank, which may impede the flow of gas-phase refrigerant in the center and increase pressure loss. If the pressure loss increases, it will cause a decrease in heat exchange performance whether the device is functioning as a condenser or an evaporator.

[0012] In view of the above, the present disclosure aims to provide a heat exchanger that can suppress deterioration of heat exchange performance due to the influence of refrigerant distribution and pressure loss, for a heat exchanger used in a heat dissipation state and a heat absorption state.

[0013] A heat exchanger according to one aspect of the present disclosure includes multiple refrigerant flow paths, a first tank, and a second tank, and is used in a heat absorption state in which a refrigerant absorbs heat from a heat exchange target, and a heat release state in which heat possessed by the refrigerant is released to the heat exchange target. The multiple refrigerant flow paths are stacked in a predetermined stacking direction, and a refrigerant flows through the multiple refrigerant flow paths. The first tank extends in the stacking direction of the multiple refrigerant flow paths and is connected to one end of the multiple refrigerant flow paths. The second tank extends in the stacking direction of the multiple refrigerant flow paths and is connected to the other end of the multiple refrigerant flow paths.

[0014] A distribution space and a collection space are formed inside the first tank and the second tank. The distribution space is a space for distributing the refrigerant to the multiple refrigerant flow paths. The collection space is a space for collecting the refrigerant that has flowed through the multiple refrigerant flow paths. A refrigerant distribution member is disposed in the distribution space of at least one of the first tank and the second tank, which improves the distribution performance of the refrigerant to the multiple refrigerant flow paths with respect to the flow of the refrigerant in the stacking direction.

[0015] The refrigerant distribution member has an opening and a refrigerant guide portion. The opening is located at the center of the distribution space in a cross section perpendicular to the stacking direction and allows the refrigerant to flow in the stacking direction in both the heat absorption state and the heat release state. The refrigerant guide portion is located around the opening along the inner wall surface of at least one of the first tank and the second tank and applies a horizontal inertial force to the refrigerant flow.

[0016] Such a heat exchanger is used in a heat absorption state in which the refrigerant absorbs heat from the heat exchange object, and a heat release state in which the heat contained in the refrigerant is released to the heat exchange object, so it is expected that the flow of refrigerant flowing inside the first tank and the second tank will be a circular flow.

[0017] A refrigerant distribution member is disposed in the distribution space of at least one of the first and second tanks of the heat exchanger, and the refrigerant distribution member has an opening and a refrigerant guide portion. The refrigerant guide portion separates the liquid-phase refrigerant flowing in the stacking direction along the inner wall surface of at least one of the first and second tanks in the annular flow state from the inner wall surface, thereby improving the refrigerant distribution performance in the distribution space.

[0018] This enables the liquid phase refrigerant to be efficiently distributed to multiple refrigerant flow paths connected to the distribution space, thereby improving the refrigerant distribution performance even when an annular flow occurs and suppressing a decrease in heat exchange performance.

[0019] In addition, an opening is formed in the refrigerant distribution member, allowing the refrigerant to flow in the stacking direction in the center of the distribution space, thereby improving the refrigerant distribution performance while suppressing an increase in pressure loss associated with the refrigerant flowing in the stacking direction through the distribution space.

[0020] The above and other objects, features, and advantages of the present disclosure will become more apparent from the following detailed description made with reference to the accompanying drawings.

[0019] Fig. 1 is a schematic diagram showing the configuration of a heat exchanger according to a first embodiment.

[0020] Fig. 2 is an external perspective view of a refrigerant distribution member in the heat exchanger according to the first embodiment.

[0031] Fig. 3 is an enlarged view of a distribution improvement section in the refrigerant distribution member according to the first embodiment.

[0032] Fig. 4 is a horizontal sectional view of the internal configuration of a header tank according to the first embodiment.

[0033] Fig. 5 is a vertical sectional view of the internal configuration of the header tank according to the first embodiment.

[0034] Fig. 6 is a front view of a refrigerant distribution member according to a second embodiment.

[0035] Fig. 7 is a side view of a refrigerant distribution member according to the second embodiment.

[0036] Fig. 8 is a horizontal sectional view of the internal configuration of the header tank according to the second embodiment.

[0037] Fig. 9 is a vertical sectional view of the internal configuration of the header tank according to the second embodiment.

[0038] Fig. 10 is a schematic diagram showing the configuration of a heat exchanger according to a third embodiment.

[0039] Fig. 11 is a horizontal sectional view of the internal configuration of a header tank according to a fourth embodiment.

[0039] Fig. 12 is an explanatory view showing the relationship between the cross-sectional areas of the openings and the refrigerant guide section in the refrigerant distribution member according to the fourth embodiment.

[0039] Fig. 13 is a vertical sectional view of the internal configuration of the header tank according to the fourth embodiment.

[0021] 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.

[0022] First Embodiment A first embodiment of the present disclosure will be described with reference to the drawings. A heat exchanger 1 according to the first embodiment is applied to an exterior heat exchanger in a refrigeration cycle of a vehicle air conditioner. In the refrigeration cycle of the vehicle air conditioner, when a heating operation is performed to heat the vehicle interior, which is the air-conditioned space, the exterior heat exchanger functions as an evaporator to cause the refrigerant to absorb heat from the outside air. On the other hand, when a cooling operation is performed to cool the vehicle interior, the exterior heat exchanger functions as a condenser to dissipate heat from the refrigerant to the outside air.

[0023] That is, when the circuit configuration is switched and the vehicle air conditioner performs heating operation, the heat exchanger 1 in the present disclosure is used as an evaporator that functions in a heat absorption state in which the refrigerant absorbs heat from the outside air, and when the circuit configuration is switched and the vehicle air conditioner performs cooling operation, the heat exchanger 1 is used as a condenser that functions in a heat release state in which the refrigerant releases heat to the outside air.

[0024] 1, the heat exchanger 1 according to the first embodiment has a core 10, which is a heat exchange section that exchanges heat between a refrigerant circulating in a refrigeration cycle and outside air. The core 10 is a laminate in which multiple tubes 11 and fins 12 are stacked alternately in the vertical direction.

[0025] Each tube 11 is a tubular member having a refrigerant flow path formed therein through which a refrigerant flows. The longitudinal direction of each tube 11 extends horizontally and corresponds to an example of a refrigerant flow path. The longitudinal direction of the tube 11 is the horizontal direction and also corresponds to the left-right direction of the heat exchanger 1. Each tube 11 is configured to have a flat shape such that the major axis direction of a cross section perpendicular to the longitudinal direction extends along the flow direction of air passing through the core portion 10.

[0026] Here, a flat shape includes an elliptical shape consisting of a curved shape combining an arc portion with a large radius of curvature and an arc portion with a small radius of curvature, and an oval shape consisting of a shape combining an arc portion and a flat portion.

[0027] In this specification, the cross-sectional major axis direction of the tube 11 is defined as the width direction of the tube. In this embodiment, the tube width direction coincides with a direction perpendicular to both the longitudinal direction of the tube 11 and the stacking direction of the tube 11, and corresponds to the front-to-rear direction of the heat exchanger 1. Hereinafter, the longitudinal direction of the tube 11 will be referred to as the "longitudinal direction," and the stacking direction of the tube 11 will be referred to as the "stacking direction." In this embodiment, the stacking direction corresponds to the direction of gravity and the up-down direction of the heat exchanger 1.

[0028] The fins 12 are components that increase the heat transfer area with the outside air and promote heat exchange between the outside air and the refrigerant. In this embodiment, the fins 12 are formed in a corrugated shape and are joined to flat portions on both sides of the tubes 11.

[0029] The tubes 11 and the fins 12 are made of a metal having excellent thermal conductivity, corrosion resistance, etc. For example, the tubes 11 and the fins 12 are made of an aluminum alloy. The tubes 11, the fins 12, the core plate 21 (described later), and the side plate 13 are integrally brazed together with a brazing material coated on predetermined locations of each component.

[0030] A pair of header tanks 20 extending in the stacking direction and having an internal space are disposed at both longitudinal ends of each tube 11. As shown in Figure 4, the header tank 20 is configured to include a core plate 21 into which the tubes 11 are inserted and joined, and a tank body 22 which, together with the core plate 21, defines the tank space.

[0031] The longitudinal ends of each tube 11 are joined to the header tank 20 in a state where they are inserted into insertion holes 21A formed in the core plate 21. The internal passages of each tube 11 communicate with the internal space of the header tank 20.

[0032] Side plates 13 are provided at both ends of the core portion 10 in the stacking direction to reinforce the core portion 10. The side plates 13 extend parallel to the longitudinal direction, and both ends are connected to the core plate 21. In this embodiment, the side plates 13 are made of a metal such as an aluminum alloy.

[0033] The header tank 20 of the heat exchanger 1 has a core plate 21 and a tank body 22. The core plate 21 is a plate-shaped member into which the tubes 11 and the side plates 13 are inserted and joined. The tank body 22, together with the core plate 21, constitutes the tank interior space, which is the space within the header tank 20.

[0034] The core plate 21 is made of a metal having excellent thermal conductivity, corrosion resistance, etc. For example, the core plate 21 is made of an aluminum alloy.

[0035] Here, one of the pair of header tanks 20 is referred to as the first tank 20A, and the other header tank 20 is referred to as the second tank 20B. The first tank 20A is disposed on one end side of the plurality of tubes 11 that constitute the core part 10, and the internal space of the first tank 20A is connected to one end of the plurality of tubes 11. The second tank 20B is disposed on the other end side of the plurality of tubes 11 that constitute the core part 10, and the internal space of the second tank 20B is connected to the other end of the plurality of tubes 11.

[0036] 1, a separator 25 that divides the internal space in the vertical direction is disposed inside the first tank 20A. In the first embodiment, the separator 25 is disposed in approximately the center of the first tank 20A in the stacking direction.

