Heat exchanger and refrigeration cycle device

Abstract

The present invention relates to a heat exchanger and a refrigeration cycle device. The heat exchanger according to an embodiment has a plurality of heat exchange tubes and headers. The headers are provided at the ends of the heat exchange tubes. The plurality of heat exchange tubes include a first and a second upstream-side heat exchange tubes arranged side by side in a first direction and a first and a second downstream-side heat exchange tubes arranged side by side in the first direction. At least one of the headers includes an inner plate body to which the heat exchange tubes are connected, an outer plate body disposed opposite to the inner plate body, and an intermediate plate body provided between the inner plate body and the outer plate body. A first conversion flow path and a second conversion flow path are formed in the intermediate plate body. The first conversion flow path connects the refrigerant flow path of the first downstream-side heat exchange tube to the refrigerant flow path of the second upstream-side heat exchange tube. The second conversion flow path connects the refrigerant flow path of the second downstream-side heat exchange tube to the refrigerant flow path of the first upstream-side heat exchange tube.

Description

Technical Field

[0001] Embodiments of the present invention relate to a heat exchanger and a refrigeration cycle device. Background Art

[0002] A header type heat exchanger has a plurality of heat exchange tubes and headers. A refrigerant flow path is formed inside the heat exchange tubes. The headers are provided at the ends of the heat exchange tubes. It is desired to improve the heat exchange efficiency of the heat exchanger.

[0003] Prior Art Documents

[0004] Patent Documents

[0005] Patent Document 1: International Publication No. 2015 / 037641 Summary of the Invention

[0006] Problems to be Solved by the Invention

[0007] The problem to be solved by the present invention is to provide a heat exchanger and a refrigeration cycle device capable of improving heat exchange efficiency.

[0008] Means for Solving the Problems

[0009] The heat exchanger according to the embodiment has a plurality of heat exchange tubes and headers. The plurality of heat exchange tubes form a refrigerant flow path for the refrigerant to flow. The headers are provided at the ends of the heat exchange tubes. The plurality of heat exchange tubes include a first upstream heat exchange tube and a second upstream heat exchange tube arranged in parallel in a first direction, and a first downstream heat exchange tube and a second downstream heat exchange tube arranged in parallel in the first direction. At least one of the headers includes an inner plate body to which the heat exchange tubes are connected, an outer plate body disposed opposite to the inner plate body, and an intermediate plate body provided between the inner plate body and the outer plate body. A first conversion flow path and a second conversion flow path are formed in the intermediate plate body. The first conversion flow path connects the refrigerant flow path of the second downstream heat exchange tube to the refrigerant flow path of the first upstream heat exchange tube. The second conversion flow path connects the refrigerant flow path of the first downstream heat exchange tube to the refrigerant flow path of the second upstream heat exchange tube. Brief Description of the Drawings

[0010] Figure 1 is a schematic configuration diagram of the refrigeration cycle device according to the embodiment.

[0011] Figure 2 is a perspective three-dimensional view of the heat exchanger according to the embodiment.

[0012] Figure 3 is an exploded three-dimensional view of the heat exchanger according to the embodiment.

[0013] Figure 4It is a cross-sectional view of the first header pipe.

[0014] Figure 5 It is an exploded perspective view of the second header pipe.

[0015] Figure 6 It is a cross-sectional view of the second header pipe.

[0016] Figure 7 It is a cross-sectional view of the first header pipe of the first modification example.

[0017] Figure 8 It is a cross-sectional view of the first header pipe of the second modification example.

[0018] Figure 9 It is an exploded perspective view of the first header pipe of the third modification example.

[0019] Figure 10 It is a cross-sectional view of the first header pipe of the third modification example. Detailed implementation manners

[0020] Hereinafter, the heat exchanger of the implementation manner will be described with reference to the accompanying drawings.

[0021] In the present application, the X direction, the Y direction, and the Z direction are defined as follows. The Z direction is the long side direction (extension direction) of the first header pipe and the second header pipe. For example, the Z direction is the vertical direction, and the +Z direction is upward. The X direction is the central axis direction (extension direction) of the heat exchange pipe. For example, the X direction is the horizontal direction, and the +X direction is the direction from the second header pipe toward the first header pipe. The Y direction (the first direction) is the direction perpendicular to the X direction and the Z direction. The Y direction is preferably the horizontal direction.

[0022] Figure 1 It is a schematic configuration diagram of the refrigeration cycle device of the implementation manner.

[0023] As Figure 1 shown, the refrigeration cycle device 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger (heat exchanger) 4, an expansion device 5, and an indoor heat exchanger (heat exchanger) 6. The components of the refrigeration cycle device 1 are sequentially connected by a pipe 7. In Figure 1 it, the flow direction of the refrigerant (heat medium) during refrigeration operation is indicated by a solid line arrow, and the flow direction of the refrigerant during heating operation is indicated by a dotted line arrow.

[0024] The compressor 2 includes a compressor main body 2A and a liquid receiver 2B. The compressor main body 2A compresses the low-pressure gas refrigerant taken into the interior to make it a high-temperature and high-pressure gas refrigerant. The liquid receiver 2B separates the gas-liquid two-phase refrigerant and supplies the gas refrigerant to the compressor main body 2A.

