Heat exchanger and air-conditioning device provided with heat exchanger

Abstract

The heat exchanger is provided with a plurality of flat tubes arranged in a first direction and each extending in a second direction intersecting the first direction. The flat tube has a tube wall provided with a heat transfer flow path through which a fluid flows in an internal space, the tube wall has a flat plate-shaped tube side wall portion facing in a first direction, and a through hole is formed in the tube side wall portion. Adjacent flat tubes have a connecting portion that connects the tube walls to each other and interconnects the heat transfer flow paths inside the tube walls to each other, and the connecting portion is configured from a connecting protrusion formed on at least one of the opposing tube side wall portions of the adjacent flat tubes, the connecting protrusion protruding in the first direction from the peripheral edge portion of the through-hole.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to a headerless heat exchanger and an air conditioning device provided with the same. BACKGROUND

[0002] Among heat exchangers, there is a heat exchanger in which a plurality of heat exchange members are layered and heat exchange of a first fluid such as refrigerant and a second fluid such as air is performed. In such a heat exchanger, a headerless heat exchanger is disclosed (for example, refer to Patent Literature 1). For the heat exchanger of Patent Literature 1, as a first fluid flow path, there are a plurality of heat transfer flow paths provided in the layering direction of the heat exchange members in a substantially rectangular shape and extending in the length direction of the heat exchange members, respectively, and a header flow path extending in the layering direction of the heat exchange members and communicating the plurality of heat transfer flow paths. In the heat exchanger of Patent Literature 1, the heat exchange members are plate pieces, and by recesses and protrusions provided in the plate pieces, a heat transfer flow path of refrigerant is formed between the plate piece and the adjacent plate piece on one side in the layering direction, and an air flow path is formed between the plate piece and the adjacent plate piece on the other side in the layering direction. Further, by providing through holes in the portions where the plate pieces and the adjacent plate pieces on the other side in the layering direction are joined, the heat transfer flow paths of the refrigerant are formed to communicate with each other.

[0003] PRIOR ART DOCUMENTS

[0004] PATENT LITERATURE

[0005] Patent Literature 1: Japanese Patent Application Publication No. 2020-176791 SUMMARY

[0006] PROBLEMS TO BE SOLVED BY THE INVENTION

[0007] However, the heat exchanger of Patent Literature 1 is configured by layering plate pieces, and the heat transfer flow path of refrigerant and the air flow path are formed by recesses and protrusions provided in the plate pieces, and the header flow path of refrigerant is formed by through holes provided in the joining portions of the plate pieces, and thus the pitch of the plate pieces and the total width of the heat transfer flow path of refrigerant and the air flow path in the layering direction of the plate pieces are determined by the size of the recesses and protrusions of the plate pieces (i.e., the depth of the grooves or the height of the protrusions). Further, although it is possible to change the width of the air flow path in the layering direction of the plate pieces depending on the size of the recesses and protrusions, there is a limit to the change in the size of the recesses and protrusions since the recesses and protrusions are directly processed on the plate pieces, and in addition, if the width of the air flow path is to be expanded, the width of the heat transfer flow path of refrigerant will be reduced. In this way, the heat exchanger of Patent Literature 1 is configured with low design freedom of the air flow path.

[0008] The present disclosure is made to solve the above-described problems, and aims to improve the design freedom of the air flow path in a headerless heat exchanger.

[0009] MEANS FOR SOLVING THE PROBLEMS

[0010] The first heat exchanger according to the present disclosure includes a plurality of flat tubes arranged in a first direction and each extending in a second direction intersecting the first direction, wherein the flat tubes each have a tube wall provided with a heat transfer flow path through which a fluid circulates in an internal space, the tube wall has a flat plate-shaped tube side wall portion facing in the first direction, a through hole is formed in the tube side wall portion, and adjacent flat tubes have a connection portion connecting the tube walls to each other and connecting the heat transfer flow paths in the internal spaces of the tube walls to each other, the connection portion is constituted by a connection protrusion portion formed on at least one of the facing tube side wall portions of the adjacent flat tubes, and the connection protrusion portion protrudes in the first direction from a peripheral portion of the through hole.

[0011] Further, the air conditioning device according to the present disclosure includes a refrigerant circuit connecting a compressor, the heat exchanger, an expansion valve, and an indoor heat exchanger via refrigerant pipes, through which a fluid circulates.

[0012] Effects of the Invention

[0013] In the heat exchanger and the air conditioning device including the same according to the present disclosure, the heat transfer flow path of the fluid is provided in the tube wall of the flat tube, and the adjacent flat tubes have the connection portion connecting the tube walls to each other and connecting the heat transfer flow paths to each other, and the connection portion protrudes in the first direction from the peripheral portion of the through hole of the tube side wall portion. Therefore, the width of the first direction of the air flow path on the outside of the connection portion can be changed by changing the length of the connection portion, and thus the width of the first direction of the air flow path can be expanded without reducing the width of the first direction of the heat transfer flow path of the fluid. Therefore, the design freedom of the air flow path can be improved in the heat exchanger without a header. BRIEF DESCRIPTION OF DRAWINGS

[0014] Figure 1 FIG. 1 is a perspective view showing the general configuration of a heat exchanger according to Embodiment 1.

[0015] Figure 2 FIG. 2 is a refrigerant circuit diagram of an air conditioning device according to Embodiment 1. Figure 1

[0016] Figure 3 FIG. 3 is a perspective view showing the configuration of a flat tube of the heat exchanger according to Embodiment 1. Figure 1

[0017] Figure 4 FIG. 4 is a longitudinal sectional view of the heat exchanger according to Embodiment 1. Figure 1

[0018] Figure 5 FIG. 5 is a partial sectional view showing the A-A section of the portion surrounded by the ellipse of the heat exchanger according to Embodiment 1. Figure 4 FIG. 6 is a longitudinal sectional view of a heat exchanger according to Embodiment 2.​​​

[0019] Figure 6 is a perspective view showing the outline configuration of the heat exchanger according to Embodiment 2.

[0020] Figure 7 is a longitudinal sectional view of the heat exchanger according to Figure 6

[0021] Figure 8 is a view showing one configuration example of the joint portion enclosed by the frame of Figure 7

[0022] Figure 9 is a perspective view showing the configuration of the heat exchanger according to Embodiment 3.

[0023] Figure 10 is a perspective view showing the outline configuration of the heat exchanger according to Embodiment 4.

[0024] Figure 11 is a longitudinal sectional view of the heat exchanger according to Figure 10

[0025] Figure 12 is a horizontal sectional view of the section at plane B of the heat exchanger according to Figure 10

[0026] Figure 13 is a horizontal sectional view of the section at plane C of the heat exchanger according to Figure 10

[0027] Figure 14 is a perspective view showing the outline configuration of the heat exchanger according to Embodiment 5.

[0028] Figure 15 is a longitudinal sectional view showing the configuration of the position restriction portion of the flat tube of the heat exchanger according to Embodiment 6. DETAILED DESCRIPTION

[0029] Hereinafter, the heat exchanger according to Embodiment 1 will be described with reference to the drawings and the like. In the following drawings including Figure 1 , the relative dimensional relationship and the shape of each constituent member are sometimes different from the actual ones. In the following drawings, elements denoted by the same reference numerals are the same or equivalent configurations, which is common throughout the specification. In addition, in order to make understanding easier, terms indicating directions (for example, "upper", "lower", "right", "left", "front", "rear", and the like) are appropriately used, but these expressions are merely described as such for the convenience of explanation and do not limit the arrangement and orientation of the device or the member. In the specification, the positional relationship of each constituent member to each other, the extension direction of each constituent member, and the arrangement direction of each constituent member are in principle the parameters when the heat exchanger is set in a usable state.​​​​​

[0030] Implementation method 1.