[0037] The first tank 20A of the heat exchanger 1 according to the first embodiment is formed with an inlet 30 and an outlet 35. The inlet 30 is a connection port for allowing the refrigerant circulating through the refrigeration cycle to flow into the interior of the heat exchanger 1 (i.e., the interior of the first tank 20A). The outlet 35 is a connection port for allowing the refrigerant that has circulated inside the heat exchanger 1 (i.e., the interior of the first tank 20A) to flow out to the refrigeration cycle outside the heat exchanger 1.

[0038] As shown in FIG. 1, in the heat exchanger 1 according to the first embodiment, the inlet 30 is formed on the lower side of the first tank 20A in the direction of gravity, and the outlet 35 is formed on the upper side of the first tank 20A in the direction of gravity.

[0039] As described above, the separator 25 is disposed inside the first tank 20A according to the first embodiment, and the internal space of the first tank 20A is divided into two spaces in the vertical direction by the separator 25. The space on the lower side of the first tank 20A in the direction of gravity is connected to the refrigeration cycle via the inlet 30. The space on the upper side of the first tank 20A in the direction of gravity is connected to the refrigeration cycle via the outlet 35.

[0040] That is, within the internal space of the first tank 20A according to the first embodiment, the space below the separator 25 in the direction of gravity constitutes a space for distributing the refrigerant that has flowed in from the inlet 30 to the plurality of tubes 11 that constitute the lower part of the core portion 10. Therefore, the internal space of the first tank 20A that is located below the separator 25 in the direction of gravity constitutes a distribution space DS.

[0041] The space within the internal space of the first tank 20A according to the first embodiment, above the separator 25 in the direction of gravity, forms a space where the refrigerant that has flowed through the plurality of tubes 11 that form the upper part of the core unit 10 is collected so that it can flow out from the outlet 35. Therefore, the internal space of the first tank 20A located above the separator 25 in the direction of gravity forms a collection space AS. In other words, the internal space of the first tank 20A according to the first embodiment is vertically partitioned by the separator 25 into two spaces: a distribution space DS and a collection space AS.

[0042] 1, the second tank 20B of the heat exchanger 1 according to the first embodiment has two spaces formed therein: a collection space AS and a distribution space DS. The plurality of tubes 11 constituting the lower portion of the core unit 10 are connected to the internal space on one side of the stacking direction (the lower side in the direction of gravity) of the second tank 20B. Therefore, the space located on the lower side in the direction of gravity within the internal space of the second tank 20B constitutes the collection space AS, which collects the refrigerant that has flowed through the tubes 11 constituting the lower portion of the core unit 10.

[0043] Unlike the first tank 20A, the internal space of the second tank 20B according to the first embodiment does not include a separator 25, and instead forms a single space that is connected vertically. Therefore, when the refrigerant flows into the collection space AS of the second tank 20B via the multiple tubes 11 that form the lower part of the core 10, the refrigerant flows toward the other side in the stacking direction (upward in the direction of gravity) and flows into the distribution space DS of the second tank 20B.

[0044] 1, the internal space on the other side in the stacking direction (upper side in the direction of gravity) inside the second tank 20B forms a distribution space DS. The distribution space DS of the second tank 20B is connected to a plurality of tubes 11 that form the upper part of the core unit 10. Therefore, the distribution space DS of the second tank 20B forms the distribution space DS in the internal space of the second tank 20B for distributing the refrigerant that flows from the collection space AS to the distribution space DS to each of the tubes 11 that form the upper part of the core unit 10.

[0045] Inside the second tank 20B, the collection space AS and the distribution space DS are divided at a portion corresponding to the position of the separator 25 in the first tank 20A. As described above, since both the first tank 20A and the second tank 20B are configured to be connected to the ends of a plurality of stacked tubes 11, the portion corresponding to the position of the separator 25 can be identified based on the number of tubes 11. In other words, the collection space AS and the distribution space DS in the second tank 20B can be divided based on the number of tubes 11 that make up the core portion 10.

[0046] Next, the flow of the refrigerant in the heat exchanger 1 according to the first embodiment will be described with reference to the drawings. The outline arrows shown in Fig. 1 indicate the flow of the refrigerant.

[0047] The refrigerant circulating through the refrigeration cycle flows from the inlet 30 of the heat exchanger 1 into the distribution space DS below the first tank 20A. The refrigerant that has flowed into the distribution space DS of the first tank 20A flows into the collection space AS below the second tank 20B via the multiple tubes 11 that form the lower part of the core 10. The refrigerant that has flowed into the second tank 20B flows upward in the stacking direction within the tank interior, from the collection space AS of the second tank 20B to the distribution space DS.

[0048] When the refrigerant flows into the distribution space DS of the second tank 20B, it flows into the collection space AS of the first tank 20A through the multiple tubes 11 that form the upper part of the core 10. The refrigerant that flows into the collection space AS of the first tank 20A flows out of the heat exchanger 1 through the outlet 35 and circulates through the refrigeration cycle. In this way, the heat exchanger 1 according to the first embodiment is configured so that the flow of the refrigerant makes one turn inside the heat exchanger 1.

[0049] Here, when examining the refrigerant distribution performance in the header tank 20 of the heat exchanger 1, it is assumed that the state of the refrigerant flowing into the header tank 20 will have a significant impact, and that it will be particularly affected by the amount and ratio of liquid-phase refrigerant and gas-phase refrigerant contained in the flowing-in refrigerant.

[0050] For example, when the heat exchanger 1 is used exclusively as an evaporator, it is considered that the heat exchanger 1 is disposed immediately downstream of a pressure reducing section such as an expansion valve. In such a configuration, the refrigerant flowing out from the pressure reducing section flows into the header tank 20 of the heat exchanger 1, and is considered to flow in a so-called atomized flow state. The atomized flow state is a state in which the refrigerant flowing into the header tank 20 contains mist-like liquid refrigerant, and due to the positional relationship between the heat exchanger 1 and the pressure reducing section, it is considered that the refrigerant flows in stably in an atomized flow state.

[0051] In this regard, when the refrigerant flows into the header tank 20 in a state where there is more liquid-phase refrigerant than in a state of atomized flow, it is assumed that the refrigerant flows in a state called annular flow. The annular flow refers to a state in which the liquid-phase refrigerant flows in a ring shape along the tank inner wall surface 23 of the header tank 20, and the gas-phase refrigerant flows in a central portion away from the tank inner wall surface 23.

[0052] In the case of the heat exchanger 1 according to the first embodiment, when the refrigerant flow is configured to turn back once at the second tank 20B as it flows from the inlet 30 to the outlet 35, the refrigerant exchanges heat with the outside air, which is the heat exchange target, as it flows from the first tank 20A to the second tank 20B. Even when the refrigerant flows in as a mist flow from the inlet 30, the heat exchange with the outside air as it flows from the first tank 20A to the second tank 20B affects the ratio and distribution of the gas-phase refrigerant and the liquid-phase refrigerant, and therefore, a circular flow of the refrigerant may occur inside the second tank 20B.

[0053] The ratio and distribution of liquid and gas phase refrigerant in the refrigerant flow are significantly different between the circulating flow and the atomized flow. For this reason, in the heat exchanger 1 in which the circulating flow occurs, it is desirable to improve the refrigerant distribution performance in the header tank 20 in a manner that is suited to the ratio and distribution of liquid and gas phase refrigerant in the circulating flow.

[0054] In the heat exchanger 1 according to the first embodiment of the present disclosure, in order to improve the refrigerant distribution performance in the internal space of the second tank 20B, a refrigerant distribution member 50 is arranged in the distribution space DS of the second tank 20B, as shown in FIG.

[0055] Next, the configuration of the refrigerant distribution member 50 arranged in the heat exchanger 1 according to the first embodiment will be described with reference to Figures 2 and 3. Figure 2 is an external perspective view of the refrigerant distribution member 50 according to the first embodiment, and Figure 3 is an enlarged view showing the configuration of the distribution improvement section 51 in the refrigerant distribution member 50.

[0056] 2, the refrigerant distribution member 50 according to the first embodiment has a distribution improvement portion 51 and a flat plate portion 55. The distribution improvement portions 51 are formed at both ends of the elongated flat plate portion 55, and are formed perpendicular to the flat plate portion 55. The flat plate portion 55 is disposed inside the header tank 20 so as to be aligned with the core plate 21. Therefore, the distribution improvement portion 51 of the refrigerant distribution member 50 is disposed so as to horizontally cross the internal space of the header tank 20, which extends in the stacking direction.

[0057] The distribution improvement section 51 according to the first embodiment is formed with an opening 52, a refrigerant guide section 53, and a support section 54. The opening 52 is located in the center of the distribution improvement section 51 and is configured to allow refrigerant to flow through the opening 52 with minimal pressure loss. As shown in Figures 4 and 5, when the refrigerant distribution member 50 is disposed inside the header tank 20, the opening 52 is located in the center of the distribution space DS in a horizontal cross section perpendicular to the header tank 20 extending in the stacking direction.

[0058] The refrigerant guide portion 53 is a guide piece that applies horizontal inertial force to the refrigerant flowing along the tank inner wall surface 23, guiding it to become a swirling flow, and is formed by cutting out a part of the distribution improvement portion 51 that forms the periphery of the opening 52. The refrigerant guide portions 53 according to the first embodiment are formed as a pair at positions facing each other across the opening 52, and as shown in FIG. 4 , the pair of refrigerant guide portions 53 are each arranged along the tank inner wall surface 23.

[0059] 5, the refrigerant guide portion 53 formed on one side in the width direction is inclined so that it is positioned closer to one side (upper) in the stacking direction as it approaches one side in the longitudinal direction, and the refrigerant guide portion 53 formed on the other side in the width direction is inclined so that it is positioned closer to one side (upper) in the stacking direction as it approaches the other side in the longitudinal direction.