[0025] The four-way valve 3 reverses the flow direction of the refrigerant to switch between refrigeration operation and heating operation. During refrigeration operation, the refrigerant flows in the order of the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion device 5, and the indoor heat exchanger 6. At this time, the refrigeration cycle device 1 causes the outdoor heat exchanger 4 to function as a condenser and the indoor heat exchanger 6 to function as an evaporator to cool the interior. During heating operation, the refrigerant flows in the order of the compressor 2, the four-way valve 3, the indoor heat exchanger 6, the expansion device 5, and the outdoor heat exchanger 4. At this time, the refrigeration cycle device 1 causes the indoor heat exchanger 6 to function as a condenser and the outdoor heat exchanger 4 to function as an evaporator to heat the interior.

[0026] The condenser dissipates heat from the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 2 to the external gas and condenses it, thereby making it a high-pressure liquid refrigerant.

[0027] The expansion device 5 reduces the pressure of the high-pressure liquid refrigerant fed from the condenser to make it a low-temperature and low-pressure gas-liquid two-phase refrigerant.

[0028] The evaporator absorbs heat from the external gas and vaporizes the low-temperature and low-pressure gas-liquid two-phase refrigerant fed from the expansion device 5, thereby making it a low-pressure gaseous refrigerant.

[0029] In this way, in the refrigeration cycle device 1, the refrigerant as the working fluid circulates while undergoing a phase change between the gaseous refrigerant and the liquid refrigerant. The refrigerant dissipates heat during the process of changing from the gaseous refrigerant to the liquid refrigerant and absorbs heat during the process of changing from the liquid refrigerant to the gaseous refrigerant. The refrigeration cycle device 1 uses the heat dissipation or heat absorption of the refrigerant to perform heating, refrigeration, defrosting, etc.

[0030] Figure 2 is a perspective view of the heat exchanger of the embodiment. As Figure 2 shown, the heat exchanger 4 of the embodiment is used in one or both of the outdoor heat exchanger 4 and the indoor heat exchanger 6 of the refrigeration cycle device 1. Hereinafter, the case where the heat exchanger 4 is used as the outdoor heat exchanger 4 of the refrigeration cycle device 1 (refer to Figure 1 ) will be described as an example.

[0031] The heat exchanger 4 has a first header 10, a second header 20, and heat exchange tubes (heat transfer tubes) 30.

[0032] Figure 3 is an exploded perspective view of the heat exchanger 4. Figure 4 is a cross-sectional view of the first header 10 along the XZ plane.

[0033] As Figure 3As shown, the first header 10 is formed by successively stacking the first inner plate body 11, the first intermediate plate body 13, the second intermediate plate body 14, the third intermediate plate body 15, and the first outer plate body 12.

[0034] The first inner plate body 11, the first to third intermediate plate bodies 13 - 15, and the first outer plate body 12 are formed of materials with relatively high thermal conductivity and relatively small specific gravity, such as aluminum and aluminum alloys. The first inner plate body 11, the first to third intermediate plate bodies 13 - 15, and the first outer plate body 12 are substantially parallel to the YZ plane. The first outer plate body 12 is disposed opposite to the surface (+X direction side surface of the first inner plate body 11, the first main surface 11a). The first to third intermediate plate bodies 13 - 15 are disposed between the first inner plate body 11 and the first outer plate body 12.

[0035] The first main surface 11a of the first inner plate body 11 is the main surface of the first inner plate body 11 and is the surface opposite to the first outer plate body 12. The second main surface 11b is the surface opposite to the first main surface 11a.

[0036] A plurality of insertion portions 41 are formed on the first inner plate body 11. The insertion portions 41 penetrate the first inner plate body 11 in the thickness direction. The insertion portions 41 are formed in a slit shape parallel to the Y direction. The end portions of the heat exchange tubes 30 are inserted into the insertion portions 41. Thus, the heat exchange tubes 30 are connected to the first inner plate body 11.

[0037] A plurality of hole-shaped flow paths 16 are formed on the first intermediate plate body 13. The hole-shaped flow paths 16 penetrate the first intermediate plate body 13 in the thickness direction. The plurality of hole-shaped flow paths 16 include a first hole-shaped flow path 16A to a sixth hole-shaped flow path 16F.

[0038] The first hole-shaped flow path 16A has an oval shape when viewed from the X direction. The "oval shape" is a shape formed by two parallel and opposite straight lines and curved convex shapes (such as semi-circular shapes, elliptical arc shapes, etc.) that connect the ends of the two straight lines to each other. The first hole-shaped flow path 16A is an elongated hole extending in the Y direction. The first hole-shaped flow path 16A is in the highest position among the first hole-shaped flow path 16A to the sixth hole-shaped flow path 16F (i.e., located on the side closest to the +Z direction).

[0039] The second hole-shaped flow path 16B (the second conversion flow path) has an upper region 16B1, a connection region 16B2, and a lower region 16B3. The upper region 16B1 is in a position lower than the first hole-shaped flow path 16A (i.e., located on the -Z direction side of the first hole-shaped flow path 16A). The upper region 16B1 is an elongated hole extending in the Y direction.