[0031] Figure 1 1 is a perspective view showing a schematic configuration of a heat exchanger according to Embodiment 1. Figure 1 As shown, the heat exchanger 101 has a plurality of flat tubes 10 arranged in a first direction D1 and connected to each other. The flat tubes 10 extend in the direction in which the tube axis Ax extends (hereinafter also referred to as the tube axis direction), and present a flat shape that is long in one direction in a cross section perpendicular to the tube axis Ax. Hereinafter, the first direction D1 in which the plurality of flat tubes 10 are arranged is sometimes referred to as the stacking direction, the tube axis direction of the flat tube 10 is sometimes referred to as the second direction D2 or the length direction of the flat tube 10, and the length direction of the cross section of the flat tube 10 is sometimes referred to as the third direction D3 or the width direction of the flat tube 10. In addition, the following is defined as: Figure 1 As shown, the heat exchanger 101 is arranged such that the stacking direction (first direction D1) of the flat tubes 10 is the left-right direction. Furthermore, each flat tube 10 is defined as being arranged such that its tube axis Ax is oriented in the vertical direction perpendicular to the stacking direction (first direction D1), and its width direction (third direction D3) is oriented in the front-back direction perpendicular to both the tube axis and the stacking direction.

[0032] The arrangement of the heat exchanger 101 or the angle between the stacking direction (first direction D1) of the flat tubes 10 in the heat exchanger 101 and the tube axis direction (second direction D2) of each flat tube 10 is not limited to the above-described arrangement. For example, the heat exchanger 101 may be arranged at an angle so that the tube axis direction of each flat tube 10 is inclined relative to the vertical direction. Alternatively, if the heat exchanger 101 is arranged so that the stacking direction (first direction D1) of the flat tubes 10 is oriented horizontally, the heat exchanger 101 may be configured so that the tube axis direction of each flat tube 10 is inclined relative to the vertical direction.

[0033] Gaps serving as air flow paths P2 are formed between the tube walls 11 of the flat tubes 10 adjacent in the stacking direction (first direction D1 ). In the heat exchanger 101 , air flows through each gap along the width direction (third direction D3 ) of the flat tubes 10 .

[0034] On the flat tubes 10 arranged at one end in the stacking direction among the plurality of flat tubes 10, a first pipe a and a second pipe b that become the inlet and outlet of a fluid (for example, refrigerant or the like) in the heat exchanger 101 are provided. Here, the fluid that flows through the flat tubes 10 can be either refrigerant or water or brine or the like. A fluid flow path is provided between the first pipe a and the second pipe b in the heat exchanger 101. The fluid flow path is provided in the plurality of flat tubes 10. The heat exchanger 101 performs heat exchange between air and the fluid. Hereinafter, the description will be given assuming that the fluid that flows through the plurality of flat tubes 10 is refrigerant.

[0035] The adjacent flat tubes 10 have a joint portion 19 for joining the tube walls 11 of each other. Each flat tube 10 has a tube wall 11, and a joint protrusion portion 19a, 19b (refer to the later-described Figure 3 ) that extends outward from the tube wall 11 in the first direction D1 and constitutes the joint portion 19. The flat tube 10 has a tube structure that ensures an internal space for the refrigerant to flow through in the length direction (second direction D2) thereof, that is, from the upper end to the lower end of the tube wall 11. The detailed structure of the flat tube 10 will be described later.

[0036] The end portions on both sides in the length direction (second direction D2) of the flat tube 10 are sealed. Specifically, the heat exchanger 101 has a tube sealing portion 20 that plugs each open end le of the flat tube 10 on both sides in the length direction (second direction D2) thereof. In the example of Figure 1 , on each flat tube 10, the tube sealing portion 20 is provided at two positions on the upper side and the lower side of the flat tube. The tube sealing portion 20 is joined to the open end le of the flat tube 10 by a joining means such as brazing or an adhesive.

[0037] Figure 2 is a refrigerant circuit diagram of an air conditioning device 100 that mounts the Figure 1 heat exchanger 101. As shown in Figure 2 , the heat exchanger 101 constitutes a part of a refrigerant circuit 100c for circulating refrigerant in the air conditioning device 100.

[0038] The air conditioning device 100 has a compressor 102, a heat exchanger 101, an expansion valve 105, an indoor heat exchanger 104, and a four-way valve 103. In Figure 2 , the compressor 102, the heat exchanger 101, the expansion valve 105, and the four-way valve 103 are provided in an outdoor unit 100A, and the indoor heat exchanger 104 is provided in an indoor unit 100B. The first pipe a and the second pipe b (refer to Figure 1 ) that become the inlet and outlet of refrigerant of the heat exchanger 101 are connected to the four-way valve 103 and the expansion valve 105 of the refrigerant circuit 100c.

[0039] The compressor 102, the heat exchanger 101, the expansion valve 105, the indoor heat exchanger 104, and the four-way valve 103 are connected to each other via refrigerant pipes, thereby constituting a refrigerant circuit 100c in which refrigerant circulates. In the air conditioning device 100, by the operation of the compressor 102, a refrigeration cycle in which refrigerant circulates while changing phase in the compressor 102, the heat exchanger 101, the expansion valve 105, and the indoor heat exchanger 104 is performed.

[0040] In the outdoor unit 100A, an outdoor fan 107 that forcibly passes outdoor air through the heat exchanger 101 is provided. The heat exchanger 101 performs heat exchange between the refrigerant and the flow of outdoor air generated by the operation of the outdoor fan 107. In the indoor unit 100B, an indoor fan 106 that forcibly passes indoor air through the indoor heat exchanger 104 is provided. The indoor heat exchanger 104 performs heat exchange between the refrigerant and the flow of indoor air generated by the operation of the indoor fan 106.

[0041] The operation of the air conditioning device 100 can be switched between a cooling operation and a heating operation. In Figure 2 In the air conditioning device 100, the flow direction of the refrigerant at the time of the cooling operation is indicated by a dashed arrow, and the flow direction of the refrigerant at the time of the heating operation is indicated by a solid arrow. The four-way valve 103 is an electromagnetic valve that switches the flow path of the refrigerant in accordance with the switching of the cooling operation and the heating operation of the air conditioning device 100. The four-way valve 103 guides the refrigerant from the compressor 102 to the heat exchanger 101 and guides the refrigerant from the indoor heat exchanger 104 to the compressor 102 at the time of the cooling operation, and guides the refrigerant from the compressor 102 to the indoor heat exchanger 104 and guides the refrigerant from the heat exchanger 101 to the compressor 102 at the time of the heating operation.

[0042] At the time of the cooling operation of the air conditioning device 100, the refrigerant compressed by the compressor 102 is sent to the heat exchanger 101. In the heat exchanger 101, the refrigerant releases heat to the outdoor air and condenses. Then, the refrigerant is sent to the expansion valve 105, is depressurized by the expansion valve 105, and is then sent to the indoor heat exchanger 104. Then, the refrigerant absorbs heat from the indoor air in the indoor heat exchanger 104 and evaporates, and then returns to the compressor 102. Therefore, at the time of the cooling operation of the air conditioning device 100, the heat exchanger 101 functions as a condenser, and the indoor heat exchanger 104 functions as an evaporator.

[0043] During the heating operation of the air conditioning apparatus 100, the refrigerant compressed by the compressor 102 is sent to the indoor heat exchanger 104. In the indoor heat exchanger 104, the refrigerant releases heat to the indoor air and condenses. Then, the refrigerant is sent to the expansion valve 105, is depressurized by the expansion valve 105, and is then sent to the heat exchanger 101. Then, the refrigerant in the heat exchanger 101 absorbs heat from the outdoor air and evaporates, and then returns to the compressor 102. Thus, during the heating operation of the air conditioning apparatus 100, the heat exchanger 101 functions as an evaporator, and the indoor heat exchanger 104 functions as a condenser.