[0060] The support portion 54 is a protrusion formed on the outer periphery of the distribution improvement portion 51 at a position facing the flat plate portion 55. As shown in Figures 4 and 5, the support portion 54 fits into a recess formed in a portion constituting the longitudinal end of the tank inner wall surface 23, thereby positioning and fixing the distribution improvement portion 51 of the refrigerant distribution member 50 at a predetermined position.

[0061] 2, the flat plate portion 55 is an elongated plate-like portion formed with a length shorter than the overall length of the header tank 20 in the stacking direction. Both ends of the flat plate portion 55 in the short direction are bent to increase the rigidity of the flat plate portion 55. As shown in FIGS. 4 and 5, the flat plate portion 55 according to the first embodiment is disposed in the distribution space DS of the second tank 20B so as to be aligned with the core plate 21 located on the core portion 10 side.

[0062] The flat plate portion 55 of the refrigerant distribution member 50 is formed to have a dimension shorter than the entire length of the second tank 20B and shorter than the distribution space DS of the second tank 20B, so that the arrangement in the internal space of the second tank 20B can be appropriately determined. This allows the flat plate portion 55 of the refrigerant distribution member 50 and the multiple communication holes 56 to efficiently exhibit the effect of improving the refrigerant distribution performance.

[0063] 1 , in the refrigerant distribution member 50 according to the first embodiment, a plurality of communication holes 56 are formed in the flat plate portion 55. The communication holes 56 are aligned in the longitudinal direction at the same intervals as the plurality of insertion holes 21A formed in the core plate 21. As described above, the ends of the tubes 11 are inserted into the insertion holes 21A of the core plate 21, and therefore, each insertion hole 21A is arranged to communicate with the end of the tube 11.

[0064] When the annular flow flows into the header tank 20, a strong inertial force tends to act on the liquid-phase refrigerant along the tank inner wall surface 23. In particular, when the heat exchanger 1 is used as an evaporator (i.e., in a heat-absorbing state), the inertial force tends to act more strongly on the refrigerant than when it is used as a condenser. For this reason, if a configuration is adopted in which the refrigerant distribution member 50 is not provided, of the multiple tubes 11 connected to the distribution space DS of the second tank 20B, more refrigerant is distributed to the tubes 11 on the downstream side of the refrigerant flow, and less refrigerant is distributed to the tubes 11 on the upstream side of the refrigerant flow.

[0065] As described above, if the refrigerant distribution performance in the distribution space DS of the second tank 20B becomes uneven, the heat exchange performance of the heat exchanger 1 will be reduced. In particular, when a configuration in which the refrigerant flow turns once in the second tank 20B is adopted, as in the heat exchanger 1 according to the first embodiment, it is considered that this is more likely to be a factor in reducing heat exchange performance. The tubes 11 located upstream of the refrigerant flow in the distribution space DS of the second tank 20B constitute the central portion of the core 10 of the heat exchanger 1, and are a portion through which outside air, which is the target of heat exchange, can easily pass. Considering this point, improving the refrigerant distribution performance in the distribution space DS of the second tank 20B has a significant impact on improving the heat exchange performance of the heat exchanger 1.

[0066] In the heat exchanger 1 of the first embodiment, by arranging a refrigerant distribution member 50 in the distribution space DS of the second tank 20B, the distribution of refrigerant to each tube 11 that constitutes the core portion 10 is improved, thereby suppressing a decrease in heat exchange performance even in situations where annular flow occurs.

[0067] Next, the effect of the refrigerant distribution member 50 in the second tank 20B of the heat exchanger 1 according to the first embodiment will be described with reference to FIGS.

[0068] 4, the opening 52 of the refrigerant distribution member 50 is located at the center of the horizontal cross section of the distribution space DS of the second tank 20B extending in the stacking direction. When the refrigerant flows in a circular flow through the second tank 20B according to the first embodiment, the gas phase refrigerant mainly flows through the center of the header tank 20.

[0069] 4 and 5, by arranging the opening 52 of the refrigerant distribution member 50 in the center of the horizontal cross section of the distribution space DS of the second tank 20B, a smooth flow of gas-phase refrigerant can be achieved whether the heat exchanger 1 is used as a condenser or an evaporator. That is, according to the heat exchanger 1 according to the first embodiment, the opening 52 of the refrigerant distribution member 50 can suppress a decrease in heat exchange performance due to a pressure loss of the refrigerant even when a circular flow occurs.

[0070] As described above, the distribution improvement section 51 is formed with a pair of refrigerant guide sections 53 via the opening 52, and as shown in Fig. 4, the refrigerant guide sections 53 are arranged along the tank inner wall surface 23 of the second tank 20B. The refrigerant guide section 53 formed on one side in the width direction is inclined so that it is positioned closer to one side (upper) in the stacking direction as it approaches one side in the longitudinal direction. The refrigerant guide section 53 formed on the other side in the width direction is inclined so that it is positioned closer to one side (upper) in the stacking direction as it approaches the other side in the longitudinal direction.

[0071] When the refrigerant flows in a circular flow state inside the header tank 20, the liquid-phase refrigerant flows along the tank inner wall surface 23. Therefore, when the refrigerant flows along the tank inner wall surface 23 and reaches the distribution improvement section 51, the pair of refrigerant guide sections 53 separate the liquid-phase refrigerant flowing along the tank inner wall surface 23 from the tank inner wall surface 23, and apply a horizontal inertial force to the refrigerant.

[0072] As a result, the pair of refrigerant guide sections 53 in the distribution improvement section 51 can promote a spiral swirling flow of refrigerant downstream as it passes through the distribution improvement section 51 in the stacking direction.

[0073] As a result, the liquid-phase refrigerant flowing along the tank inner wall surface 23 in a circular flow state can be separated and mixed with the gas-phase refrigerant passing through the opening 52, thereby improving the refrigerant distribution performance to the multiple tubes 11 arranged side by side in the stacking direction in the distribution space DS. In the heat exchanger 1 according to the first embodiment, a sufficient amount of refrigerant can be distributed even to the upstream side of the refrigerant flow in the distribution space DS of the second tank 20B, so that the heat exchange performance in the center of the core portion 10 can be sufficiently ensured and a decrease in heat exchange performance can be suppressed.

[0074] 5, the flat plate portion 55 of the refrigerant distribution member 50 according to the first embodiment is disposed along the second tank 20B. The ends of the tubes 11 inserted into the insertion holes 21A of the core plate 21 are inserted into the communication holes 56 formed in the flat plate portion 55, respectively.

[0075] As a result, in the distribution space DS of the second tank 20B, the refrigerant flows in a circular flow state through the space formed by the tank inner wall surface 23 on the tank main body 22 side and the flat plate portion 55 of the refrigerant distribution member 50.

[0076] Furthermore, since the end of the tube 11 inserted into the insertion hole 21A of the core plate 21 is inserted into the communicating hole 56 of the flat plate portion 55, the space between the core plate 21 and the flat plate portion 55 is almost completely blocked by the tube 11.

[0077] By configuring in this manner, when the refrigerant flowing in a circular flow state flows into the distribution space DS of the second tank 20B, the liquid phase refrigerant flowing along the tank inner wall surface 23 flows along the tank inner wall surface 23 which is composed of the tank main body portion 22 and the flat plate portion 55.

[0078] As shown in Figures 4 and 5, the opening edges of each communication hole 56 in the flat plate portion 55 are close to the ends of each tube 11 that pass through the core plate 21, so that the liquid phase refrigerant that has been peeled off from the tank inner wall surface 23 can be efficiently guided to each tube 11, improving distribution.

[0079] As a result, the heat exchanger 1 of the first embodiment can suppress a decrease in heat exchange performance due to pressure loss and distribution characteristics by placing the refrigerant distribution member 50 in the distribution space DS of the second tank 20B, even when distributing refrigerant in a circular flow state.

[0080] According to the heat exchanger 1 of the first embodiment, the inlet 30 is formed in a lower portion of the first tank 20A in the direction of gravity, and the outlet 35 is formed in an upper portion of the first tank 20A in the direction of gravity. Therefore, gravity can be made to act in the opposite direction to the flow of refrigerant in the stacking direction during the process from the inlet 30 to the outlet 35, and gravity can be effectively used to improve the distribution performance of the refrigerant to the upstream side of the refrigerant flow in the distribution space DS of the second tank 20B.

[0081] As described above, the heat exchanger 1 according to the first embodiment constitutes an exterior heat exchanger in the refrigeration cycle of a vehicle air conditioner, and functions as either a heat absorber that absorbs heat from the exterior air into the refrigerant, or a radiator that radiates heat from the refrigerant to the exterior air, depending on the operating mode. The heat exchanger 1 according to the first embodiment has a core 10 formed by stacking multiple tubes 11 between a first tank 20A and a second tank 20B.

[0082] In the heat exchanger 1 according to the first embodiment, a refrigerant distribution member 50 is arranged in the internal space of the second tank 20B, improving the refrigerant distribution performance to the multiple tubes 11 connected to the second tank 20B.

[0083] 3, the refrigerant distribution member 50 according to the first embodiment has an opening 52 in the center of the distribution improvement section 51. As a result, even when an annular flow occurs inside the header tank 20, the heat exchanger 1 can achieve a smooth flow of gas-phase refrigerant and suppress deterioration of heat exchange performance due to refrigerant pressure loss, regardless of whether the heat exchanger 1 is used as a condenser or an evaporator.

[0084] 3 and 4, the refrigerant distribution member 50 has a pair of refrigerant guide portions 53 in the distribution improvement portion 51, and is arranged along the tank inner wall surface 23 of the second tank 20B. The pair of refrigerant guide portions 53 impart a horizontal inertial force to the liquid-phase refrigerant flowing in the stacking direction along the tank inner wall surface 23 in a circular flow state.