[0040] The lower region 16B3 is located at a position lower than the third hole-shaped flow path 16C (i.e., on the -Z direction side of the third hole-shaped flow path 16C). The lower region 16B3 is an elongated hole extending along the Y direction. The lower region 16B3 is located at a position in the +Y direction relative to the upper region 16B1. The lower region 16B3 is positioned in a line with the fourth hole-shaped flow path 16D in the Y direction. The lower region 16B3 is on the +Y direction side with respect to the fourth hole-shaped flow path 16D. The lower region 16B3 is located at a position lower than the upper region 16B1.

[0041] The connecting region 16B2 connects the +Y direction end of the upper region 16B1 and the -Y direction end of the lower region 16B3. The connecting region 16B2 is an elongated hole that extends obliquely in a manner of descending toward the +Y direction.

[0042] The third hole-shaped flow path 16C has an oval shape when viewed from the X direction. The third hole-shaped flow path 16C is an elongated hole extending along the Y direction. The third hole-shaped flow path 16C is located at a position lower than the first hole-shaped flow path 16A (i.e., on the -Z direction side of the first hole-shaped flow path 16A). The third hole-shaped flow path 16C is positioned in a line with the upper region 16B1 in the Y direction. The third hole-shaped flow path 16C is on the +Y direction side with respect to the upper region 16B1.

[0043] The fourth hole-shaped flow path 16D is located at a position lower than the upper region 16B1 (i.e., on the -Z direction side of the upper region 16B1). The fourth hole-shaped flow path 16D has an oval shape when viewed from the X direction. The fourth hole-shaped flow path 16D is an elongated hole extending along the Y direction.

[0044] The fifth hole-shaped flow path 16E is located at a position lower than the fourth hole-shaped flow path 16D (i.e., on the -Z direction side of the fourth hole-shaped flow path 16D). The fifth hole-shaped flow path 16E has an oval shape when viewed from the X direction. The fifth hole-shaped flow path 16E is an elongated hole extending along the Y direction.

[0045] The sixth hole-shaped flow path 16F is located at a position lower than the lower region 16B3 (i.e., on the -Z direction side of the lower region 16B3). The sixth hole-shaped flow path 16F is positioned in a line with the fifth hole-shaped flow path 16E in the Y direction. The sixth hole-shaped flow path 16F is on the +Y direction side with respect to the fifth hole-shaped flow path 16E. The fifth hole-shaped flow path 16E and the sixth hole-shaped flow path 16F are formed at intervals in the Y direction.

[0046] A plurality of hole-shaped flow paths 17 are formed on the second intermediate plate body 14. The hole-shaped flow paths 17 penetrate the second intermediate plate body 14 along the thickness direction. The plurality of hole-shaped flow paths 17 include the first hole-shaped flow path 17A to the fifth hole-shaped flow path 17E.

[0047] The first hole-shaped flow path 17A has the same shape as the first hole-shaped flow path 16A. When viewed from the X direction, the first hole-shaped flow path 17A is in a position that coincides with the first hole-shaped flow path 16A. The second hole-shaped flow path 17B has the same shape as the third hole-shaped flow path 16C. When viewed from the X direction, the second hole-shaped flow path 17B is in a position that coincides with the third hole-shaped flow path 16C. The third hole-shaped flow path 17C has the same shape as the fourth hole-shaped flow path 16D. When viewed from the X direction, the third hole-shaped flow path 17C is in a position that coincides with the fourth hole-shaped flow path 16D. The fourth hole-shaped flow path 17D has the same shape as the fifth hole-shaped flow path 16E. When viewed from the X direction, the fourth hole-shaped flow path 17D is in a position that coincides with the fifth hole-shaped flow path 16E. The fifth hole-shaped flow path 17E has the same shape as the sixth hole-shaped flow path 16F. When viewed from the X direction, the fifth hole-shaped flow path 17E is in a position that coincides with the sixth hole-shaped flow path 16F. The fourth hole-shaped flow path 17D and the fifth recess 17E are formed at intervals in the Y direction.

[0048] A plurality of hole-shaped flow paths 18 are formed in the third intermediate plate body 15. The hole-shaped flow paths 18 penetrate the third intermediate plate body 15 in the thickness direction. The hole-shaped flow paths 16 to 18 can be formed by punching a flat plate-shaped body.

[0049] The plurality of hole-shaped flow paths 18 include a first hole-shaped flow path 18A to a third hole-shaped flow path 18C.

[0050] The first hole-shaped flow path 18A has the same shape as the first hole-shaped flow path 17A. When viewed from the X direction, the first hole-shaped flow path 18A is in a position that coincides with the first hole-shaped flow path 17A. The second hole-shaped flow path 18B (the first conversion flow path) has a lower region 18B1, a connection region 18B2, and an upper region 18B3. The lower region 18B1 is in a position lower than the first hole-shaped flow path 18A (i.e., on the -Z direction side of the first hole-shaped flow path 18A). The lower region 18B1 is a long hole extending in the Y direction.

[0051] The upper region 18B3 is in a position higher than the lower region 18B1. The upper region 18B3 is in a position lower than the first hole-shaped flow path 18A (i.e., on the -Z direction side of the first hole-shaped flow path 18A). The upper region 18B3 is a long hole extending in the Y direction. The upper region 18B3 is located in a position closer to the +Y direction than the lower region 18B1.

[0052] The connection region 18B2 connects the +Y direction end of the lower region 18B1 and the -Y direction end of the upper region 18B3. The connection region 18B2 is a long hole that extends obliquely in a manner rising toward the +Y direction.

