CN114341587A - Heat exchanger and refrigeration cycle device - Google Patents

Abstract

The present invention relates to a heat exchanger and a refrigeration cycle apparatus. The heat exchanger of the embodiment has a plurality of heat exchange tubes and a header. Headers are provided at the ends of the heat exchange tubes. The plurality of heat exchange tubes include 1 st and 2 nd upstream side heat exchange tubes arranged in parallel in the 1 st direction in this order and 1 st and 2 nd downstream side heat exchange tubes arranged in parallel in the 1 st direction in this order. At least one of the headers includes an inner plate body to which the heat exchange tubes are connected, an outer plate body disposed to face the inner plate body, and an intermediate plate body provided between the inner plate body and the outer plate body. The intermediate plate body is provided with a 1 st switching flow path and a 2 nd switching flow path. The 1 st switching flow path communicates the refrigerant flow path of the 1 st downstream side heat exchange tube with the refrigerant flow path of the 2 nd upstream side heat exchange tube. The 2 nd switching flow path communicates the refrigerant flow path of the 2 nd downstream side heat exchange tube with the refrigerant flow path of the 1 st upstream side heat exchange tube.

Description

Heat exchangers and refrigeration cycle devices

technical field

Embodiments of the present invention relate to a heat exchanger and a refrigeration cycle apparatus.

Background technique

The header-type heat exchanger includes a plurality of heat exchange tubes and headers. A refrigerant flow path is formed inside the heat exchange tube. 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.

prior art literature

Patent Literature

Patent Document 1: International Publication No. 2015/037641

SUMMARY OF THE INVENTION

The problem to be solved by the invention

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

means of solving problems

The heat exchanger of the embodiment has a plurality of heat exchange tubes and headers. The plurality of heat exchange tubes form a refrigerant flow path through which the refrigerant flows. 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 the first direction, and a first downstream heat exchange tube arranged in parallel in the first direction. and the second downstream heat exchange tube. At least one of the headers includes an inner plate body to which the heat exchange tubes are connected, an outer plate body arranged to face the inner plate body, and an intermediate plate body provided between the inner plate body and the outer plate body. A first switching flow path and a second switching flow path are formed on the intermediate plate body. The first switching flow path communicates the refrigerant flow path of the first downstream heat exchange tube and the refrigerant flow path of the second upstream heat exchange tube. The second switching flow path communicates the refrigerant flow path of the second downstream heat exchange tube and the refrigerant flow path of the first upstream heat exchange tube.

Description of drawings

FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus according to an embodiment.

2 is a perspective perspective view of the heat exchanger of the embodiment.

3 is an exploded perspective view of the heat exchanger according to the embodiment.

4 is a cross-sectional view of the first header.

Fig. 5 is an exploded perspective view of the second header.

6 is a cross-sectional view of a second header.

7 is a cross-sectional view of a first header of a first modification.

8 is a cross-sectional view of a first header of a second modification.

9 is an exploded perspective view of a first header of a third modification.

10 is a cross-sectional view of a first header of a third modification.

Detailed ways

Hereinafter, the heat exchanger according to the embodiment will be described with reference to the drawings.

In this application, the X direction, the Y direction, and the Z direction are defined as follows. The Z direction is the longitudinal direction (extending direction) of the first header and the second header. For example, the Z direction is the vertical direction, and the +Z direction is the upper direction. The X direction is the central axis direction (extending direction) of the heat exchange tube. For example, the X direction is the horizontal direction, and the +X direction is the direction from the second header to the first header. The Y direction (first direction) is a direction perpendicular to the X direction and the Z direction. The Y direction is preferably the horizontal direction.

FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus according to an embodiment.

As shown in FIG. 1 , the refrigeration cycle apparatus 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 constituent elements of the refrigeration cycle apparatus 1 are sequentially connected by pipes 7 . In FIG. 1 , the flow direction of the refrigerant (heat medium) during cooling operation is indicated by solid arrows, and the flow direction of the refrigerant during heating operation is indicated by broken line arrows.

The compressor 2 has a compressor body 2A and an accumulator 2B. The compressor main body 2A compresses the low-pressure gas refrigerant taken into the inside to become a high-temperature and high-pressure gas refrigerant. The accumulator 2B separates the gas-liquid two-phase refrigerant and supplies the gas refrigerant to the compressor main body 2A.