[0044] Figure 3 is a perspective view showing the constitution of the flat tube 10 of the heat exchanger 101 of Figure 1 . Figure 4 is a longitudinal sectional view of the heat exchanger 101 of Figure 1 . Figure 5 is a partial sectional view showing the A-A section of the portion surrounded by the ellipse of Figure 4 . Hereinafter, the refrigerant flow path of the heat exchanger 101 and the structure of the flat tube 10 will be described in detail using Figures 1-5 . In Figure 1 , Figure 4 and Figure 5 , the flow direction of the refrigerant in the case where the heat exchanger 101 is used as a condenser is indicated by a solid blank arrow. In addition, in Figure 5 , the flow direction of the air is indicated by a broken blank arrow.

[0045] As shown in Figures 3-5 , the tube wall 11 has: substantially flat plate-shaped tube side wall portions 10a and 10b facing in the first direction Dl; and curved surface-shaped connecting wall portions 10c and 10d connecting the tube side wall portion 10a and the tube side wall portion 10b at each end portion of the tube side wall portions 10a and 10b on both sides in the third direction D3. The tube side wall portion 10a and the tube side wall portion 10b each have a rectangular shape in which the long side extends in the length direction (the second direction D2) of the flat tube 10 and the short side extends in the width direction (the third direction D3) of the flat tube 10. The tube side wall portions 10a and 10b are each flat plate-shaped, but the "flat plate-shaped" in the present application can also be a surface that is not entirely constituted by a plane, as long as the structure is visible as a whole as extending in a plane. For example, a recess, a protrusion, or a wavy shape can be formed in a part of the region extending in a plane. Figure 4 In Figure 4 , the wall portion on the left side of the tube wall 11 is the tube side wall portion 10a, and the wall portion on the right side of the tube wall 11 is the tube side wall portion 10b. As shown in , a through hole hla penetrating in the first direction Dl is formed in the left side tube side wall portion 10a, and a through hole hlb penetrating in the first direction Dl is formed in the right side tube side wall portion 10b.

[0046] The connecting portion 19 of the adjacent flat tubes 10 has a cylindrical shape with a hollow portion Sg extending in the first direction D1. The connecting portion 19 is composed of a connecting protrusion 19a or 19b extending from the peripheral edge of the through hole h1a or h1b in at least one of the opposing tube sidewalls 10a or 10b of the adjacent flat tubes 10 toward the opposing tube sidewall 10b or 10a. Figure 4 In the embodiment, the connecting portion 19 is composed of cylindrical connecting protrusions 19a and 19b formed on the opposing tube sidewalls 10a and 10b of adjacent flat tubes 10. These through-holes h1a and h1b and connecting protrusions 19a and 19b can be formed, for example, by flanging by forming a hole in a flat plate portion of the flat tube 10 and deforming the flat plate portion at the periphery thereof into a cylindrical shape.

[0047] like Figure 4 As shown, the connecting portion 19 connects the through-holes h1a and h1b provided in the tube side walls 10a and 10b via the hollow portion Sg, thereby connecting the internal spaces of the adjacent tube walls 11. Furthermore, the connecting portion 19 functions to define the air flow path P2, which is the space outside the connecting portion 19 and the hollow portion Sg inside the connecting portion.

[0048] like Figure 4 As shown, the through hole h1a, the through hole h1b and the connecting portion 19 are formed inward of the open ends 1e on both sides in the longitudinal direction (second direction D2) of the flat tube 10. Figure 1 In the heat exchanger 101 thus configured, the through-holes h1a and h1b, the connecting protrusions 19a and 19b of each flat tube 10 are formed below and above the upper opening ends 1e of the flat tubes 10 .

[0049] Such a flat tube 10 can be manufactured, for example, by pre-forming through-holes h1a and h1b and connecting protrusions 19a and 19b in a blank member of the flat tube 10, and then forming the member by roll forming. Alternatively, the connecting protrusions 19a and 19b can be formed by raising the peripheral edges of the through-holes h1a and h1b when forming the blank member of the flat tube 10. For example, a metal material with high thermal conductivity, such as aluminum, copper, or brass, can be used for the flat tube 10.

[0050] The refrigerant flow path in the heat exchanger 101 has: a heat transfer flow path Pl a provided in the tube wall 11 of each flat tube 10 and extending in the length direction (second direction D2) of the flat tube 10; and a header flow path Pl b extending in the stacking direction (first direction Dl) of the plurality of flat tubes 10 and communicating the heat transfer flow paths Pl a of the plurality of flat tubes 10. One end of the header flow path Pl b extending in the first direction Dl is connected to the first pipe a (refer to Figure 1 ).

[0051] The through hole hla, the through hole hlb, and the hollow portion Sg of the connecting portion 19, and the like constitute the header flow path Pl b, and the refrigerant flows through the hollow portion Sg. In the heat exchanger 101, the connecting portion 19 is constituted by a portion of the flat tube 10, and the portion of the header flow path Pl b that is disposed between the tube walls 11 of the flat tube 10 is the hollow portion Sg inside the connecting portion 19. Therefore, in the heat exchanger 101, the header flow path Pl b is formed by the flat tube 10 that is the heat exchange member, and thus, a header other than the plurality of flat tubes 10 is not required, and a configuration without a header is achieved.

[0052] In the example of Figure 5 , inside each flat tube 10, a first partition 30 extending in the length direction (second direction D2, vertical direction) of the flat tube 10 and partitioning the internal space of the tube wall 11 of the flat tube 10 in the width direction (third direction D3, front-rear direction) of the flat tube 10 is provided. Also, the upper end 30e of the first partition 30 is provided at a position lower than the open end 10e on the upper side of the flat tube 10. Thus, in the upper portion of the internal space of the tube wall 11, a return flow path Pl at through which the refrigerant flows in the front-rear direction (third direction D3) is formed. That is, in the example of Figure 5 , the heat transfer flow path Pl a of the refrigerant has an inverted U shape including the return flow path Pl at.

[0053] In the example of Figure 1 , Figures 3-5 , as shown in Figure 4 , the refrigerant flow path of the heat exchanger 101 is constituted by a plurality of heat transfer flow paths Pl a and a header flow path Pl b and a header flow path Pl c (refer to Figure 3 ) provided side by side in the front-rear direction in the lower portion of the heat exchanger 101. The header flow path Pl b is constituted by the hollow portions Sg of the plurality of connecting portions 19 provided on the front side in the lower portion of the heat exchanger 101, and the like. Also, as shown in Figure 3 , the header flow path Pl c is constituted by the hollow portions (not shown) of the plurality of connecting portions 18 provided on the rear side in the lower portion of the heat exchanger 101, and the like. As shown in Figure 1 and Figure 4As shown, the right end of the front-side header flow passage P1b is connected to the first pipe a, and the right end of the rear-side header flow passage P1c is connected to the second pipe b.

[0054] In addition, Figure 1 , Figures 3-5 The heat exchanger 101 shown is an example of the heat exchanger 101 of the present disclosure, and the shape of the heat transfer flow passage P1a, the presence or absence, number, and arrangement of the first partition 30 in the flat tube 10, and the arrangement of the first pipe a and the second pipe b in the heat exchanger 101, and the like can be appropriately changed.