[0053] The third hole-shaped flow path 18C is oval when viewed in the X direction. The third hole-shaped flow path 18C is a long hole extending in the Y direction. The third hole-shaped flow path 18C is in the lowest position among the first to third hole-shaped flow paths 18A to 18C (i.e., located on the side closest to the -Z direction). When viewed in the X direction, the third hole-shaped flow path 18C has a length that includes the fourth hole-shaped flow path 17D and the fifth recess 17E. When viewed in the X direction, the -Y direction end of the third hole-shaped flow path 18C coincides with the -Y direction end of the fourth hole-shaped flow path 17D. When viewed in the X direction, the +Y direction end of the third hole-shaped flow path 18C coincides with the +Y direction end of the fifth recess 17E.

[0054] The first main surface 12a of the first outer plate body 12 is the main surface of the first outer plate body 12 and is the surface facing the first inner plate body 11. The second main surface 12b is the surface opposite to the first main surface 12a.

[0055] As Figure 4 shown, the hole-shaped flow paths 16 to 18 of the first inner plate body 11, the intermediate plate bodies 13 to 15, and the first outer plate body 12 form a header flow path portion 19 (space).

[0056] Insertion portions 42 and 43 are formed on the first outer plate body 12. For example, the insertion portions 42 and 43 are circular.

[0057] A tubular first refrigerant port 51 is inserted into the insertion portion 42. The end of the first refrigerant port 51 opens inside the third hole-shaped flow path 18C. This opening serves as an inlet for introducing refrigerant into the heat exchanger 4 or an outlet for discharging refrigerant from the heat exchanger 4.

[0058] A tubular second refrigerant port 52 is inserted into the insertion portion 43. The end of the second refrigerant port 52 opens inside the first hole-shaped flow path 18A. This opening serves as an inlet for introducing refrigerant into the heat exchanger 4 or an outlet for discharging refrigerant from the heat exchanger 4.

[0059] Figure 5 is an exploded perspective view of the second header 20. Figure 6 is a cross-sectional view of the second header 20 along the XZ plane.

[0060] As Figure 5 and Figure 6As shown, the second header 20 is formed by successively laminating a second inner plate body 21, a second intermediate plate body 23, and a second outer plate body 22. The second inner plate body 21, the second intermediate plate body 23, and the second outer plate body 22 are formed of a material having a relatively high thermal conductivity and a relatively small specific gravity, such as aluminum or an aluminum alloy. The second inner plate body 21, the second intermediate plate body 23, and the second outer plate body 22 are substantially parallel to the YZ plane. The second outer plate body 22 is disposed opposite to the surface (-X direction side surface) of the second inner plate body 21 (the first main surface 21a). The second intermediate plate body 23 is disposed between the second inner plate body 21 and the second outer plate body 22.

[0061] The first main surface 21a is the main surface of the second inner plate body 21 and is the surface opposite to the second outer plate body 22. The second main surface 21b is the surface opposite to the first main surface 21a.

[0062] A plurality of insertion portions 44 are formed in the second inner plate body 21. The insertion portions 44 penetrate the second inner plate body 21 in the thickness direction. The insertion portions 44 are formed in a slit shape parallel to the Y direction. The end portions of the heat exchange tubes 30 are inserted into the insertion portions 44.

[0063] A plurality of hole-shaped flow paths 24 are formed in the second intermediate plate body 23. The hole-shaped flow paths 24 penetrate the second intermediate plate body 23 in the thickness direction.

[0064] The plurality of hole-shaped flow paths 24 include a first hole-shaped flow path 24A to a fourth hole-shaped flow path 24D. The first hole-shaped flow path 24A to the fourth hole-shaped flow path 24D are rectangular when viewed from the X direction. The first hole-shaped flow path 24A and the second hole-shaped flow path 24B are arranged in the Y direction. The third hole-shaped flow path 24C is located on the -Z direction side of the first hole-shaped flow path 24A. The fourth hole-shaped flow path 24D is located on the -Z direction side of the second hole-shaped flow path 24B. The third hole-shaped flow path 24C and the fourth hole-shaped flow path 24D are arranged in the Y direction.

[0065] As Figure 6 shown, the second inner plate body 21, the hole-shaped flow paths 24 of the second intermediate plate body 23, and the second outer plate body 22 form a header flow path portion 26 (space).

[0066] As Figure 5 shown, the header flow path portion 26 divided by the first hole-shaped flow path 24A is referred to as a first header flow path portion 26A. The header flow path portion 26 divided by the second hole-shaped flow path 24B is referred to as a second header flow path portion 26B. The header flow path portion 26 divided by the third hole-shaped flow path 24C is referred to as a third header flow path portion 26C. The header flow path portion 26 divided by the fourth hole-shaped flow path 24D is referred to as a fourth header flow path portion 26D.

[0067] As Figure 2 shown, the first header 10 and the second header 20 are arranged separately from each other in the X direction.

[0068] The heat exchange tube 30 is formed of a material having a relatively high thermal conductivity and a relatively small specific gravity, such as aluminum or an aluminum alloy. The heat exchange tube 30 is formed in a flat tubular shape. That is, the dimension of the heat exchange tube 30 in the Y direction is larger than the dimension in the Z direction. The shape of the cross section (YZ cross section) of the heat exchange tube 30 orthogonal to the length direction is an oval shape. The heat exchange tube 30 extends along the X direction. A refrigerant flow path 34 (see Figure 4 ) is formed inside the heat exchange tube 30. The refrigerant flow path 34 is formed over the entire length of the heat exchange tube 30.