The four-way valve 3 reverses the flow direction of the refrigerant to switch the cooling operation and the heating operation. During the cooling 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 apparatus 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 room. During the 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 apparatus 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 room.

The condenser radiates heat and condenses the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 to the outside air, thereby making it a high-pressure liquid refrigerant.

The expansion device 5 reduces the pressure of the high-pressure liquid refrigerant sent from the condenser, and turns it into a low-temperature and low-pressure gas-liquid two-phase refrigerant.

The evaporator causes the low-temperature and low-pressure gas-liquid two-phase refrigerant fed from the expansion device 5 to absorb heat from the outside air and vaporize it, thereby turning it into a low-pressure gas refrigerant.

In this way, in the refrigeration cycle apparatus 1 , the refrigerant serving as the working fluid circulates while being phase-changed between the gas refrigerant and the liquid refrigerant. The refrigerant dissipates heat in the process of changing the phase from the gas refrigerant to the liquid refrigerant, and absorbs heat in the process of changing the phase from the liquid refrigerant to the gas refrigerant. The refrigeration cycle apparatus 1 performs heating, cooling, defrosting, and the like by utilizing heat radiation or heat absorption of the refrigerant.

2 is a perspective view of the heat exchanger according to the embodiment. As shown in FIG. 2 , the heat exchanger 4 of the embodiment is used for one or both of the outdoor heat exchanger 4 and the indoor heat exchanger 6 of the refrigeration cycle apparatus 1 . Hereinafter, the case where the heat exchanger 4 is used as the outdoor heat exchanger 4 of the refrigeration cycle apparatus 1 (see FIG. 1 ) will be described as an example.

The heat exchanger 4 includes a first header 10 , a second header 20 , and heat exchange tubes (heat transfer tubes) 30 .

FIG. 3 is an exploded perspective view of the heat exchanger 4 . FIG. 4 is a cross-sectional view of the first header 10 taken along the XZ plane.

As shown in FIG. 3 , by 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 in this order, the first cluster is formed. Tube 10.

The first inner plate body 11 , the first to third intermediate plate bodies 13 to 15 , and the first outer plate body 12 are formed of materials with high thermal conductivity and small specific gravity, such as aluminum and aluminum alloys. The first inner plate body 11 , the first to third intermediate plate bodies 13 to 15 , and the first outer plate body 12 are substantially parallel to the YZ plane. The first outer plate body 12 and the surface (first main surface 11a) on the +X direction side of the first inner plate body 11 are arranged to face each other. The first to third intermediate plate bodies 13 to 15 are provided between the first inner plate body 11 and the first outer plate body 12 .

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

A plurality of insertion portions 41 are formed in the first inner panel body 11 . The insertion portion 41 penetrates the first inner panel body 11 in the thickness direction. The insertion portion 41 is formed in a slit shape parallel to the Y direction. The end portion of the heat exchange tube 30 is inserted into the insertion portion 41 . Thereby, the heat exchange tube 30 is connected to the first inner plate body 11 .

A plurality of hole-shaped flow paths 16 are formed in the first intermediate plate body 13 . The hole-shaped flow path 16 penetrates the first intermediate plate body 13 in the thickness direction. The plurality of hole-shaped flow channels 16 include first hole-shaped flow channels 16A to sixth hole-shaped flow channels 16F.

The first hole-shaped flow path 16A has an oval shape when viewed in the X direction. The "oval shape" is a shape composed of two straight lines parallel to each other and facing each other and a curved convex shape (eg, semicircular shape, elliptical arc shape, etc.) connecting 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 channel 16A is located at the highest position (that is, the position on the most +Z direction side) among the first hole-shaped flow channel 16A to the sixth hole-shaped flow channel 16F.

The second hole-shaped flow path 16B (second switching flow path) has an upper region 16B1, a connection region 16B2, and a lower region 16B3. The upper region 16B1 is located at a position lower than the first hole-shaped flow path 16A (that is, 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.

The lower region 16B3 is located at a position lower than the third hole-shaped flow path 16C (that is, on the -Z direction side of the third hole-shaped flow path 16C). The lower region 16B3 is a long hole extending in the Y direction. The lower region 16B3 is located in the +Y direction relative to the upper region 16B1. The lower region 16B3 is in a position aligned with the fourth hole-shaped flow path 16D in the Y direction. The lower region 16B3 is located on the +Y direction side with respect to the fourth hole-shaped flow path 16D. The lower area 16B3 is located at a lower position than the upper area 16B1.