[0055] Next, an example of the operation of the heat exchanger 101 when the heat exchanger 101 is used as a condenser will be described using Figures 1-2 and Figures 4-5 As shown in Figure 1 , the high-temperature and high-pressure gas-state refrigerant flows into the heat exchanger 101 from the first pipe a. As shown in Figure 4 , in the heat exchanger 101, the high-temperature and high-pressure gas-state refrigerant first flows into the front-side header flow passage P1b that penetrates the lower portions of the plurality of flat tubes 10 in the left-right direction, and flows from right to left in the header flow passage P1b. In this process, the high-temperature and high-pressure gas-state refrigerant is distributed to the heat transfer flow passages P1a provided in the tube walls 11 of the plurality of flat tubes 10 and flows in. The high-temperature and high-pressure gas-state refrigerant flowing into each heat transfer flow passage P1a flows upward on the front side of the internal space of the tube wall 11, flows rearward along the return flow passage P1at (see Figure 5 ) on the upper portion of the internal space of the tube wall 11, and then flows downward on the rear side of the internal space of the tube wall 11. At this time, the high-temperature and high-pressure gas-state refrigerant exchanges heat with the air flowing through the gaps between the tube walls 11 of the flat tubes 10 (i.e., the air flow passages P2), and is cooled by the air and condensed into high-pressure gas-liquid two-phase-state refrigerant. The high-pressure gas-liquid two-phase-state refrigerant from the plurality of heat transfer flow passages P1a flows into the header flow passage P1c (see Figure 3 ) that penetrates the rear portions of the plurality of flat tubes 10, and converges in the header flow passage P1c. As shown in Figure 1 and Figure 3 , the high-pressure gas-liquid two-phase-state refrigerant converging in the header flow passage P1c flows out to the outside of the heat exchanger 101 (for example, the expansion valve 105 of the refrigerant circuit 100c shown in Figure 2 ) from the second pipe b connected to the header flow passage P1c.

[0056] As shown in Figure 4As shown, the joining portions 19 joining the tube walls 11 of the adjacent flat tubes 10 to each other communicate the heat transfer flow paths Pl a with each other, and divide the refrigerant flow paths (particularly, the header flow paths Plb) and the air flow paths P2 outside at the gaps between the tube walls 11. Also, the joining portions 19 are constituted by the joining protruding portions 19a, 19b that are a part of the flat tubes 10.

[0057] Therefore, in the heat exchanger 101 of the present disclosure, as long as the length of the joining portions 19 is set according to the desired tube pitch Lp, the tube pitch Lp and the width of the air flow paths P2 in the first direction Dl can be changed without reducing the width of the heat transfer flow paths Pl a of the refrigerant in the first direction Dl. Thus, compared with the conventional heat exchanger made of stacked sheets, the heat exchanger 101 having a high degree of freedom in the design of the air flow paths can be provided.

[0058] In addition, in the configuration in which the heat transfer flow paths of the refrigerant and the air flow paths are provided between the stacked sheets as in the conventional one, compared with the configuration of the present disclosure, the area of the joint portion of the heat exchange members to each other (the sheets to each other in the conventional configuration) becomes large, and there are problems such as an increase in the ventilation resistance, a deterioration in the drainage of the condensation water, or a blockage of the air flow paths P2 due to frost. In addition, due to the increase in the ventilation resistance, the deterioration in the drainage of the condensation water, or the blockage of the air flow paths P2 due to frost, the heat exchange performance is reduced.

[0059] On the other hand, in the heat exchanger 101 of the present disclosure, the area of the joint portion of the heat exchange members to each other (i.e., the flat tubes 10 to each other) can be minimized, and even in the case where the width of the air flow paths P2 in the first direction Dl is enlarged, as long as the length of the joining portions 19 is changed, the change in the components can be small.

[0060] The joining protruding portion 19a and the joining protruding portion 19b constituting the joining portion 19 are, for example, a fitting configuration. A specific example of such a configuration is described. In the right side tube side wall portion 10b in the left side flat tube 10 among the flat tubes 10 adjacent in the first direction Dl, a right side protruding cylindrical joining protruding portion 19b is formed, and in the left side tube side wall portion 10a in the right side flat tube 10, a left side protruding cylindrical joining protruding portion 19a is formed. The inner diameter Dia of the joining protruding portion 19a is set to be substantially the same size as the outer diameter Dob of the joining protruding portion 19b, and when the flat tubes 10 are stacked, the flat tubes 10 are joined to each other by fitting the right side end portion of the joining protruding portion 19b into the joining protruding portion 19a. In this case, the depth of the fitting and the length of the first direction Dl of each joining protruding portion 19a, 19b can be appropriately determined so that the ends of each joining protruding portion 19a, 19b do not protrude into the heat transfer flow paths Pl a of the facing flat tubes 10 when the tube pitch L is set to the desired length.

[0061] Alternatively, the joining protrusion 19a and the joining protrusion 19b can not be fitted together. For example, the outer diameter Dob of the joining protrusion 19b can be set to be slightly smaller than the inner diameter Dia of the joining protrusion 19a, and the end portion on the right side of the joining protrusion 19b can be inserted into the joining protrusion 19a so that the tube pitch Lp is the desired length, and then the joining protrusion 19a and the joining protrusion 19b can be joined by brazing or an adhesive or the like.

[0062] Alternatively, the shape of the joining protrusion 19a and the joining protrusion 19b that constitute the joining portion 19 is not limited to the shape described above, and only needs to divide the refrigerant collecting passage P1b and the air passage P2 by the joining protrusion 19a and the joining protrusion 19b. Alternatively, the joining protrusion 19a and the joining protrusion 19b can be formed so as to partially overlap in the first direction D1 (see FIG. 2), or the end portions can be joined to each other without overlapping in the first direction D1. In the configuration in which the joining protrusion 19a and the joining protrusion 19b partially overlap in the first direction D1, since a portion of the joining portion 19 in the first direction D1 is a double-walled structure, the strength of the joining portion 19 can be improved compared to the configuration in which the end portions are joined to each other. Figure 4 Alternatively, the shape of the joining protrusion 19a and the joining protrusion 19b that constitute the joining portion 19 is not limited to the shape described above, and only needs to divide the refrigerant collecting passage P1b and the air passage P2 by the joining protrusion 19a and the joining protrusion 19b. Alternatively, the joining protrusion 19a and the joining protrusion 19b can be formed so as to partially overlap in the first direction D1 (see FIG. 2), or the end portions can be joined to each other without overlapping in the first direction D1. In the configuration in which the joining protrusion 19a and the joining protrusion 19b partially overlap in the first direction D1, since a portion of the joining portion 19 in the first direction D1 is a double-walled structure, the strength of the joining portion 19 can be improved compared to the configuration in which the end portions are joined to each other.

[0063] As described above, the heat exchanger 101 according to Embodiment 1 of the present disclosure is a heat exchanger 101 that includes a plurality of flat tubes 10 arranged in a first direction D1 and each extending in a second direction D2 that intersects the first direction D1. The flat tubes 10 have tube walls 11 that have heat transfer passages P1a for a fluid to flow through the inside. The tube walls 11 have flat plate-shaped tube side wall portions 10a, 10b facing the first direction D1, and through holes h1a, h1b are formed in the tube side wall portions 10a, 10b. In addition, adjacent flat tubes 10 have a joining portion 19 that connects the tube walls 11 to each other and connects the heat transfer passages P1a inside the tube walls 11 to each other. The joining portion 19 is constituted by joining protrusions 19a, 19b that protrude in the first direction D1 from the peripheral edge portions of the through holes h1a, h1b formed on at least one of the facing tube side wall portions 10a, 10b of the adjacent flat tubes 10.

[0064] In the heat exchanger 101, the heat transfer flow path Pla is provided in the tube wall 11 of the flat tube 10, and the adjacent flat tubes 10 have the connecting portion 19 connecting the tube walls 11 to each other and making the heat transfer flow paths Pla communicate with each other, the connecting portion 19 being constituted by the connecting protrusion portions 19a, 19b protruding in the first direction Dl from the peripheral edge portions of the through holes hla, hlb of the tube side wall portions 10a, 10b. In the conventional heat exchanger, the heat transfer flow path of the refrigerant and the air flow path are formed by directly processing the corrugation on the plate, and the heat transfer flow paths are made to communicate with each other by the through holes provided at the joint portions of the plates, so that if the width of the air flow path is to be enlarged, the width of the heat transfer flow path of the refrigerant becomes small. On the other hand, in the heat exchanger 101 of the present disclosure, the heat transfer flow path Pla of the fluid is provided in the flat tube 10, and the connecting portion 19 making the heat transfer flow paths Pla communicate with each other is constituted by the connecting protrusion portions 19a, 19b protruding in the first direction Dl from the tube side wall portions 10a, 10b. Therefore, since the width of the first direction Dl of the air flow path P2 (i.e., the gap between the tube walls 11) can be changed by changing the length of the connecting portion 19, the width of the first direction Dl of the air flow path P2 can be enlarged without reducing the width of the first direction Dl of the heat transfer flow path Pla of the fluid. Thus, the design freedom of the air flow path can be improved in the heat exchanger 101 without the header.