[0069] At least a part of a plurality of heat exchange tubes 30 are arranged at intervals in the Z direction. The +X direction end portion of the heat exchange tube 30 is inserted into an insertion portion 41 formed in the first header 10 (see Figure 4 ). Thereby, the +X direction end portion of the refrigerant flow path 34 of the heat exchange tube 30 opens inside the header flow path portion 19 of the first header 10. Therefore, the header flow path portion 19 communicates with the refrigerant flow path 34 of the heat exchange tube 30.

[0070] The -X direction end portion of the heat exchange tube 30 is inserted into an insertion portion 44 formed in the second header 20 (see Figure 6 ). Thereby, the -X direction end portion of the refrigerant flow path 34 of the heat exchange tube 30 opens inside the header flow path portion 26 of the second header 20. Therefore, the header flow path portion 26 communicates with the refrigerant flow path 34 of the heat exchange tube 30.

[0071] For example, a plurality of heat exchange tubes 30 constitute four heat exchange tube pairs 31. One heat exchange tube pair 31 is constituted by a pair of heat exchange tubes 30, 30 arranged in the +Y direction. The four heat exchange tube pairs 31 are arranged at intervals vertically.

[0072] The first heat exchange tube pair 31A from the top among the four heat exchange tube pairs 31 includes two heat exchange tubes 30A, 30B arranged in sequence in the +Y direction.

[0073] The second heat exchange tube pair 31B from the top includes a first downstream heat exchange tube 30C and a second downstream heat exchange tube 30D. The first downstream heat exchange tube 30C and the second downstream heat exchange tube 30D are arranged in sequence in the +Y direction. That is, the two heat exchange tubes 30 constituting the heat exchange tube pair 31B are arranged in the order of the first downstream heat exchange tube 30C and the second downstream heat exchange tube 30D toward the +Y direction.

[0074] The third heat exchange tube pair 31C from above includes a first upstream heat exchange tube 30E and a second upstream heat exchange tube 30F. The first upstream heat exchange tube 30E and the second upstream heat exchange tube 30F are arranged in sequence in the +Y direction. That is, the two heat exchange tubes 30 that make up the heat exchange tube pair 31C are arranged in the order of the first upstream heat exchange tube 30E and the second upstream heat exchange tube 30F in the +Y direction.

[0075] The fourth heat exchange tube pair 31D from above includes two heat exchange tubes 30G and 30H arranged in sequence in the +Y direction.

[0076] The heat exchange tubes 30A, 30C, 30E, and 30G are arranged on one side in the Y direction (-Y direction side. That is, Figure 2 the near front side in Figure 2 ). The heat exchange tubes 30B, 30D, 30F, and 30H are arranged on the other side in the Y direction (+Y direction side. That is,

[0077] the inside in Figure 3 ).

[0078] The first upstream heat exchange tube 30E is connected to the second downstream heat exchange tube 30D through the second hole-shaped flow path 18B (the first conversion flow path) (refer to Figure 3 ).

[0079] The gap between the first header 10 and the second header 20 and the heat exchange tube 30 is sealed by brazing or the like. The specific sequence of brazing is as follows. Solder is applied to the inner surfaces of the first header 10 and the second header 20. The heat exchange tube 30 is inserted into the first header 10 and the second header 20 to assemble the heat exchanger 4. The assembled heat exchanger 4 is heated in a furnace. By heating, the solder on the inner surfaces of the first header 10 and the second header 20 melts. The molten solder plugs the gap between the first header 10 and the second header 20 and the heat exchange tube 30. The heat exchanger 4 is cooled and the solder solidifies. Thus, the first header 10, the second header 20, and the heat exchange tube 30 are fixed.

[0080] An external gas flow path along the Y direction is formed between the vertically adjacent heat exchange tubes 30. The heat exchanger 4 circulates external gas in the external gas flow path through a blower fan (not shown) or the like. The heat exchanger 4 exchanges heat between the external gas flowing in the external gas flow path and the refrigerant flowing in the refrigerant flow path 34. The heat exchange is carried out indirectly through the heat exchange tube 30.

[0081] In Figure 1When the refrigeration cycle device 1 shown operates in a refrigeration mode, the outdoor heat exchanger 4 functions as a condenser. In this case, the gaseous refrigerant flowing out from the compressor 2 flows into the outdoor heat exchanger 4.

[0082] As Figure 2 shown, the refrigerant flows into the interior of the first header 10 from the first refrigerant port 51. The refrigerant flowing into the header flow path portion 19 of the third hole-shaped flow path 18C from the first refrigerant port 51 (refer to Figure 3 ) is distributed to the hole-shaped flow paths 17D, 16E and the hole-shaped flow paths 17E, 16F and flows. The refrigerant flowing in the hole-shaped flow paths 17D, 16E is referred to as "first refrigerant". The refrigerant flowing in the hole-shaped flow paths 17E, 16F is referred to as "second refrigerant".