The connection region 16B2 connects the end of the upper region 16B1 in the +Y direction and the end of the lower region 16B3 in the −Y direction. The connection region 16B2 is a long hole extending obliquely so as to descend in the +Y direction.

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

The fourth hole-shaped flow path 16D is located at a position lower than the upper region 16B1 (that is, located on the −Z direction side of the upper region 16B1 ). The fourth hole-shaped flow channel 16D has an oval shape when viewed in the X direction. The fourth hole-shaped flow channel 16D is an elongated hole extending in the Y direction.

The fifth hole-shaped flow channel 16E is located at a lower position than the fourth hole-shaped flow channel 16D (that is, on the -Z direction side of the fourth hole-shaped flow channel 16D). The fifth hole-shaped flow path 16E has an oval shape when viewed in the X direction. The fifth hole-shaped flow path 16E is an elongated hole extending in the Y direction.

The sixth hole-shaped flow path 16F is located at a position lower than the lower region 16B3 (that is, located on the −Z direction side of the lower region 16B3 ). The sixth hole-shaped flow channel 16F is located at a position aligned with the fifth hole-shaped flow channel 16E in the Y direction. The sixth hole-shaped flow channel 16F is located on the +Y direction side with respect to the fifth hole-shaped flow channel 16E. The fifth hole-shaped flow channel 16E and the sixth hole-shaped flow channel 16F are formed at intervals in the Y direction.

A plurality of hole-shaped flow paths 17 are formed in the second intermediate plate body 14 . The hole-shaped flow path 17 penetrates the second intermediate plate body 14 in the thickness direction. The plurality of hole-shaped flow channels 17 include a first hole-shaped flow channel 17A to a fifth hole-shaped flow channel 17E.

The first hole-shaped flow channel 17A has the same shape as the first hole-shaped flow channel 16A. When viewed from the X direction, the first hole-shaped flow path 17A is at a position corresponding to the first hole-shaped flow path 16A. The second hole-shaped flow channel 17B has the same shape as the third hole-shaped flow channel 16C. When viewed from the X direction, the second hole-shaped flow channel 17B is located at a position corresponding to the third hole-shaped flow channel 16C. The third hole-shaped flow channel 17C has the same shape as the fourth hole-shaped flow channel 16D. When viewed from the X direction, the third hole-shaped flow path 17C is at a position corresponding to the fourth hole-shaped flow path 16D. The fourth hole-shaped flow channel 17D has the same shape as the fifth hole-shaped flow channel 16E. When viewed from the X direction, the fourth hole-shaped flow path 17D is in a position corresponding to the fifth hole-shaped flow path 16E. The fifth hole-shaped flow channel 17E has the same shape as the sixth hole-shaped flow channel 16F. When viewed from the X direction, the fifth hole-shaped flow channel 17E is located at a position corresponding to the sixth hole-shaped flow channel 16F. The fourth hole-shaped flow path 17D and the fifth concave portion 17E are formed at intervals in the Y direction.

A plurality of hole-shaped flow paths 18 are formed in the third intermediate plate body 15 . The hole-shaped flow path 18 penetrates 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 body.

The plurality of hole-shaped flow channels 18 include a first hole-shaped flow channel 18A to a third hole-shaped flow channel 18C.

The first hole-shaped flow channel 18A has the same shape as the first hole-shaped flow channel 17A. When viewed from the X direction, the first hole-shaped flow path 18A is at a position corresponding to the first hole-shaped flow path 17A. The second hole-shaped flow path 18B (first switching flow path) has a lower region 18B1, a connection region 18B2, and an upper region 18B3. The lower region 18B1 is located at a position lower than the first hole-shaped flow path 18A (that is, on the −Z direction side of the first hole-shaped flow path 18A). The lower region 18B1 is an elongated hole extending in the Y direction.

The upper area 18B3 is at a higher position than the lower area 18B1. The upper region 18B3 is located at a position lower than the first hole-shaped flow path 18A (that is, 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 the +Y direction relative to the lower region 18B1.

The connection region 18B2 connects the end of the lower region 18B1 in the +Y direction and the end of the upper region 18B3 in the −Y direction. The connection region 18B2 is a long hole extending obliquely so as to rise in the +Y direction.