[0065] Further, the connecting portion 19 is constituted by the connecting protrusion portions 19a, 19b formed on both of the facing tube side wall portions 10a, 10b of the adjacent flat tubes 10. Thus, compared with the case where the connecting portion 19 is constituted by one of the connecting protrusion portions 19a, 19b, the connecting protrusion portions 19a, 19b are less likely to intrude into the tube wall 11.

[0066] Further, the connecting protrusion portions 19a, 19b formed on both of the facing tube side wall portions 10a, 10b of the adjacent flat tubes 10 overlap at least a part in the first direction Dl. Thus, a part of the connecting portion 19 can be formed as a double-walled structure, and the strength of the connecting portion 19 can be improved.

[0067] Further, the flat tube 10 has the first partition 30 disposed in the internal space of the tube wall 11, extending in the second direction D2, and dividing the internal space in a third direction D3 orthogonal to the first direction Dl and the second direction D2. Further, at least one end (for example, the upper end 30e) of the first partition 30 in the second direction D2 is located inward of both ends (both open ends 10e) of the flat tube 10 in the second direction D2.

[0068] Thus, since the free change of the fluid flow path can be achieved, for example, in the case where the heat transfer flow path Pla is folded up and down in correspondence with the position of the inlet and outlet of the fluid, it is not necessary to arrange two rows of flat tubes 10 and provide a cross-row header.

[0069] Embodiment 2.

[0070] Figure 6 is a perspective view showing the outline configuration of the heat exchanger 101b according to Embodiment 2. Figure 7 is Figure 6 a longitudinal sectional view of the heat exchanger 101b of Figure 8 is a view showing one example of the configuration of the joint portion 19 enclosed by the frame in Figure 7 Figure 6 and Figure 8 , the flow direction of the refrigerant in the case where the heat exchanger 101b is used as a condenser is indicated by a blank arrow in solid line. The heat exchanger 101b according to Embodiment 2 will be described based on Figures 6-8 Embodiment 2. The heat exchanger 101b according to Embodiment 2 is a configuration in which the configuration of the pipe sealing portion 20 in the heat exchanger 101 according to Embodiment 1 is changed. In addition, regarding the configuration elements having the same functions and effects as those of Embodiment 1, the same reference numerals are marked and the description thereof is omitted.

[0071] In the heat exchanger 101 according to Embodiment 1, the pipe sealing portion 20 is provided at two positions of the upper side and the lower side of each flat tube 10, whereas in the heat exchanger 101b according to Embodiment 2, a common pipe sealing portion 120 is provided with respect to the plurality of flat tubes 10 at two positions of the upper side and the lower side of the plurality of flat tubes 10.

[0072] As shown in Figure 6 , the pipe sealing portion 120 is configured by a substantially rectangular plate-like member that covers the open ends le of the plurality of flat tubes 10. The open ends le of the plurality of flat tubes 10 are fixed to the pipe sealing portion 120 at a constant pitch. In detail, as shown in Figure 7 , the pipe sealing portion 120 has a plurality of groove portions 120r and flat portions 120p between the groove portions 120r. In the pipe sealing portion 120, the groove portions 120r are formed at a constant pitch Lr in the stacking direction (the first direction Dl) of the flat tubes 10 so as to extend in the width direction (the third direction D3) of the flat tubes 10 along the open ends le of the flat tubes 10. The pitch Lr of the groove portions 120r in the pipe sealing portion 120 is the same as the tube pitch Lp of the flat tubes 10. The end portions of the flat tubes 10 including the open ends le are arranged in each groove portion 120r of the pipe sealing portion 120. The width of the groove portions 120r in the first direction Dl is substantially the same size as the thickness of the flat tubes 10 in the first direction Dl, and is the same or slightly larger.

[0073] ​In the lower tube sealing portion 120, a drainage hole 120h for draining water such as condensation water or frost melt water generated by the flat tube 10 is formed in the flat portion 120p except for the portion (i.e., the groove portion 120r) that blocks the lower open end 10e of the flat tube 10.

[0074] When stacking the flat tubes 10 during the manufacture of the heat exchanger 101b, the longitudinal ends of each flat tube 10 are inserted into the grooves 120r of the tube sealing portion 120, with the facing connecting protrusions 19a and 19b of adjacent flat tubes 10 engaged with each other. This arrangement allows the plurality of flat tubes 10 to be arranged with a constant tube pitch Lp in the first direction D1. Subsequently, the grooves 120r of the tube sealing portion 120 are joined to the longitudinal ends of each flat tube 10 by means of brazing or adhesive. Furthermore, the connecting protrusions 19a and 19b of adjacent flat tubes 10 are joined by means of brazing or adhesive. Furthermore, by securing the open ends 1e of the plurality of flat tubes 10 to the tube sealing portion 20 using a joining means, the sealing strength of the open ends 1e of the longitudinal ends of the flat tubes 10 can be improved.

[0075] like Figure 7 As shown, in the structure in which the positions of the plurality of flat tubes 10 in the stacking direction (first direction D1) are determined by the tube sealing portion 120, in order to facilitate adjustment of the distance between the tube walls 11 of adjacent flat tubes 10 when the flat tubes 10 are stacked, a slightly engaged structure is preferred over a structure in which the connecting protrusion 19b is embedded in the connecting protrusion 19a.

[0076] As an example of such a configuration, use Figure 8 In Figure 8 In the example, the connecting protrusions 19b and 19a that constitute the connecting portion 19 of adjacent flat tubes 10 are each formed into a cylindrical shape, curved so that the opening diameter at the distal end is larger than that at the proximal end. Connecting protrusion 19b is formed around the through-hole h1b in the tube sidewall 10b, while connecting protrusion 19a is formed around the through-hole h1a in the tube sidewall 10a. Through-hole h1b is smaller than through-hole h1a. When stacking the flat tubes 10, when connecting protrusion 19b is inserted into connecting protrusion 19a, the distal end of connecting protrusion 19b hooks onto the inner surface of connecting protrusion 19a.

[0077] Thus, compared to a configuration where the connecting protrusions 19b of the connecting portion 19 are fitted together, a slightly engaged configuration can reduce the contact area between the connecting protrusions 19b and 19b, thereby reducing friction. Consequently, when multiple flat tubes 10 are installed in the tube sealing portion 120, the distance between the tube walls 11 of adjacent flat tubes 10 can be easily adjusted.

[0078] Figure 8 The connecting protrusions 19a and 19b of the embodiment 2 can also be formed in the same manner as the connecting protrusions 19a and 19b of the embodiment 1. Figure 4 The connecting protrusions 19a and 19b of the embodiment 2 can also be formed in the same manner as the connecting protrusions 19a and 19b of the embodiment 1.

[0079] As described above, the heat exchanger 101b of the embodiment 2 is configured on the basis of the heat exchanger 101 of the embodiment 1, and further includes the plate-shaped tube sealing portion 120 which is arranged at at least one end (the open end 10e) of the plurality of flat tubes 10 in the second direction D2 and covers one end of the heat transfer flow path Pal of the plurality of flat tubes 10. Further, one end (the open end 1e) of the flat tube 10 is fixed in the groove portion 120r formed in the tube sealing portion 120 at a constant pitch Lr. In addition, as described above, since the end portion of the flat tube 10 is inserted in the groove portion 120r, the strength is excellent. In addition, as the concave-convex structure on the tube sealing portion 120 side which is combined with the end portion of the flat tube 10, a convex portion (not shown) can be formed instead of the groove portion 120r. A tube sealing portion 120 in which convex portions are formed at a constant pitch Lr can be used, and each convex portion is inserted in the inside of the end portion of the flat tube 10.