[0083] The first refrigerant flows in the heat exchange tubes 30 (30G) in the -X direction from the hole-shaped flow paths 17D, 16E (refer to Figure 3 ) and flows into the lower part of the third header flow path portion 26C of the second header 20. The first refrigerant flows in the heat exchange tubes 30 (30E) in the +X direction from the upper part of the third header flow path portion 26C and flows into the second hole-shaped flow path 18B (first conversion flow path) via the hole-shaped flow paths 16D, 17C of the first header 10 (refer to Figure 3 ). The first refrigerant reaches the hole-shaped flow paths 17B, 16C from the lower region 18B1 of the second hole-shaped flow path 18B through the connection region 18B2 and the upper region 18B3. The first refrigerant flows in the heat exchange tubes 30 (30D) in the -X direction from the hole-shaped flow paths 17B, 16C and flows into the lower part of the second header flow path portion 26B of the second header 20. The first refrigerant flows in the heat exchange tubes 30 (30B) in the +X direction from the upper part of the second header flow path portion 26B and flows out through the second refrigerant port 52 via the hole-shaped flow paths 16A, 17A, 18A of the first header 10.

[0084] The number of heat exchange tubes 30G, 30E, 30D, 30B through which the first refrigerant passes and arranged on one side in the Y direction (-Y direction side. Figure 2 the near front side in) is 2. The number of heat exchange tubes 30B, 30D arranged on the other side in the Y direction (+Y direction side. That is, Figure 2 the inside in) is 2. Therefore, the number of heat exchange tubes 30 on one side in the Y direction is the same as that on the other side. Therefore, the deviation of the heat exchange efficiency in the Y direction can be suppressed.

[0085] The second refrigerant flows from the hole-shaped flow paths 17E, 16F (refer to Figure 3) flows in the heat exchange tubes 30 (30H) in the -X direction and flows into the lower part of the fourth header flow path portion 26D of the second header 20. The second refrigerant flows in the heat exchange tubes 30 (30F) in the +X direction from the upper part of the fourth header flow path portion 26D and flows into the second hole-shaped flow path 16B (the second conversion flow path) of the first header 10 (see Figure 3 ). The second refrigerant reaches the upper region 16B1 from the lower region 16B3 of the second hole-shaped flow path 16B through the connection region 16B2. The second refrigerant flows in the heat exchange tubes 30 (30C) in the -X direction from the upper region 16B1 and flows into the lower part of the first header flow path portion 26A of the second header 20. The second refrigerant flows in the heat exchange tubes 30 (30A) in the +X direction from the upper part of the first header flow path portion 26A and flows out through the second refrigerant port 52 via the hole-shaped flow paths 16A, 17A, 18A of the first header 10.

[0086] The number of the heat exchange tubes 30C, 30A arranged on one side in the Y direction (-Y direction side. Figure 2 in the near front side) among the heat exchange tubes 30H, 30F, 30C, 30A through which the second refrigerant passes is two. The number of the heat exchange tubes 30H, 30F arranged on the other side in the Y direction (+Y direction side. That is, Figure 2 in the inner side) is two. Therefore, the number of the heat exchange tubes 30 on one side in the Y direction is the same as that on the other side. Therefore, the deviation of the heat exchange efficiency in the Y direction can be suppressed.

[0087] The gaseous refrigerant dissipates heat to the external gas and condenses during the process of flowing through the heat exchange tubes 30. The condensed refrigerant becomes a liquid refrigerant and flows out of the heat exchanger 4 through the second refrigerant port 52.

[0088] In Figure 1 when the refrigeration cycle device 1 shown performs a heating operation, the refrigerant flows in the opposite direction to the above. That is, the liquid refrigerant flows into the first header 10 from the second refrigerant port 52, and the gas-liquid two-phase refrigerant flows out from the first refrigerant port 51.

[0089] In the heat exchanger 4 of the embodiment, the second hole-shaped flow path 18B (the first conversion flow path) and the second hole-shaped flow path 16B (the second conversion flow path) are formed on the intermediate plate bodies 13 to 15. Therefore, the first refrigerant flows from the upstream heat exchange tube 30E on the -Y direction side to the downstream heat exchange tube 30D on the +Y direction side. The second refrigerant flows from the upstream heat exchange tube 30F on the +Y direction side to the downstream heat exchange tube 30C on the -Y direction side. Thereby, the uneven flow of the refrigerant in the Y direction can be suppressed, and the reduction of the heat exchange efficiency can be suppressed.

[0090] In the heat exchanger 4 of the embodiment, a refrigerant port 51 having an inlet for the refrigerant and a refrigerant port 52 having an outlet for the refrigerant are provided in the first header 10 (see Figure 2 ). In the heat exchanger 4, since both the refrigerant ports 51 and 52 are provided in the first header 10, miniaturization can be achieved as compared with the case where the refrigerant ports are dispersedly provided in two headers. Therefore, the heat exchanger 4 is excellent in terms of the storage property in the housing.

[0091] In the heat exchanger 4 of the embodiment, the first header 10 and the second header 20 are composed of plate materials 11 to 14, so that the structure of the header can be simplified. Therefore, miniaturization and weight reduction can be achieved. Therefore, the heat exchanger 4 is excellent in terms of the storage property in the housing.