[0085] This promotes a spiral swirling flow of the refrigerant flowing downstream in the internal space of the second tank 20B. In the case of an annular flow, the liquid-phase refrigerant flowing along the tank inner wall surface 23 can be separated and mixed with the gas-phase refrigerant passing through the opening 52, thereby improving the refrigerant distribution performance to the multiple tubes 11 arranged side by side in the stacking direction in the distribution space DS.

[0086] As shown in Fig. 2 and other figures, the refrigerant distribution member 50 according to the first embodiment has, in addition to the distribution improvement portion 51, a flat plate portion 55 and a plurality of communication holes 56. As shown in Fig. 5, the flat plate portion 55 of the refrigerant distribution member 50 according to the first embodiment is arranged so as to be aligned with the second tank 20B. Ends of the plurality of tubes 11 inserted into the plurality of insertion holes 21A of the core plate 21 are inserted into the plurality of communication holes 56 formed in the flat plate portion 55, respectively.

[0087] As a result, in the distribution space DS of the second tank 20B, the refrigerant flows in an annular flow state through a space defined by the tank inner wall surface 23 on the tank main body 22 side and the flat plate portion 55 of the refrigerant distribution member 50. When the refrigerant flowing in an annular flow state enters the distribution space DS of the second tank 20B, the liquid-phase refrigerant flowing along the tank inner wall surface 23 flows along the tank inner wall surface 23 defined by the tank main body 22 and the flat plate portion 55.

[0088] As shown in Figures 4 and 5, the opening edges of each communication hole 56 in the flat plate portion 55 are close to the ends of each tube 11 that pass through the core plate 21, so that the liquid phase refrigerant that has been peeled off from the tank inner wall surface 23 can be efficiently guided to each tube 11, improving distribution.

[0089] As a result, the heat exchanger 1 of the first embodiment can suppress a decrease in heat exchange performance due to pressure loss and distribution characteristics by placing the refrigerant distribution member 50 in the distribution space DS of the second tank 20B, even when distributing refrigerant in a circular flow state.

[0090] The flat portion 55 of the refrigerant distribution member 50 according to the first embodiment is formed with a dimension shorter than the overall length of the second tank in the stacking direction, and shorter than the distribution space DS of the second tank 20B.

[0091] As a result, according to the heat exchanger 1 of the first embodiment, the arrangement in the internal space of the second tank 20B can be appropriately determined, and the effect of improving the refrigerant distribution performance by the flat plate portion 55 and the multiple communicating holes 56 can be efficiently achieved.

[0092] 1, in the heat exchanger 1 according to the first embodiment, a distribution space DS and a collection space AS are formed in the internal spaces of the first tank 20A and the second tank 20B, respectively. In the heat exchanger 1 according to the first embodiment, the refrigerant flows in the following order: the distribution space DS of the first tank 20A, the lower part of the core unit 10, the collection space AS of the second tank 20B, the distribution space DS of the second tank 20B, the upper part of the core unit, and the collection space AS of the first tank 20A.

[0093] In a heat exchanger 1 configured as described above, the ratio of liquid-phase refrigerant to gas-phase refrigerant often fluctuates as the refrigerant flows, and it is expected that a circular flow will flow inside the header tank 20. According to the heat exchanger 1 according to the first embodiment, even in a configuration in which the refrigerant flow turns back once through the internal space of the second tank 20B, creating a circular flow, the refrigerant distribution performance inside the header tank 20 can be improved by providing the refrigerant distribution member 50.

[0094] In the heat exchanger 1 according to the first embodiment, the refrigerant distribution member 50 is arranged within the distribution space DS of the second tank 20B, improving the distribution performance for the multiple tubes 11 that constitute the upper part of the core portion 10.

[0095] In the above-described configuration, the refrigerant is subject to heat exchange as it flows through the lower portion of the core 10 while traveling from the distribution space DS of the first tank 20A to the collection space AS of the second tank 20B. That is, the distribution and ratio of the liquid-phase refrigerant and the gas-phase refrigerant changes due to the heat exchange, and the refrigerant flows through the internal space of the second tank 20B, so it is expected that a circular flow will occur in the distribution space DS of the second tank 20B.

[0096] In the heat exchanger 1 according to the first embodiment, the refrigerant distribution member 50 is arranged inside the distribution space DS of the second tank 20B, where it is thought that an annular flow is likely to occur, and therefore, the deterioration of the refrigerant distribution performance due to the annular flow can be effectively suppressed.

[0097] 1 , in the heat exchanger 1, the inlet 30 is formed in a lower portion of the first tank 20A in the direction of gravity, and the outlet 35 is formed in an upper portion of the first tank 20A in the direction of gravity. Therefore, when the refrigerant flows from the inlet 30 to the outlet 35, gravity acts in the opposite direction to the flow of refrigerant in the stacking direction in the distribution space DS of the second tank 20B. In other words, in the heat exchanger 1 according to the first embodiment, gravity can be effectively used to improve the distribution performance of the refrigerant in the distribution space DS of the second tank 20B toward the upstream side of the refrigerant flow, in addition to the effect of improving the distribution performance by the refrigerant distribution member 50.

[0098] Second Embodiment Next, a second embodiment, which differs from the above-described embodiment, will be described with reference to Figures 6 to 9. In the second embodiment, the configuration of the refrigerant distribution member 50 differs from that of the first embodiment. Therefore, the refrigerant distribution member 50 according to the second embodiment will be described in detail. The other configurations of the heat exchanger 1 (for example, the configurations of the core 10 and header tank 20) ​​are the same as those of the first embodiment, and therefore will not be described again.

[0099] The heat exchanger 1 of the second embodiment is configured in the same manner as the first embodiment, and has a core portion 10 between a first tank 20A and a second tank 20B, in which multiple tubes 11 are stacked in the stacking direction.

[0100] In the heat exchanger 1 according to the second embodiment, a separator 25 is arranged inside the first tank 20A, and a distribution space DS and a collection space AS are formed in the internal spaces of the first tank 20A and the second tank 20B, respectively.

[0101] Therefore, in the second embodiment, the refrigerant flows in the following order: inlet 30, distribution space DS of the first tank 20A, the lower part of the core portion 10, collection space AS of the second tank 20B, distribution space DS of the second tank 20B, the upper part of the core portion 10, collection space AS of the first tank 20A, and outlet 35.

[0102] The refrigerant distribution member 50 disposed in the heat exchanger 1 according to the second embodiment will be described with reference to the drawings. In the heat exchanger 1 according to the second embodiment, the refrigerant distribution member 50 is disposed in the internal space of the second tank 20B.

[0103] Specifically, the refrigerant distribution member 50 according to the second embodiment is disposed in the internal space of the second tank 20B so as to correspond to the position of the separator 25 in the internal space of the first tank 20A. The position corresponding to the position of the separator 25 can be determined according to the number of tubes 11 connected to the header tank 20. In other words, the refrigerant distribution member 50 according to the second embodiment is disposed in the upstream portion of the distribution space DS of the second tank 20B in the refrigerant flow direction.

[0104] 6 and 7, the refrigerant distribution member 50 according to the second embodiment has a distribution improvement section 51, but unlike the refrigerant distribution member 50 according to the first embodiment, it does not have a flat plate section 55. That is, the refrigerant distribution member 50 according to the second embodiment is constituted by the distribution improvement section 51, and the distribution improvement section 51 is arranged so as to horizontally cross the internal space of the header tank 20 extending in the stacking direction.

[0105] The refrigerant distribution member 50 according to the second embodiment has an opening 52, a plurality of refrigerant guide portions 53, and a support portion 54. In the refrigerant distribution member 50 according to the second embodiment, the opening 52 is located in the center of the distribution improvement portion 51 and is configured to allow refrigerant to flow through the opening 52 with minimal pressure loss. As shown in Figures 6 and 7, when the refrigerant distribution member 50 is placed inside the header tank 20, the opening 52 is located in the center of the distribution space DS in a horizontal cross section perpendicular to the header tank 20 extending in the stacking direction.

[0106] The refrigerant distribution member 50 according to the second embodiment is formed with a plurality of refrigerant guide portions 53. Each refrigerant guide portion 53 is a guide piece that applies a horizontal inertial force to the refrigerant flowing along the tank inner wall surface 23, guiding the refrigerant to form a swirling flow, and is formed by cutting out a part of the distribution improvement portion 51 that forms the periphery of the opening 52.

[0107] The refrigerant guide portions 53 according to the second embodiment are formed at three locations that form the periphery of the opening 52. As shown in Fig. 8 , the three refrigerant guide portions 53 are each arranged along the tank inner wall surface 23.

[0108] Of the three refrigerant guide portions 53, two refrigerant guide portions 53 are arranged to face each other across the opening 52 in the width direction of the heat exchanger 1. The remaining one of the three refrigerant guide portions 53 is arranged closer to the core plate 21 than the opening 52 in the longitudinal direction of the heat exchanger 1.

[0109] 6 and 7 , the refrigerant guide portion 53 formed on one side in the width direction is inclined so as to be positioned closer to one side (upper) in the stacking direction as it approaches one side in the longitudinal direction. The refrigerant guide portion 53 formed on the other side in the width direction is inclined so as to be positioned closer to one side (upper) in the stacking direction as it approaches the other side in the longitudinal direction. The refrigerant guide portion 53 located closer to the core plate 21 than the opening 52 is inclined so as to be positioned closer to one side (upper) in the stacking direction as it approaches from one side to the other side in the width direction.

[0110] In the refrigerant distribution member 50 according to the second embodiment, the support portion 54 is a protrusion formed on the outer periphery of the distribution improvement portion 51 at a position facing a refrigerant guide portion 53 formed on the core plate 21 side, across an opening 52. As shown in Figures 6 and 7, the support portion 54 according to the second embodiment fits into a recess formed in a portion constituting a longitudinal end of the tank inner wall surface 23 formed by the tank main body 22, thereby positioning and fixing the distribution improvement portion 51 of the refrigerant distribution member 50 at a predetermined position.