[0080] Thus, the heat exchange area can be ensured, and the flat tubes 10 can be arranged at a constant tube pitch Lp by the tube sealing portion 120.

[0081] Embodiment 3.

[0082] Figure 9 is a perspective view showing the configuration of the heat exchanger 101c according to the embodiment 3. In Figure 9 , the flow direction of the refrigerant in the case where the heat exchanger 101c is used as a condenser is indicated by a solid blank arrow or a dashed blank arrow. The flow direction of the refrigerant in the case where the heat exchanger 101c is used as an evaporator is indicated by a solid arrow or a dashed arrow. Figure 9 The heat exchanger 101c according to the embodiment 3 will be described. The heat exchanger 101c of the embodiment 3 is configured by additionally providing the heat transfer fins 50 in the heat exchanger 101b of the embodiment 2. In addition, regarding the configuration elements having the same functions and effects as those of the embodiment 2, the same reference numerals are attached and the description thereof is omitted.

[0083] In the heat exchanger 101c of the embodiment 3, as the heat transfer fins 50, for example, corrugated fins which connect the facing tube side wall portions 10a, 10b of the adjacent flat tubes 10 to each other are provided in each gap, that is, the air flow path P2 of the plurality of flat tubes 10. In this case, each of the facing tube side wall portions 10a, 10b of the adjacent flat tubes 10 and the heat transfer fin 50 are brazed to each other. Thus, the heat exchange between the refrigerant and the air is promoted, and the heat exchange performance of the heat exchanger 101c is improved.

[0084] In addition, the heat exchanger 101c of Embodiment 3, like the heat exchanger 101 of Embodiment 1, has high design freedom for the air flow path P2, and therefore, the addition of the heat transfer fins 50 is easy. Here, the pitch Lr of the groove portions 120r of the tube sealing portions 120 can be set as desired.

[0085] As described above, the heat exchanger 101c of Embodiment 3, by adding the heat transfer fins 50, increases the heat transfer area, and thus, the heat exchange performance can be improved.

[0086] Embodiment 4.

[0087] Figure 10 is a perspective view showing the schematic configuration of the heat exchanger 101d according to Embodiment 4. Figure 11 is a longitudinal sectional view of the heat exchanger 101d of Figure 10 . Figure 12 is a transverse sectional view of the heat exchanger 101d of Figure 10 , taken at a plane B. Figure 13 is a transverse sectional view of the heat exchanger 101d of Figure 10 , taken at a plane C. In Figures 10-12 , the flow direction of the refrigerant in the case where the heat exchanger 101d is used as a condenser is indicated by a solid white arrow. In addition, in Figures 12-13 , the flow direction of the air is indicated by a broken white arrow. Based on Figures 10-13 , the heat exchanger 101d according to Embodiment 4 will be described. The heat exchanger 101d of Embodiment 4 is configured by changing the positions of the first and second pipes a and b in the heat exchanger 101b of Embodiment 2, and with this change, the refrigerant flow path is also changed. In addition, regarding the configuration elements having the same functions and effects as those of Embodiment 1, the same reference numerals are given and the description thereof will be omitted.

[0088] As shown in Figure 10 , in the heat exchanger 101d of Embodiment 4, the second pipe b is provided on the flat tubes 110 arranged at one end in the stacking direction among the plurality of flat tubes 110, and the first pipe a is provided on the flat tubes 110 arranged at the other end in the stacking direction. Specifically, the first pipe a is provided at the lower portion of the leftmost flat tube 110 and at the center in the front-rear direction, and the second pipe b is provided at the lower portion of the rightmost flat tube 110 and at the center in the front-rear direction.

[0089] In the heat exchanger 101d, the first partition 30 is not provided in the tube wall 111 of the flat tube 110 (see Figure 6 of Embodiment 2). On the other hand, the heat exchanger 101d is configured such that the second partition 40 is provided in the tube wall 111 of the flat tube 110.Figure 11 As shown in FIG. 1, the heat exchanger 101d is provided with the second partition 40 that divides the manifold flow path Plb in the stacking direction (the first direction Dl) of the flat tubes 110. The second partition 40 interrupts the travel of the refrigerant in the first direction Dl between the adjacent heat transfer flow paths Pla. Specifically, the second partition 40 is provided in the through hole hla of the tube-side wall portion 110a or the through hole hlb of the tube-side wall portion 110b of the link portion 119.

[0090] In the example shown in FIG. 1, the second partition 40 is provided in the manifold flow path Plb connected to the first pipe a, and the manifold flow path Plb is divided into the left-side manifold flow path portion Plbl connected to the first pipe a and the right-side manifold flow path portion Plb2. The second partition 40 is provided between the link protrusion portion 119b of the left-side flat tube 110 and the link protrusion portion 119a of the right-side flat tube 110 so as to be visible from the outside. That is, at the position where the second partition 40 is provided, the respective ends of the link protrusion portion 119a and the link protrusion portion 119b are engaged with the second partition 40. Figure 11 As shown in FIG. 1, the heat exchanger 101d is provided with the second partition 40 that divides the manifold flow path Plb in the stacking direction (the first direction Dl) of the flat tubes 110. The second partition 40 interrupts the travel of the refrigerant in the first direction Dl between the adjacent heat transfer flow paths Pla. Specifically, the second partition 40 is provided in the through hole hla of the tube-side wall portion 110a or the through hole hlb of the tube-side wall portion 110b of the link portion 119.

[0091] Figure 10 As shown in FIG. 1, the heat exchanger 101d is provided with the second partition 40 that divides the manifold flow path Plb in the stacking direction (the first direction Dl) of the flat tubes 110. The second partition 40 interrupts the travel of the refrigerant in the first direction Dl between the adjacent heat transfer flow paths Pla. Specifically, the second partition 40 is provided in the through hole hla of the tube-side wall portion 110a or the through hole hlb of the tube-side wall portion 110b of the link portion 119. Figure 11 As shown in FIG. 1, the heat exchanger 101d is provided with the second partition 40 that divides the manifold flow path Plb in the stacking direction (the first direction Dl) of the flat tubes 110. The second partition 40 interrupts the travel of the refrigerant in the first direction Dl between the adjacent heat transfer flow paths Pla. Specifically, the second partition 40 is provided in the through hole hla of the tube-side wall portion 110a or the through hole hlb of the tube-side wall portion 110b of the link portion 119.

[0092] In the heat exchanger 101d, the first partition 30 is not provided in the tube wall 111 of the flat tube 110 (see the example shown in FIG. 2 of Embodiment 2), and therefore, the internal space of the tube wall 111 becomes one I-shaped heat transfer flow path Pla.

[0093] Figure 6 In the heat exchanger 101d, the first partition 30 is not provided in the tube wall 111 of the flat tube 110 (see the example shown in FIG. 2 of Embodiment 2), and therefore, the internal space of the tube wall 111 becomes one I-shaped heat transfer flow path Pla.

[0094] ​​Furthermore, the second separator 40 is provided within the lower header flow path P1b between the tube walls 111 of at least one pair of adjacent flat tubes 110 among the plurality of flat tubes 110. That is, a plurality of second separators 40 may be provided in the lower header flow path P1b. In this case, by also providing one or more second separators 40 in the upper header flow path P1d, a serpentine refrigerant flow path can be formed.