[0092] As a comparative example, a heat exchanger without headers is assumed. This heat exchanger uses a serpentine heat exchange tube in which straight portions and bent portions are alternately formed. In the case of using a flat heat exchange tube, in the bent portion, it is necessary to increase the curvature radius in order to prevent buckling, and it is difficult to miniaturize the heat exchanger. If a circular tubular heat exchange tube is used only in the bent portion, the curvature radius can be reduced. However, in this case, a mechanism for connecting the flat heat exchange tube and the circular tubular heat exchange tube is required, so that miniaturization is difficult.

[0093] Figure 7 It is a sectional view along the XZ plane of the first header 10A of the first modification. The same reference numerals are given to the components that have been described, and the description thereof is omitted.

[0094] The first header 10A uses the first inner plate body 111 instead of the first inner plate body 11 (see Figure 5 ). In the first header 10A, the first outer plate body 112 is used instead of the first outer plate body 12 (see Figure 5 ).

[0095] The first inner plate body 111 includes a plate body main portion 113 and a covering layer 114. For example, the plate body main portion 113 is made of an aluminum-containing material (aluminum, aluminum alloy, etc.). The covering layer 114 is provided on the outer surface 113b (the second main surface) of the plate body main portion 113. The outer surface 113b is the surface opposite to the first main surface, and the first main surface is the surface facing the first outer plate body 112. The covering layer 114 is made of a Zn-containing metal material. For example, the covering layer 115 is made of a 7000 series aluminum alloy. The Zn content (content rate) in the covering layer 114 is higher than the Zn content (content rate) in the plate body main portion 113.

[0096] The first outer plate body 112 includes a main plate body portion 115 and a covering layer 116. For example, the main plate body portion 115 is made of an aluminum-containing material (such as aluminum, aluminum alloy, etc.). The covering layer 116 is provided on the outer surface 115b (the second main surface) of the main plate body portion 115. The outer surface 115b is the surface opposite to the first main surface, and the first main surface is the surface facing the first inner plate body 111. The covering layer 116 is made of a Zn-containing metal material. For example, the covering layer 115 is made of an aluminum alloy of the 7000 series. The Zn content (content rate) in the covering layer 116 is higher than the Zn content (content rate) in the main plate body portion 115.

[0097] The first inner plate body 111 and the first outer plate body 112 can be made of clad steel (laminated sheet material) with a Zn-containing covering layer formed in advance. The covering layer can also be formed by spraying.

[0098] For the second header, a plate body with a covering layer can also be used in the same way as the first header 10A.

[0099] In this heat exchanger, since the plate bodies 111 and 112 have the covering layers 114 and 116, the corrosion resistance of the first header 10A can be improved.

[0100] Figure 8 It is a cross-sectional view of the first header 10B of the second modified example along the XZ plane. The same reference numerals are used for the components that have been described and the description thereof is omitted.

[0101] As Figure 8 shown, a low melting point layer 214 is provided on the main surfaces of the first inner plate body 11, the first to third intermediate plate bodies 13 to 15, and the first outer plate body 12 that face other plate materials.

[0102] For example, the plate bodies 11 to 15 are made of an aluminum-containing material (such as aluminum, aluminum alloy, etc.). The low melting point layer 214 is made of a Si-containing metal material. For example, the low melting point layer 214 is made of an aluminum alloy of the 4000 series. The Si content (content rate) in the low melting point layer 214 is higher than the Si content (content rate) in the plate bodies 11 to 15. The melting point of the constituent material of the low melting point layer 214 is lower than the melting point of the constituent material of the plate bodies 11 to 15.

[0103] The plate body having the low melting point layer 214 can be made of clad steel (laminated sheet material) with a Si-containing low melting point layer formed in advance. The low melting point layer can also be formed by laminating a clad sheet made of a low melting point material on the plate body.

[0104] For the second header, a plate body with a low melting point layer can also be used in the same way as the first header 10B.

[0105] In this heat exchanger, the low melting point layer 214 functions as solder for sealing the gaps between the first header 10, the second header 20, and the heat exchange tubes 30, thus facilitating the soldering operation.

[0106] Figure 9 It is an exploded perspective view of the first header 10C of the third modified example. Figure 10 It is a sectional view of the first header 10C of the third modified example along the XZ plane. The components that have been described are labeled with the same reference numerals and their description is omitted.

[0107] As Figure 9 and Figure 10 shown, the first header 10C has a convex portion 301 formed on the second intermediate plate body 14 and protruding into the hole-shaped flow path 18. The convex portion 301 may also be a wall shape with a reduced thickness in the protruding direction. Additionally, the shape of the convex portion is not particularly limited and may be prismatic, cuboid, hemispherical, etc.

[0108] According to the first header 10C, the refrigerant flowing into the hole-shaped flow path 18 through the first refrigerant port 51 is easily split into two parts by the convex portion 301.

[0109] In addition, in the illustrated example, the convex portion is exemplified as a configuration for promoting refrigerant splitting, but the concave portion formed on the second intermediate plate body 14 also has the effect of promoting refrigerant splitting.

[0110] According to at least one of the embodiments described above, since the first conversion flow path and the second conversion flow path are formed on the intermediate plate body of the header, the uneven flow of the refrigerant in the first direction can be suppressed, and the heat exchange efficiency can be improved.

[0111] Several embodiments of the present invention have been described, but these embodiments are presented as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in various other ways, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are included in the invention described in the claims and the scope equivalent thereto.