[0111] Next, the effect of the refrigerant distribution member 50 in the second tank 20B of the heat exchanger 1 according to the second embodiment will be described with reference to FIGS. 8 and 9. FIG.

[0112] 8, the opening 52 of the refrigerant distribution member 50 according to the second embodiment is located at the center of the horizontal cross section of the distribution space DS of the second tank 20B extending in the stacking direction. In the second embodiment, when the refrigerant flows in a circular flow through the second tank 20B, mainly the gas phase refrigerant flows through the center of the header tank 20.

[0113] 8 and 9, by arranging the opening 52 according to the second embodiment in the central portion of the horizontal cross section of the distribution space DS of the second tank 20B, a smooth flow of gas-phase refrigerant can be achieved whether the heat exchanger 1 is used as a condenser or an evaporator. That is, according to the heat exchanger 1 according to the second embodiment, even when a circular flow occurs due to the opening 52 of the refrigerant distribution member 50, a decrease in heat exchange performance caused by a pressure loss of the refrigerant can be suppressed.

[0114] As described above, the distribution improvement section 51 has refrigerant guide sections 53 formed at three locations around the opening, and as shown in Figures 8 and 9, they are arranged along the tank inner wall surface 23 of the second tank 20B.

[0115] The refrigerant guide portion 53 formed on one side in the width direction is inclined so as to be positioned closer to one side (upper) in the stacking direction as it approaches one side in the longitudinal direction. The refrigerant guide portion 53 formed on the other side in the width direction is inclined so as to be positioned closer to one side (upper) in the stacking direction as it approaches the other side in the longitudinal direction. The refrigerant guide portion 53 located closer to the core plate 21 than the opening 52 is inclined so as to be positioned closer to one side (upper) in the stacking direction as it approaches from one side to the other side in the width direction.

[0116] When the refrigerant in a circular flow state reaches the distribution improvement section 51 along the tank inner wall surface 23, the three refrigerant guide sections 53 separate the liquid phase refrigerant flowing along the tank inner wall surface 23 from the tank inner wall surface 23, and impart a horizontal inertial force to it.

[0117] As a result, the three refrigerant guide sections 53 in the distribution improvement section 51 can promote a spiral swirling flow of refrigerant downstream as it passes through the distribution improvement section 51 in the stacking direction.

[0118] As a result, the liquid-phase refrigerant flowing along the tank inner wall surface 23 in a circular flow state can be separated and mixed with the gas-phase refrigerant passing through the opening 52, thereby improving the refrigerant distribution performance to the multiple tubes 11 arranged side by side in the stacking direction in the distribution space DS. In the heat exchanger 1 according to the second embodiment, a sufficient amount of refrigerant can also be distributed to the upstream side of the refrigerant flow in the distribution space DS of the second tank 20B, so that the heat exchange performance in the center of the core portion 10 can be sufficiently ensured and a decrease in heat exchange performance can be suppressed.

[0119] As described above, according to the heat exchanger 1 of the second embodiment, even if the number of refrigerant guide portions 53 in the refrigerant distribution member 50 and the presence or absence of flat plate portions 55 are changed, the same effects as those of the above-mentioned embodiment can be obtained from the same configuration and operation.

[0120] Third Embodiment Next, a third embodiment, which differs from the above-described embodiment, will be described with reference to FIG. 10 . In the third embodiment, the configuration of each header tank 20 in the heat exchanger 1 and the arrangement of the refrigerant distribution member 50 differ from those in the above-described embodiment. Therefore, the configuration of the first tank 20A and the second tank 20B in the heat exchanger 1 according to the third embodiment, and the arrangement of the refrigerant distribution member 50 according to the third embodiment will be described in detail. The other configurations of the heat exchanger 1 are the same as those in the above-described embodiment, so a repeated description will be omitted.

[0121] The configuration of a heat exchanger 1 according to the third embodiment will be described with reference to the drawings. As shown in Fig. 10, a separator 25 is not disposed inside a first tank 20A according to the third embodiment. In the heat exchanger 1 according to the third embodiment, an outlet 35 is not provided on the upper side of the first tank 20A in the direction of gravity as in the first embodiment, but is provided on the upper side of the second tank 20B in the direction of gravity.

[0122] In the third embodiment, the inlet 30 of the heat exchanger 1 is provided on the lower side of the first tank 20A in the direction of gravity, similarly to the first embodiment.

[0123] That is, in the heat exchanger 1 according to the third embodiment, the internal space of the first tank 20A and the internal space of the second tank 20B are connected via all of the tubes 11 that constitute the core portion 10 .

[0124] Therefore, in the heat exchanger 1 according to the third embodiment, when the refrigerant flows into the first tank 20A through the inlet 30, it is distributed to all of the tubes 11 that constitute the core portion 10. Therefore, in the third embodiment, the entire internal space of the first tank 20A is the distribution space DS.

[0125] The refrigerant that has flowed through all the tubes 11 that make up the core portion 10 flows into the internal space of the second tank 20B. In the internal space of the second tank 20B, the refrigerant that has flowed out from all the tubes 11 of the core portion 10 is collected and flows out of the heat exchanger 1 through the outlet 35. Therefore, in the third embodiment, the entire internal space of the second tank 20B is the collection space AS.

[0126] Next, the configuration and arrangement of a refrigerant distribution member 50 according to a third embodiment will be described with reference to the drawings. In the heat exchanger 1 according to the third embodiment, the refrigerant distribution member 50 is disposed inside the distribution space DS of the first tank 20A, unlike the above-described embodiments. The refrigerant distribution member 50 according to the third embodiment has the same configuration as the refrigerant distribution member 50 according to the first embodiment, and includes a pair of distribution improvement portions 51 and a flat plate portion 55.

[0127] The configuration of the refrigerant distribution member 50 according to the third embodiment is similar to that of the first embodiment described above, and therefore will not be described again.

[0128] 10, the refrigerant distribution member 50 according to the third embodiment is disposed in the internal space (i.e., distribution space DS) of the first tank 20A. The refrigerant distribution member 50 according to the third embodiment is disposed so that the distribution improvement section 51 is located approximately in the center of the internal space of the first tank 20A in the stacking direction. At this time, the flat plate section 55 of the refrigerant distribution member 50 is disposed along the core plate 21 of the first tank 20A so as to extend downstream of the refrigerant flow in the stacking direction.

[0129] In the heat exchanger 1 according to the third embodiment, the refrigerant distribution member 50 has the same configuration as that of the first embodiment and is disposed in the distribution space DS of the first tank 20A. Therefore, in the third embodiment, the distribution improvement section 51 of the refrigerant distribution member 50 is formed with an opening 52 and a pair of refrigerant guide sections 53.

[0130] Therefore, according to the heat exchanger 1 of the third embodiment, even when the refrigerant flows in a circular flow state inside the first tank 20A, the opening 52 allows the gas phase refrigerant to flow smoothly, thereby suppressing a decrease in heat exchange performance due to pressure loss of the refrigerant.

[0131] In the third embodiment, the distribution improvement section 51 of the refrigerant distribution member 50 is formed with a pair of refrigerant guide sections 53, so that in the case of an annular flow, the liquid-phase refrigerant flowing along the tank inner wall surface 23 can be separated and mixed with the gas-phase refrigerant passing through the opening 52. This promotes a swirling flow of the refrigerant flowing in the internal space of the first tank 20A in a spiral downstream direction, improving the refrigerant distribution performance to the multiple tubes 11 arranged side by side in the stacking direction in the distribution space DS.

[0132] The refrigerant distribution member 50 according to the third embodiment has a flat plate portion 55 with a plurality of communication holes 56 formed therein, and is disposed along the tank inner wall surface 23 of the first tank 20A. Ends of the plurality of tubes 11 inserted through the plurality of insertion openings 21A of the core plate 21 are inserted into the plurality of communication holes 56 formed in the flat plate portion 55. The opening edge of each communication hole 56 in the flat plate portion 55 is adjacent to the end of each tube 11 passing through the core plate 21, so that the liquid-phase refrigerant separated from the tank inner wall surface 23 can be efficiently guided to each tube 11, improving distribution.

[0133] As a result, the heat exchanger 1 of the third embodiment can suppress the deterioration of heat exchange performance due to pressure loss and distribution characteristics by placing the refrigerant distribution member 50 in the distribution space DS of the first tank 20A, even when distributing refrigerant in a circular flow state.

[0134] As described above, according to the heat exchanger 1 of the third embodiment, even if the configuration of the first tank 20A and the second tank 20B is changed, the same effects can be obtained from the configuration and operation as in the above-mentioned embodiment.

[0135] 11 to 13, a fourth embodiment, which differs from the above-described embodiment, will be described. In the fourth embodiment, the internal configuration of each header tank 20 in the heat exchanger 1 and the configuration of the opening 52 and the refrigerant guide portion 53 in the refrigerant distribution member 50 differ from the above-described embodiment.

[0136] Therefore, the configurations of the first tank 20A and the second tank 20B in the heat exchanger 1 according to the fourth embodiment, and the configuration of the refrigerant distribution member 50 according to the fourth embodiment will be described in detail. Since the other configurations of the heat exchanger 1 are the same as those in the above-described embodiments, repeated description will be omitted.

[0137] The heat exchanger 1 according to the fourth embodiment includes a core 10, a first tank 20A, and a second tank 20B, similar to the above-described embodiments. The core 10 is configured by stacking multiple tubes 11 and fins 12 alternately in the vertical direction, similar to the above-described embodiments. The tubes 11 are flat tubular members, and a refrigerant flow path through which a refrigerant flows is formed inside the tubes 11. The tubes 11 constitute part of the refrigerant flow path in the heat exchanger 1, and are an example of a tube member.