[0095] Next, use Figure 2 、 Figures 10-13 An example of the operation of the heat exchanger 101d when the heat exchanger 101d is used as a condenser will be described. Figure 10 As shown in FIG, a high-temperature and high-pressure gaseous refrigerant flows from the first pipe a into the heat exchanger 101d. Figure 11 As shown, in the heat exchanger 101d, the high-temperature and high-pressure gaseous refrigerant first flows into the left manifold flow path portion P1b1 in the manifold flow path P1b that passes through the lower portion of the plurality of flat tubes 110, and flows from left to right in the manifold flow path portion P1b1. In this process, the high-temperature and high-pressure gaseous refrigerant is distributed to flow into the heat transfer flow paths P1a provided in the tube walls 111 of the respective flat tubes 110 on the left among the plurality of flat tubes 110. The high-temperature and high-pressure gaseous refrigerant that has flowed into the heat transfer flow paths P1a of the plurality of flat tubes 110 on the left flows upward in the internal space of the tube wall 111, and then flows into the manifold flow path P1d (refer to FIG. 1 ) that passes through the upper portion of the plurality of flat tubes 110. Figure 12 ) After merging, while flowing to the right in the header flow path P1d, it is distributed to the heat transfer flow paths P1a of the right-side plurality of flat tubes 110 and flows downward. Figure 13 As shown, when flowing upward in the heat transfer flow paths P1a of the plurality of flat tubes 110 on the left, and when flowing downward in the heat transfer flow paths P1a of the plurality of flat tubes 110 on the right, the high-temperature and high-pressure gaseous refrigerant exchanges heat with the air flowing through the gaps between the tube walls 111 of the flat tubes 110 (i.e., the air flow paths P2), thereby dissipating heat to the air and condensing to become a high-pressure gas-liquid two-phase refrigerant. Figure 11 As shown, the high-pressure gas-liquid two-phase refrigerant from each heat transfer flow path P1a of the plurality of flat tubes 110 on the right side flows into the right header flow path portion P1b2 of the header flow path P1b, merges in the header flow path portion P1b2, and flows from the second pipe b to the outside of the heat exchanger 101d (for example, Figure 2 The refrigerant flows out of the expansion valve 105 of the refrigerant circuit 100c shown.

[0096] As described above, the heat exchanger 101d according to Embodiment 4 is provided with the second partition 40 that is interposed between the tube walls 111 of at least one set of adjacent flat tubes 110 among the plurality of flat tubes 110 and that cuts off the flow of the aforementioned fluid between the heat transfer flow paths via the connection portions 119.

[0097] Thus, the header flow path P1b can be partitioned in a simple manner, and by providing the second partition 40 at the connection portion 119, the heat exchanger 101d can be configured so that the tightness of the second partition 40 can be confirmed from the outside.

[0098] Embodiment 5.

[0099] Figure 14 is a perspective view showing the general configuration of the heat exchanger 101e according to Embodiment 5. In Figure 14 , the flow direction of the refrigerant in the case where the heat exchanger 101e is used as a condenser is indicated by solid-line blank arrows or dashed-line blank arrows. The flow direction of the refrigerant in the case where the heat exchanger 101e is used as an evaporator is indicated by solid-line arrows or dashed-line arrows. Figure 14 The heat exchanger 101e according to Embodiment 5 will be described. Embodiment 5 is an embodiment in which the first partition 30 of Embodiment 1 is added to the heat exchanger 101d of Embodiment 4 in which the second partition 40 is provided. In addition, regarding the configuration elements having the same functions and effects as Embodiment 4, the same reference numerals are marked and the description thereof is omitted.

[0100] As shown in Figure 14 , in the heat exchanger 101e according to Embodiment 5, the second pipe b is provided at the flat tubes 210 arranged at one end in the stacking direction among the plurality of flat tubes 210, and the first pipe a is provided at the flat tubes 210 arranged at the other end in the stacking direction. In detail, the first pipe a is provided at the lower portion and the front side of the leftmost flat tube 210, and the second pipe b is provided at the lower portion and the front side of the rightmost flat tube 210.

[0101] In Figure 14 the example, the refrigerant flow path of the heat exchanger 101e is constituted by a plurality of heat transfer flow paths P1a and header flow paths P1b and P1c arranged side by side in the front and rear at the lower portion of the heat exchanger 101e. The header flow path P1b is constituted by the hollow portions Sg (see Figure 4 ) of the plurality of connection portions 219 provided at the front side at the lower portion of the heat exchanger 101e, and the like. In addition, the header flow path P1c is constituted by the hollow portions (not shown) of the plurality of connection portions 18 (see Figure 3 ) provided at the rear side at the lower portion of the heat exchanger 101e, and the like. The left end of the header flow path P1b at the front side is connected to the first pipe a, and the right end is connected to the second pipe b.

[0102] In the heat exchanger 101e, the first partition 30 is provided in the tube wall 211 of each flat tube 210, and a return flow path P1at is formed in the upper portion of the inner space of the tube wall 211, through which the refrigerant flows in the front-rear direction, as in the case of the heat exchanger 1 of Embodiment 1. That is, the heat transfer flow path P1a of the refrigerant has an inverted U shape including the return flow path P1at.

[0103] In addition, the front-side header flow path P1b is divided by the second partition 40 into a left-side header flow path portion P1b1 connected to the first pipe a and a right-side header flow path portion P1b2 connected to the second pipe b.

[0104] Next, the operation of the heat exchanger 101e will be described with reference to FIG. 10. Figure 14 An example of the operation of the heat exchanger 101e in the case where the heat exchanger 101e is used as a condenser will be described. The refrigerant in a high-temperature and high-pressure gaseous state flows into the heat exchanger 101e from the first pipe a. In the heat exchanger 101e, the refrigerant in a high-temperature and high-pressure gaseous state first flows into the left-side header flow path portion P1b1 in the front-side header flow path P1b, and in the course of flowing from left to right in this header flow path portion P1b1, flows into each heat transfer flow path P1a of a plurality of flat tubes 210 on the left side. The refrigerant in a high-temperature and high-pressure gaseous state flowing in each heat transfer flow path P1a of the plurality of flat tubes 210 on the left side flows in the order of upper, rear, and lower in the inner space of the tube wall 211, and thereafter converges in the rear-side header flow path P1d, and in the course of flowing to the right in this header flow path P1d, flows into each heat transfer flow path P1a of a plurality of flat tubes 210 on the right side, and flows in the order of upper, front, and lower. In the course of flowing along each heat transfer flow path P1a of the plurality of flat tubes 210 on the left side, and in the course of flowing along each heat transfer flow path P1a of the plurality of flat tubes 210 on the right side, the refrigerant in a high-temperature and high-pressure gaseous state exchanges heat with air flowing through the gaps between the tube walls 211 of the flat tubes 210 (i.e., the air flow path P2) via the tube walls 211, and is condensed by radiating heat to the air, and becomes refrigerant in a high-pressure gas-liquid two-phase state. Then, the refrigerant in a high-pressure gas-liquid two-phase state from each heat transfer flow path P1a of the plurality of flat tubes 210 on the right side flows into the right-side header flow path portion P1b2 in the front-side header flow path P1b, converges in this header flow path portion P1b2, and flows out from the second pipe b to the outside of the heat exchanger 101e (e.g., the refrigerant circuit 100c shown in FIG. 9) via the expansion valve 105. Figure 2

[0105] Embodiment 6.

[0106] Figure 15 is a longitudinal sectional view showing the configuration of the position restriction portion 315 of the flat tube 310 of the heat exchanger 101f according to Embodiment 6. Based on the above description, the position restriction portion 315 is formed in the tube wall 311 of each flat tube 310, and a return flow path P1at is formed in the upper portion of the inner space of the tube wall 311, through which the refrigerant flows in the front-rear direction.​Figure 15 The heat exchanger 101f according to Embodiment 6 will be described. The heat exchanger 101f is configured by changing the shape of the flat tube 10 of the heat exchanger 101 according to Embodiment 1. The heat exchanger 101f according to Embodiment 6 is different from the case of Embodiment 1 in that it has position restriction portions 315 that restrict the distance between the tube walls 311 of adjacent flat tubes 310. In addition, regarding the constituent elements having the same functions and effects as those of Embodiment 1, the same reference numerals are given and the description thereof is omitted.