[0112] Description of reference numerals

[0113] 1: Refrigeration cycle device; 4: Outdoor heat exchanger (heat exchanger); 10: First header (header); 11, 111: First inner plate body (inner plate body); 11a: First main surface; 12, 112: First outer plate body (outer plate body); 12a: First main surface; 13: First intermediate plate body (intermediate plate body); 14: Second intermediate plate body (intermediate plate body); 15: Third intermediate plate body (intermediate plate body); 16B: Second hole-shaped flow path (second conversion flow path); 18B: Second hole-shaped flow path (first conversion flow path); 113b: Outer surface (second main surface); 115b: Outer surface (second main surface); 30: Heat exchange tube; 30C: First downstream heat exchange tube; 30D: Second downstream heat exchange tube; 30E: First upstream heat exchange tube; 30F: Second upstream heat exchange tube; 34: Refrigerant flow path; 113b: Outer surface (second main surface); 114, 116: Covering layer; 115b: Outer surface (second main surface); 301: Convex portion.

Claims

1. A heat exchanger, comprising: a plurality of heat exchange tubes, in which a refrigerant flow path for refrigerant to flow is formed; and headers, provided at ends of the above-mentioned heat exchange tubes, the direction in which the above-mentioned headers extend is the Z direction, the direction in which the above-mentioned plurality of heat exchange tubes extend is the X direction, the direction perpendicular to the above-mentioned Z direction and the above-mentioned X direction is the Y direction, the above-mentioned plurality of heat exchange tubes include a first upstream-side heat exchange tube and a second upstream-side heat exchange tube arranged in parallel in sequence in the above-mentioned Y direction, and a first downstream-side heat exchange tube and a second downstream-side heat exchange tube arranged in parallel in sequence in the above-mentioned Y direction, at least one of the above-mentioned headers includes an inner plate body for connecting the above-mentioned heat exchange tubes, an outer plate body arranged opposite to the above-mentioned inner plate body, and a plurality of intermediate plate bodies provided between the above-mentioned inner plate body and the above-mentioned outer plate body, a first conversion flow path for communicating the refrigerant flow path of the above-mentioned second downstream-side heat exchange tube with the refrigerant flow path of the above-mentioned first upstream-side heat exchange tube and a second conversion flow path for communicating the refrigerant flow path of the above-mentioned first downstream-side heat exchange tube with the refrigerant flow path of the above-mentioned second upstream-side heat exchange tube are formed on the above-mentioned plurality of intermediate plate bodies, the above-mentioned first conversion flow path and the above-mentioned second conversion flow path are formed on different intermediate plate bodies among the above-mentioned plurality of intermediate plate bodies, the above-mentioned first conversion flow path has a first lower region, a first connection region, and a first upper region, the above-mentioned first upper region is at a position higher than the above-mentioned first lower region in the above-mentioned Z direction, the above-mentioned first upper region is located at a position closer to the +Y direction than the above-mentioned first lower region, the above-mentioned first connection region connects the +Y direction end of the above-mentioned first lower region and the -Y direction end of the above-mentioned first upper region, and is an oblong hole extending obliquely, the above-mentioned second conversion flow path has a second upper region, a second connection region, and a second lower region, the above-mentioned second lower region is at a position lower than the above-mentioned second upper region in the above-mentioned Z direction, the above-mentioned second lower region is located at a position closer to the +Y direction than the above-mentioned second upper region, the above-mentioned second connection region connects the +Y direction end of the above-mentioned second upper region and the -Y direction end of the above-mentioned second lower region, and is an oblong hole extending obliquely, the above-mentioned refrigerant reaches the above-mentioned first upper region from the above-mentioned first lower region of the above-mentioned first conversion flow path through the above-mentioned first connection region, the above-mentioned refrigerant reaches the above-mentioned second upper region from the above-mentioned second lower region of the above-mentioned second conversion flow path through the above-mentioned second connection region.

2. The heat exchanger according to claim 1, wherein, among the plurality of heat exchange tubes having a refrigerant flow path communicating with the above-mentioned first conversion flow path, the number of heat exchange tubes arranged on one side in the above-mentioned Y direction is the same as the number of heat exchange tubes arranged on the other side in the above-mentioned Y direction, among the plurality of heat exchange tubes having a refrigerant flow path communicating with the above-mentioned second conversion flow path, the number of heat exchange tubes arranged on one side in the above-mentioned Y direction is the same as the number of heat exchange tubes arranged on the other side in the above-mentioned Y direction.

3. The heat exchanger according to claim 1 or 2, wherein, the above-mentioned outer plate body has a Zn-containing coating on a second main surface opposite to a first main surface, and the first main surface faces the above-mentioned inner plate body.

4. The heat exchanger according to claim 1 or 2, wherein, in one of the headers provided at the ends of one side and the other side of the heat exchange tubes, an inlet for introducing the refrigerant into the heat exchanger and an outlet for discharging the refrigerant from the heat exchanger are formed.

5. The heat exchanger according to claim 1 or 2, wherein, protrusions or recesses for promoting the diversion of the refrigerant introduced into the heat exchanger are formed on the plurality of intermediate plate bodies.

6. A refrigeration cycle device, wherein, it includes the heat exchanger according to any one of claims 1 to 5.

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