[0138] Both the first tank 20A and the second tank 20B are configured to have a core plate 21 and a tank main body 22. The core plate 21 of the first tank 20A and the second tank 20B is formed with a plurality of insertion holes 21A, and longitudinal ends of the tubes 11 are inserted into the insertion holes 21A and joined to the respective insertion holes 21A. As a result, the internal passages of the tubes 11 communicate with the internal spaces of the first tank 20A and the second tank 20B.

[0139] Side plates 13 are provided at both ends of the core portion 10 in the stacking direction to reinforce the core portion 10. The side plates 13 extend parallel to the longitudinal direction and are connected to the core plates 21 at both ends.

[0140] In the heat exchanger 1 according to the fourth embodiment, a separator 25 is also disposed in the internal space of the first tank 20A. The first tank 20A is formed with an inlet 30 and an outlet 35. In the heat exchanger 1 according to the fourth embodiment, as in the first embodiment, the inlet 30 is formed on the lower side of the first tank 20A in the direction of gravity, and the outlet 35 is formed on the upper side of the first tank 20A in the direction of gravity.

[0141] That is, within the internal space of the first tank 20A according to the fourth embodiment, the space below the separator 25 in the direction of gravity constitutes a distribution space DS. And within the internal space of the first tank 20A, the space above the separator 25 in the direction of gravity constitutes a collection space AS. That is, the internal space of the first tank 20A according to the fourth embodiment is vertically partitioned by the separator 25 into two spaces: the distribution space DS and the collection space AS.

[0142] The second tank 20B of the heat exchanger 1 according to the fourth embodiment has two spaces formed therein: a collection space AS and a distribution space DS. Specifically, the space located on the lower side of the second tank 20B in the direction of gravity forms the collection space AS, which collects the refrigerant that has flowed through the tubes 11 that form the lower part of the core 10.

[0143] When the refrigerant flows into the collection space AS of the second tank 20B through the multiple tubes 11 that form the lower portion of the core 10, it flows toward the other side in the stacking direction (upward in the direction of gravity) and flows into the distribution space DS of the second tank 20B. Therefore, the internal space on the other side in the stacking direction (upward in the direction of gravity) inside the second tank 20B forms the distribution space DS.

[0144] Next, the flow of refrigerant in the heat exchanger 1 according to the fourth embodiment will be described. As described above, the schematic configuration of the heat exchanger 1 according to the fourth embodiment is the same as that of the first embodiment. Therefore, the flow of refrigerant in the heat exchanger 1 according to the fourth embodiment is as shown by the outline arrows in FIG. 1 .

[0145] In the heat exchanger 1 of the fourth embodiment, in order to improve the refrigerant distribution performance in the internal space of the second tank 20B, a refrigerant distribution member 50 is arranged in the distribution space DS of the second tank 20B, as in the first embodiment.

[0146] Next, the configuration of the refrigerant distribution member 50 according to the fourth embodiment will be described with reference to the drawings. The refrigerant distribution member 50 according to the fourth embodiment has a distribution improvement portion 51 and a flat plate portion 55, similar to the refrigerant distribution member 50 according to the first embodiment.

[0147] The distribution improvement sections 51 are formed at both ends of the elongated flat plate section 55, and are formed so as to be perpendicular to the flat plate section 55. The flat plate section 55 is arranged so as to be aligned with the core plate 21 inside the header tank 20. Therefore, the distribution improvement sections 51 of the refrigerant distribution member 50 are arranged so as to horizontally cross the internal space of the header tank 20, which extends in the stacking direction.

[0148] The distribution improvement section 51 according to the fourth embodiment is formed with an opening 52, a refrigerant guide section 53, and a support section 54. The opening 52 is located in the center of the distribution improvement section 51 and is configured to allow refrigerant to flow through the opening 52 with minimal pressure loss. Specifically, the opening 52 is formed to be larger than the refrigerant guide section 53 in a horizontal cross section perpendicular to the header tanks 20 extending in the stacking direction.

[0149] As shown in Figures 11 to 13, when the refrigerant distribution member 50 is placed inside the header tank 20, the opening 52 is located in the center of the distribution space DS in a horizontal cross section perpendicular to the header tank 20 extending in the stacking direction.

[0150] The refrigerant guide portion 53 is a guide piece that applies a horizontal inertial force to the refrigerant flowing along the tank inner wall surface 23, guiding the refrigerant to form a swirling flow, and is formed by cutting out a part of the distribution improvement portion 51 that forms the periphery of the opening 52. The refrigerant guide portions 53 according to the fourth embodiment are formed as a pair at positions facing each other across the opening 52, and as shown in Figures 11 to 13, the pair of refrigerant guide portions 53 are each arranged along the tank inner wall surface 23.

[0151] 13, the refrigerant guide portion 53 formed on one side in the width direction is inclined so that it is positioned closer to one side (upper) in the stacking direction as it approaches one side in the longitudinal direction, and the refrigerant guide portion 53 formed on the other side in the width direction is inclined so that it is positioned closer to one side (upper) in the stacking direction as it approaches the other side in the longitudinal direction.

[0152] The refrigerant guide portion 53 is formed by cutting and raising a part of the distribution improvement portion 51, and therefore the base end of the guide piece has an opening that penetrates the distribution improvement portion 51. The refrigerant guide portions 53 are formed so that the opening areas in the distribution improvement portion 51 are different from each other. The support portion 54 is a protrusion formed on the outer periphery of the distribution improvement portion 51 at a position facing the flat plate portion 55.

[0153] 12 , in the distribution improvement section 51, with regard to the flow path cross-sectional area when viewed from the stacking direction, the flow path cross-sectional area AO of the opening 52 is configured to be larger than the flow path cross-sectional area AG of the refrigerant guide section 53. More specifically, the flow path cross-sectional area AO of the opening 52 is configured to be larger than the total area of ​​the flow path cross-sectional areas AG of the refrigerant guide section 53.

[0154] Here, the flow path cross-sectional area when viewed from the stacking direction refers to the area of ​​the portion of the opening area of ​​the opening 52 and the refrigerant guide portion 53 that can pass through the refrigerant distribution member 50 with respect to the flow of refrigerant flowing in the stacking direction. Therefore, the flow path cross-sectional area of ​​the refrigerant guide portion 53 refers to the area of ​​the portion of the opening area of ​​the refrigerant guide portion 53 that is downstream of the tip of the guide piece of the refrigerant guide portion 53.

[0155] The flat plate portion 55 is an elongated plate portion formed with a length in the stacking direction that is shorter than the overall length of the header tank 20. The flat plate portion 55 is disposed in the distribution space DS of the second tank 20B so as to be aligned with the core plate 21 located on the core portion 10 side.

[0156] The flat plate portion 55 of the refrigerant distribution member 50 is formed to have a dimension shorter than the entire length of the second tank 20B and shorter than the distribution space DS of the second tank 20B, so that the arrangement in the internal space of the second tank 20B can be appropriately determined. This allows the flat plate portion 55 of the refrigerant distribution member 50 and the multiple communication holes 56 to efficiently exhibit the effect of improving the refrigerant distribution performance.

[0157] A plurality of communication holes 56 are formed in the flat plate portion 55 of the refrigerant distribution member 50. The communication holes 56 are aligned in the longitudinal direction at the same intervals as the plurality of insertion holes 21A formed in the core plate 21. As described above, the ends of the tubes 11 are inserted into the insertion holes 21A of the core plate 21, and therefore, each insertion hole 21A is positioned to face the end of the tube 11.

[0158] 13 , a gap W of a predetermined distance is formed between the surface of the flat plate portion 55 facing the tubes 11 (in other words, the surface facing the core plate 21) and the end of the tube 11. As a result, in the heat exchanger 1 according to the fourth embodiment, refrigerant is allowed to flow in the stacking direction inside the header tank 20 through the gap W formed between the flat plate portion 55 and the tubes 11.

[0159] Here, the flow path cross-sectional area is 75 to 150 mm ２ When an annular flow flows into the header tank 20, a strong inertial force tends to act on the liquid-phase refrigerant along the tank inner wall surface 23 in the stacking direction. In particular, when the heat exchanger 1 is used as an evaporator (i.e., in a heat-absorbing state), the inertial force tends to act more strongly on the refrigerant than when it is used as a condenser. For this reason, if a configuration is adopted in which the refrigerant distribution member 50 is not provided, of the multiple tubes 11 connected to the distribution space DS of the second tank 20B, more refrigerant is distributed to the tubes 11 on the downstream side of the refrigerant flow, and less refrigerant is distributed to the tubes 11 on the upstream side of the refrigerant flow.

[0160] As described above, if the refrigerant distribution performance in the distribution space DS of the second tank 20B becomes uneven, the heat exchange performance of the heat exchanger 1 will be reduced. In particular, when a configuration in which the refrigerant flow turns once in the second tank 20B is adopted, as in the heat exchanger 1, it is considered that this is more likely to be a factor in reducing heat exchange performance. The tubes 11 located upstream of the refrigerant flow in the distribution space DS of the second tank 20B constitute the central portion of the core 10 of the heat exchanger 1, and are the portion through which outside air, which is the target of heat exchange, can easily pass. Considering this point, improving the refrigerant distribution performance in the distribution space DS of the second tank 20B has a significant impact on improving the heat exchange performance of the heat exchanger 1.

[0161] In the heat exchanger 1 of the fourth embodiment, a refrigerant distribution member 50 is placed in the distribution space DS of the second tank 20B to improve the distribution of refrigerant to each tube 11 that constitutes the core portion 10, thereby suppressing a decrease in heat exchange performance even in situations where annular flow occurs.