[0107] The adjacent flat tubes 310 have the position restriction portions 315 for setting the distance between the tube walls 311 constant. As in the case of Embodiment 1, each flat tube 310 has the tube wall 311 and the link protrusion portions 319a, 319b that constitute the link portion 319 and extend outward from the tube wall 311 in the first direction Dl. In addition, in Embodiment 6, each flat tube 310 has, as an element that constitutes the position restriction portion 315, the position restriction protrusion portions 315a, 315b that extend outward from the tube wall 311 in the first direction Dl.

[0108] Specifically, among the substantially flat plate-shaped tube side wall portions 310a and 310b of the tube wall 311 that face in the first direction Dl, the position restriction protrusion portion 315a is provided to the tube side wall portion 310a and the position restriction protrusion portion 315b is provided to the tube side wall portion 310b. Further, the distance between the tube walls 311 is restricted by the position restriction protrusion portions 315a, 315b provided to the adjacent flat tubes 310 respectively contacting each other. That is, the position restriction portion 315 is a spacer provided to the tube wall 311 of the flat tube 310.

[0109] When the heat exchanger 101f is viewed from the front, each position restriction protrusion portion 315a, 315b has, for example, a frame shape of a quadrangle. In addition, the shape of each position restriction protrusion portion 315a, 315b is not limited to the above-described shape, and may, for example, be a frame shape of a trapezoid or a triangle. By providing the position restriction protrusion portions 315a, 315b, the heat transfer area of the heat exchanger 101f is expanded and the heat exchange performance is improved. Here, each position restriction protrusion portion 315a, 315b is provided in a frame shape in order to reduce the ventilation resistance.

[0110] In Figure 15In the example shown, the position restricting portion 315 comprises position restricting protrusions 315a and 315b provided on adjacent flat tubes 310, but this configuration is not particularly limiting. Alternatively, the position restricting portion 315 may comprise a single position restricting protrusion provided on one of the opposing tube sidewalls 310a and 310b of adjacent flat tubes 310 (the tube sidewall 310a or 310b). In this case, the position restricting protrusion provided on the flat tube 310 contacts the tube wall 311 of the adjacent flat tube 310.

[0111] like Figure 15 As shown, the position-limiting protrusions 315a and 315b can be integrally formed with the flat tube 310. Specifically, they can be formed from a portion of a member constituting the flat tube 310. For example, if the flat tube 310 is made of a plate-like member, the flat tube 310 can be formed from a member including a surplus portion in addition to the portion forming the tube wall 311, while forming the through-holes h1a and the like. The position-limiting protrusions 315a and 315b can be formed by, for example, slitting and bending a portion of the surplus portion.

[0112] In addition, the position restriction protrusions 315 a and 315 b may be formed of a member different from the flat tube 310 .

[0113] As described above, in the heat exchanger 101f of Embodiment 6, position regulating protrusions 315a, 315b are provided on at least one of the facing tube side walls 310a, 310b of adjacent flat tubes 310 to regulate the distance between the tube walls 311. This increases the heat transfer area while regulating the distance between the tube walls 311 of adjacent flat tubes 310.

[0114] While the embodiments have been described above, the present disclosure is not limited to the aforementioned embodiments. For example, various embodiments may be combined to form a structure. While the heat transfer fins 50 are described in Embodiment 3 as being applied to the heat exchanger 101b of Embodiment 2, the heat transfer fins 50 of Embodiment 3 may also be applied to the heat exchangers 101 of Embodiments 1, 4, 5, or 6. Furthermore, when heat transfer fins 50 are provided in the heat exchanger 101f of Embodiment 6, the heat transfer fins 50 are positioned in the portion of the air flow path P2 excluding the portion where the connecting portion 319 and the position restricting portion 315 are provided.

[0115] Description of Reference Signs

[0116] 1e open end, 10 flat tube, 10a tube side wall portion, 10b tube side wall portion, 10c connecting wall portion, 10d connecting wall portion, 10e open end, 11 tube wall, 18 connecting portion, 19 connecting portion, 19a connecting protrusion portion, 19b connecting protrusion portion, 20 tube sealing portion, 30 first partition, 30e upper end, 40 second partition, 50 heat transfer fin, 100 air conditioning device, 100A outdoor unit, 100B indoor unit, 100c refrigerant circuit, 101 heat exchanger, 101b heat exchanger, 101c heat exchanger, 101d heat exchanger, 101e heat exchanger, 101f heat exchanger, 102 compressor, 103 four-way valve, 104 indoor heat exchanger, 105 expansion valve, 106 indoor fan, 107 outdoor fan, 110 flat tube, 110a tube side wall portion, 110b tube side wall portion, 111 tube wall, 117 connecting portion, 117a connecting protrusion portion, 117b connecting protrusion portion, 119 connecting portion, 119a connecting protrusion portion, 119b connecting protrusion portion, 120 tube sealing portion, 120h drain hole, 120p flat portion, 120r groove portion, 210 flat tube, 211 tube wall, 219 connecting portion, 310 flat tube, 310a tube side wall portion, 310b tube side wall portion, 311 tube wall, 315 position limiting portion, 315a position limiting protrusion portion, 315b position limiting protrusion portion, 319 connecting portion, 319a connecting protrusion portion, 319b connecting protrusion portion, Ax tube axis, B plane, C plane, D1 first direction, D2 second direction, D3 third direction, Dia inner diameter, Dob outer diameter, L tube pitch, Lp tube pitch, Lr pitch, P1a heat transfer flow path, P1at return flow path, P1b header flow path, P1b1 header flow path portion, P1b2 header flow path portion, P1c header flow path, P1d header flow path, P2 flow path, Pa1 heat transfer flow path, Sg hollow portion, a first pipe, b second pipe, h1a through hole, h1b through hole, h2a through hole.

Claims

1. A heat exchanger comprising a plurality of flat tubes arranged in a first direction and each extending in a second direction intersecting the first direction, wherein the flat tubes have tube walls provided with heat transfer flow paths for a fluid to flow in internal spaces, the tube walls have flat plate-like tube side wall portions facing in the first direction, through holes are formed in the tube side wall portions, adjacent flat tubes have connecting portions connecting the tube walls to each other and connecting the heat transfer flow paths in the internal spaces of the tube walls to each other, and the connecting portions are composed of connecting protrusion portions formed on at least one of the facing tube side wall portions of the adjacent flat tubes and protruding from peripheral portions of the through holes in the first direction.

2. The heat exchanger according to claim 1, wherein the heat exchanger comprises plate-like tube seal portions arranged at at least one end in the second direction of the plurality of flat tubes and covering one end of the heat transfer flow paths of the plurality of flat tubes, and the one end of the flat tubes is fixed to the tube seal portions at a constant pitch.

3. The heat exchanger according to claim 1 or 2, wherein the connecting portions are composed of the connecting protrusion portions formed on both of the facing tube side wall portions of the adjacent flat tubes.

4. The heat exchanger according to claim 3, wherein the connecting protrusion portions formed on both of the facing tube side wall portions of the adjacent flat tubes overlap at least a portion in the first direction.

5. The heat exchanger according to any one of claims 1 to 4, wherein the flat tubes have first partition members arranged in the internal spaces of the tube walls and extending in the second direction, the internal spaces being divided in a third direction orthogonal to the first direction and the second direction, and at least one end of the second direction of the first partition members is located inward from end portions on both sides of the second direction of the flat tubes.

6. The heat exchanger according to any one of claims 1 to 5, wherein the heat exchanger comprises second partition members provided between the tube walls of at least one group of adjacent flat tubes among the plurality of flat tubes and cutting off the flow of the fluid between the heat transfer flow paths via the connecting portions.

7. The heat exchanger according to any one of claims 1 to 6, wherein at least one of the facing tube side wall portions of the adjacent flat tubes is provided with a position limiting protrusion portion limiting the distance between the tube walls.

8. An air conditioning device, wherein the air conditioning device comprises a refrigerant circuit connecting a compressor, the heat exchanger according to any one of claims 1 to 7, an expansion valve, and an indoor heat exchanger via refrigerant pipes for circulating the fluid. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​

Images