[0162] Next, the effect of the refrigerant distribution member 50 in the second tank 20B of the heat exchanger 1 according to the fourth embodiment will be described with reference to FIGS.

[0163] 11 and 12 , the opening 52 of the refrigerant distribution member 50 is located at the center of the horizontal cross section of the distribution space DS of the second tank 20B extending in the stacking direction. When the refrigerant flows in a circular flow through the second tank 20B according to the fourth embodiment, the gas phase refrigerant mainly flows through the center of the header tank 20.

[0164] 12 , with respect to the flow path cross-sectional area when viewed from the stacking direction, the flow path cross-sectional area AO of the opening 52 is larger than the flow path cross-sectional area of ​​the refrigerant guide portion 53. In the fourth embodiment, the flow path cross-sectional area AO of the opening 52 is larger than the total value of the flow path cross-sectional areas AG of the pair of refrigerant guide portions 53.

[0165] By locating the opening 52 of the refrigerant distribution member 50 in the center of the horizontal cross section of the distribution space DS of the second tank 20B, the gas-phase refrigerant, which accounts for the majority of the refrigerant flowing through the second tank 20B, can flow with minimal pressure loss. As a result, whether the heat exchanger 1 is used as a condenser or an evaporator, a smooth flow of the gas-phase refrigerant can be achieved. That is, with the heat exchanger 1 according to the fourth embodiment, even when an annular flow occurs, the opening 52 of the refrigerant distribution member 50 can suppress a decrease in heat exchange performance due to refrigerant pressure loss.

[0166] The distribution improvement section 51 according to the fourth embodiment is formed with a pair of refrigerant guide sections 53 that face each other across the opening 52 and are arranged along the tank inner wall surface 23 of the second tank 20B, as shown in Figures 11 and 12. The refrigerant guide section 53 formed on one side in the width direction is inclined so that it is positioned closer to one side (upper) in the stacking direction as it approaches one side in the longitudinal direction. The refrigerant guide section 53 formed on the other side in the width direction is inclined so that it is positioned closer to one side (upper) in the stacking direction as it approaches the other side in the longitudinal direction.

[0167] When the refrigerant flows in a circular flow state inside the header tank 20, the liquid-phase refrigerant flows along the tank inner wall surface 23. Therefore, when the refrigerant flows along the tank inner wall surface 23 and reaches the distribution improvement section 51, the pair of refrigerant guide sections 53 separate the liquid-phase refrigerant flowing along the tank inner wall surface 23 from the tank inner wall surface 23, and apply a horizontal inertial force to the refrigerant.

[0168] 12, the base ends of the refrigerant guide portions 53 are each opened to have a flow path cross-sectional area AG. Therefore, the cut-and-raised guide pieces can guide the refrigerant flow passing through the openings in a predetermined direction. That is, the pair of refrigerant guide portions 53 in the distribution improvement portion 51 can promote a spiral swirling flow of the refrigerant passing through the distribution improvement portion 51 in the stacking direction downstream of the refrigerant flow. In the fourth embodiment, the refrigerant passing through the refrigerant guide portions 53 swirls at least one time (preferably multiple times) along the tank inner wall surface 23 while flowing inside the header tank 20 in the stacking direction.

[0169] As a result, the liquid-phase refrigerant flowing along the tank inner wall surface 23 in a circular flow state can be separated and mixed with the gas-phase refrigerant passing through the opening 52, thereby improving the refrigerant distribution performance to the multiple tubes 11 arranged in the stacking direction in the distribution space DS.

[0170] With respect to the flow path cross-sectional area when viewed from the stacking direction, the flow path cross-sectional area AO of the opening 52 is larger than the flow path cross-sectional area of ​​the refrigerant guide portion 53. Therefore, in the heat exchanger 1 according to the fourth embodiment, it is possible to achieve both a reduction in pressure loss due to the opening 52 formed in the center of the distribution improvement portion 51 and an improvement in distribution performance due to the pair of refrigerant guide portions 53. Furthermore, in the fourth embodiment, it is possible to distribute a sufficient amount of refrigerant even to the upstream side of the refrigerant flow in the distribution space DS of the second tank 20B, so that heat exchange performance in the center of the core portion 10 can be sufficiently ensured and a decrease in heat exchange performance can be suppressed.

[0171] 13, the flat plate portion 55 of the refrigerant distribution member 50 according to the fourth embodiment is disposed along the second tank 20B. The plurality of communication holes 56 formed in the flat plate portion 55 are disposed opposite, at intervals, the ends of the plurality of tubes 11 inserted through the plurality of insertion holes 21A of the core plate 21. Specifically, a gap W is formed between the surface of the flat plate portion 55 facing the core plate 21 (i.e., the refrigerant flow path side) and the ends of the tubes 11.

[0172] As a result, in the distribution space DS of the second tank 20B, the refrigerant flows in an annular flow state through a space defined by the tank inner wall surface 23 on the tank main body 22 side and the flat plate portion 55 of the refrigerant distribution member 50. When the refrigerant flowing in an annular flow state enters the distribution space DS of the second tank 20B, the liquid-phase refrigerant flowing along the tank inner wall surface 23 flows along the tank inner wall surface 23 defined by the tank main body 22 and the flat plate portion 55.

[0173] 11 to 13, the opening edge of each communication hole 56 in the flat plate portion 55 is positioned to face the end of each tube 11 inserted through the core plate 21, and a gap W is formed between the surface of the flat plate portion 55 and the end of the tube 11. Because the flow of the refrigerant constituting the swirling flow is not impeded in the gap W, the influence of the tube 11 on the swirling flow formed by the pair of refrigerant guide portions 53 can be reduced. As a result, in the heat exchanger 1 according to the fourth embodiment, the swirling flow in the stacking direction inside the second tank 20B is smooth, further improving the refrigerant distribution performance of the refrigerant distribution member 50.

[0174] Therefore, the heat exchanger 1 of the fourth embodiment can suppress the deterioration of heat exchange performance due to pressure loss and distribution characteristics by placing a refrigerant distribution member 50 in the distribution space DS of the second tank 20B, even when distributing refrigerant in a circular flow state.

[0175] According to the heat exchanger 1 of the fourth embodiment, the inlet 30 is formed in the lower portion of the first tank 20A in the direction of gravity, and the outlet 35 is formed in the upper portion of the first tank 20A in the direction of gravity. Therefore, gravity can be made to act in the opposite direction to the flow of refrigerant in the stacking direction during the process from the inlet 30 to the outlet 35, and gravity can be effectively used to improve the distribution performance of the refrigerant to the upstream side of the refrigerant flow in the distribution space DS of the second tank 20B.

[0176] As described above, the heat exchanger 1 according to the fourth embodiment constitutes an exterior heat exchanger in the refrigeration cycle of a vehicle air conditioner, and functions as either a heat absorber that absorbs heat from the exterior air into the refrigerant, or a radiator that radiates heat from the refrigerant to the exterior air, depending on the operating mode. The heat exchanger 1 according to the first embodiment has a core 10 formed by stacking multiple tubes 11 between a first tank 20A and a second tank 20B.

[0177] In the refrigerant distribution member 50 according to the fourth embodiment, an opening 52 is formed in the center of the distribution improvement section 51, and a pair of refrigerant guide sections 53 are formed around the opening 52 so as to face each other across the opening 52. As shown in Fig. 12, with respect to the flow path cross-sectional area when viewed from the stacking direction, the flow path cross-sectional area AO of the opening 52 is larger than the flow path cross-sectional area AG of the refrigerant guide section 53.

[0178] This allows the gas-phase refrigerant, which accounts for the majority of the refrigerant flowing inside the header tank 20, to flow through the refrigerant distribution member 50 with minimal pressure loss. Furthermore, because the flow path cross-sectional area AG of the refrigerant guide portion 53 is also ensured, a swirling flow can be generated by the refrigerant guide portion 53, improving the refrigerant distribution performance in the header tank 20. That is, in the fourth embodiment, by making the flow path cross-sectional area AO of the opening 52 larger than the flow path cross-sectional area AG of the refrigerant guide portion 53, the effect of pressure loss when the refrigerant passes through the refrigerant distribution member 50 can be reduced and the refrigerant distribution performance of the refrigerant distribution member 50 can be improved.

[0179] As shown in Figures 11 to 13, inside the second tank 20B of the heat exchanger 1 of the fourth embodiment, a gap W is formed between the surface of the flat portion 55 on the refrigerant flow path side and the end of the tube 11.

[0180] The swirl flow of the refrigerant flowing inside the second tank 20B flows through the gap W, thereby circulating in the stacking direction while suppressing the influence of the tubes 11, etc. As a result, in the heat exchanger 1 according to the fourth embodiment, the swirl flow in the stacking direction inside the second tank 20B is smooth, further improving the refrigerant distribution performance of the refrigerant distribution member 50.

[0181] 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.

[0182] In the above-described embodiment, the heat exchanger according to the present disclosure is applied to an exterior heat exchanger in a refrigeration cycle of a vehicle air conditioner, but is not limited to this. The heat exchanger according to the present disclosure can be applied to various other forms as long as it functions as a heat radiator in one circuit configuration of a refrigeration cycle and as a heat sink in another circuit configuration.

[0183] In the above-described embodiment, the heat exchanger according to the present disclosure is applied to an exterior heat exchanger in a refrigeration cycle of a vehicle air conditioner. Therefore, the heat exchange target with which the refrigerant exchanges heat is outside air whether it is a radiator or a heat sink. However, this is not limited to this. The heat exchange target with which the refrigerant exchanges heat in the heat exchanger according to the present disclosure may be different targets when it functions as a radiator or a heat sink. In addition, the heat exchange target in this case is not limited to a gas such as outside air, and a liquid heat medium (e.g., coolant) can also be used.

[0184] In the heat exchanger 1 according to the present disclosure, the refrigerant guide portion 53 of the refrigerant distribution member 50 is formed by cutting out a portion of the distribution improvement portion 51, but this is not limited to this. The shape of the refrigerant guide portion 53 can be variously configured as long as it can impart a horizontal inertial force to the refrigerant flowing in the stacking direction. Furthermore, the refrigerant guide portion 53 formed by cutting out a portion of the distribution improvement portion 51 as in the above-described embodiment may be processed to increase the horizontal inertial force imparted to the refrigerant flowing in the stacking direction.

[0185] In the first and third embodiments described above, the refrigerant distribution member 50 having the flat plate portion 55 has a configuration in which the distribution improvement portion 51 is provided at each end of the flat plate portion 55, but the present invention is not limited to this. If the distribution improvement portion 51 is formed at one end of the flat plate portion 55, the refrigerant distribution performance in the distribution space DS of the header tank 20 can be improved. In this case, it is desirable to position the refrigerant distribution member 50 so that the distribution improvement portion 51 is located upstream of the distribution space DS with respect to the refrigerant flow in the stacking direction.

[0186] In the distribution improvement section 51 of the refrigerant distribution member 50, the flow path cross-sectional area of ​​the opening 52 is configured to be larger than the flow path cross-sectional area of ​​the refrigerant guide section 53. This is not limited to the fourth embodiment, and can be applied to various aspects. For example, even when this embodiment is applied to the first to third embodiments, the same effects as those of the fourth embodiment can be achieved.

[0187] Furthermore, the formation of the gap W between the flat plate portion 55 of the refrigerant distribution member 50 and the end of the tube 11 is not limited to the fourth embodiment described above. That is, as long as the refrigerant distribution member 50 has the flat plate portion 55 and the refrigerant flow path is formed by the tube 11, a configuration in which the gap W is provided can be adopted, and this may be applied to the first embodiment, for example.

[0188] The features of the heat exchanger disclosed in this specification are as follows: (Item 1) A heat exchanger comprising: a plurality of refrigerant flow paths (11) stacked in a predetermined stacking direction and through which a refrigerant flows; a first tank (20, 20A) extending in the stacking direction of the plurality of refrigerant flow paths and connected to one end of the plurality of refrigerant flow paths; and a second tank (20, 20B) extending in the stacking direction of the plurality of refrigerant flow paths and connected to the other end of the plurality of refrigerant flow paths, wherein the heat exchanger is used in a heat absorption state in which the refrigerant absorbs heat from a heat exchange target and in a heat release state in which the heat possessed by the refrigerant is released to the heat exchange target, wherein distribution spaces (DS) for distributing the refrigerant to the plurality of refrigerant flow paths and collection spaces (AS) for collecting the refrigerant that has flowed through the plurality of refrigerant flow paths are formed inside the first tank and the second tank, and a refrigerant distribution member (50) is disposed in the distribution space of at least one of the first tank and the second tank to improve the distribution performance of the refrigerant to the plurality of refrigerant flow paths with respect to the flow of the refrigerant in the stacking direction, and the refrigerant distribution member is a heat exchanger including: an opening (52) disposed in a central portion of the distribution space in a cross section perpendicular to the stacking direction, the opening allowing the refrigerant to flow in the stacking direction in the heat absorption state and the heat release state; and a refrigerant guide portion (53) disposed around the opening along an inner wall surface of at least one of the first tank and the second tank, the refrigerant distribution member having a distribution improvement portion (51) formed to correspond to a cross section perpendicular to the stacking direction in the distribution space, the distribution improvement portion having the opening and the refrigerant guide portion, and wherein, with respect to a flow path cross-sectional area as viewed from the stacking direction, a flow path cross-sectional area (AO) of the opening formed in the central portion of the distribution improvement portion is larger than a flow path cross-sectional area (AG) of the refrigerant guide portion. (Item 3) The heat exchanger according to Item 1 or 2, wherein the refrigerant distribution member has a flat plate portion (55) extending in the stacking direction and arranged along the inner wall surface, and a plurality of communication holes (56) formed in the flat plate portion in the stacking direction and communicating with ends of the plurality of refrigerant flow paths located on the inner wall surface side.(Item 4) The heat exchanger according to item 3, wherein the refrigerant flow path is constituted by a tube member (11) formed in a tubular shape having an internal space through which the refrigerant flows, and a gap (W) is formed between an end of the tube member and a surface of the flat plate portion of the refrigerant distribution member on the side of the refrigerant flow path. (Item 5) The heat exchanger according to item 3 or 4, wherein the flat plate portion of the refrigerant distribution member extends in the stacking direction by a length shorter than the entire length in the stacking direction of at least one of the first tank and the second tank. (Item 6) The heat exchanger according to item 2, wherein the first tank has an interior formed with the distribution space (DS) for distributing the refrigerant that has flowed into the interior of the first tank to portions of the plurality of refrigerant flow paths, and the collection space (AS) for collecting the refrigerant that has flowed through the remaining portions of the plurality of refrigerant flow paths, and the second tank has an interior formed with the distribution space (DS) for distributing the refrigerant that has flowed into the interior of the second tank to the remaining portions of the plurality of refrigerant flow paths, and the collection space (AS) for collecting the refrigerant that has flowed through the portions of the plurality of refrigerant flow paths. (Item 7) The heat exchanger according to item 6, wherein the refrigerant distribution member is disposed in the distribution space of the second tank, and improves the distribution performance of the refrigerant to the remaining portions of the plurality of refrigerant flow paths. (Item 8) A heat exchanger according to any one of items 1 to 7, comprising an inlet (30) for causing the refrigerant to flow into the inside of the distribution space of at least one of the first tank and the second tank, and an outlet (35) for causing the refrigerant to flow out from the inside of the collection space of at least one of the first tank and the second tank, wherein the inlet is disposed on a lower side in the direction of gravity of at least one of the first tank and the second tank, and the outlet is disposed on an upper side in the direction of gravity of at least one of the first tank and the second tank.

[0189] 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 which is laminated and arranged in a predetermined lamination direction and in which a plurality of refrigerant flow paths (11) through which a refrigerant flows, a first tank (20, 20A) extending in the lamination direction of the plurality of refrigerant flow paths and connected to one end side of the plurality of refrigerant flow paths, and a second tank (20, 20B) extending in the lamination direction of the plurality of refrigerant flow paths and connected to the other end side of the plurality of refrigerant flow paths are provided, and which is used in an endothermic state in which heat is absorbed from a heat exchange target by the refrigerant and in a heat dissipation state in which heat of the refrigerant is dissipated to the heat exchange target. In the first tank and the second tank, a distribution space (DS) for distributing the refrigerant to the plurality of refrigerant flow paths and a collection space (AS) for collecting the refrigerant that has flowed through the plurality of refrigerant flow paths are formed. In at least one of the distribution spaces of the first tank and the second tank, a refrigerant distribution member (50) for improving the distribution performance of the refrigerant to the plurality of refrigerant flow paths with respect to the flow of the refrigerant in the lamination direction is arranged. The refrigerant distribution member is arranged at the central portion of the distribution space in a cross section perpendicular to the lamination direction, and has an opening (52) that allows the flow of the refrigerant in the lamination direction in the endothermic state and the heat dissipation state, and a refrigerant guide portion (53) that is arranged along at least one inner wall surface of the first tank and the second tank around the opening and imparts a horizontal inertial force to the flow of the refrigerant.

2. The heat exchanger according to claim 1, wherein the refrigerant distribution member is formed so as to correspond to a cross section perpendicular to the lamination direction in the distribution space, and has a distribution improvement portion (51) having the opening and the refrigerant guide portion. With respect to the flow path cross-sectional area when viewed from the lamination direction, the flow path cross-sectional area (AO) of the opening formed at the central portion of the distribution improvement portion is larger than the flow path cross-sectional area (AG) in the refrigerant guide portion.

3. The heat exchanger according to claim 1 or 2, wherein the refrigerant distribution member has a flat plate portion (55) that extends in the lamination direction and is arranged along the inner wall surface, and a plurality of communication holes (56) that are formed side by side in the lamination direction in the flat plate portion and communicate with the ends of the plurality of refrigerant flow paths located on the side of the inner wall surface.

4. The refrigerant flow path is constituted by a tube member (11) formed in a tubular shape having an internal space through which the refrigerant flows. A gap (W) is formed between the surface on the refrigerant flow path side of the flat plate portion of the refrigerant distribution member and the end portion of the tube member. The heat exchanger according to claim 3.

5. The flat plate portion of the refrigerant distribution member extends in the stacking direction with a length shorter than the total length in the stacking direction in at least one of the first tank and the second tank. The heat exchanger according to claim 3.

6. Inside the first tank, there are formed a distribution space (DS) for distributing the refrigerant flowing into the first tank to a part of the plurality of refrigerant flow paths, and an aggregation space (AS) for aggregating the refrigerant that has flowed through the remaining parts of the plurality of refrigerant flow paths. Inside the second tank, there are formed a distribution space (DS) for distributing the refrigerant flowing into the second tank to the remaining parts of the plurality of refrigerant flow paths, and an aggregation space (AS) for aggregating the refrigerant that has flowed through a part of the plurality of refrigerant flow paths. The heat exchanger according to claim 2.

7. The refrigerant distribution member is disposed in the distribution space of the second tank, and improves the distribution performance of the refrigerant to the remaining parts of the plurality of refrigerant flow paths. The heat exchanger according to claim 6.

8. It has an inlet (30) for flowing the refrigerant into the distribution space of at least one of the first tank and the second tank, and an outlet (35) for flowing the refrigerant out from the aggregation space of at least one of the first tank and the second tank. The inlet is disposed on the lower side in the gravitational direction in at least one of the first tank and the second tank, and the outlet is disposed on the upper side in the gravitational direction in at least one of the first tank and the second tank. The heat exchanger according to claim 1.

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