The third hole-shaped flow channel 18C has an oval shape when viewed in the X direction. The third hole-shaped flow channel 18C is an elongated hole extending in the Y direction. The third hole-shaped flow channel 18C is located at the lowest position (that is, the position on the most -Z direction side) among the first hole-shaped flow channel 18A to the third hole-shaped flow channel 18C. The third hole-shaped flow path 18C has a length including the fourth hole-shaped flow path 17D and the fifth concave portion 17E as viewed from the X direction. When viewed from the X direction, the end in the -Y direction of the third hole-shaped flow channel 18C coincides with the end in the -Y direction of the fourth hole-shaped flow channel 17D. When viewed from the X direction, the +Y direction end of the third hole-shaped flow channel 18C coincides with the +Y direction end of the fifth concave portion 17E.

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

As shown in FIG. 4 , the hole-shaped flow passages 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 passage portion 19 (space).

Insertion portions 42 and 43 are formed in the first outer plate body 12 . For example, the insertion parts 42 and 43 have a circular shape.

A tubular first refrigerant port 51 is inserted into the insertion portion 42 . The end portion of the first refrigerant port 51 is opened inside the third hole-shaped flow path 18C. This opening serves as an introduction port for introducing the refrigerant into the heat exchanger 4 or a lead-out port for taking out the refrigerant from the heat exchanger 4 .

A tubular second refrigerant port 52 is inserted into the insertion portion 43 . The end portion of the second refrigerant port 52 is opened inside the first hole-shaped flow path 18A. This opening serves as an introduction port for introducing the refrigerant into the heat exchanger 4 or a lead-out port for taking out the refrigerant from the heat exchanger 4 .

FIG. 5 is an exploded perspective view of the second header 20 . FIG. 6 is a cross-sectional view of the second header 20 taken along the XZ plane.

As shown in FIGS. 5 and 6 , the second header 20 is configured by stacking the second inner plate body 21 , the second intermediate plate body 23 , and the second outer plate body 22 in this order. The second inner plate body 21 , the second intermediate plate body 23 , and the second outer plate body 22 are formed of materials with high thermal conductivity and small specific gravity, such as aluminum and aluminum alloys. 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 arranged to face the surface (first principal surface 21 a ) of the second inner plate body 21 on the −X direction side. The second intermediate plate body 23 is provided between the second inner plate body 21 and the second outer plate body 22 .

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

A plurality of insertion portions 44 are formed in the second inner plate body 21 . The insertion portion 44 penetrates the second inner plate body 21 in the thickness direction. The insertion portion 44 is formed in a slit shape parallel to the Y direction. The end portion of the heat exchange tube 30 is inserted into the insertion portion 44 .

A plurality of hole-shaped flow paths 24 are formed in the second intermediate plate body 23 . The hole-shaped flow path 24 penetrates the second intermediate plate body 23 in the thickness direction.

The plurality of hole-shaped flow channels 24 include a first hole-shaped flow channel 24A to a fourth hole-shaped flow channel 24D. The first to fourth hole-shaped flow channels 24A to 24D have a rectangular shape when viewed in the X direction. The first hole-shaped flow channel 24A and the second hole-shaped flow channel 24B are formed to be aligned in the Y direction. The third hole-shaped flow channel 24C is located on the -Z direction side of the first hole-shaped flow channel 24A. The fourth hole-shaped flow channel 24D is located on the −Z direction side of the second hole-shaped flow channel 24B. The third hole-shaped flow channel 24C and the fourth hole-shaped flow channel 24D are formed to be aligned in the Y direction.

As shown in FIG. 6 , the hole-shaped flow passages 24 of the second inner plate body 21 , the second intermediate plate body 23 , and the second outer plate body 22 form a header flow passage portion 26 (space).

As shown in FIG. 5 , the header flow path portion 26 partitioned 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 partitioned 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 partitioned 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 partitioned by the fourth hole-shaped flow path 24D is referred to as a fourth header flow path portion 26D.

As shown in FIG. 2, the 1st header 10 and the 2nd header 20 are mutually spaced apart and arranged in the X direction.

The heat exchange tube 30 is formed of a material with high thermal conductivity and small specific gravity, such as aluminum or aluminum alloy. The heat exchange tube 30 is formed in a flattened tube shape. That is, the dimension in the Y direction of the heat exchange tube 30 is larger than the dimension in the Z direction. The shape of the cross section (YZ cross section) orthogonal to the longitudinal direction of the heat exchange tube 30 is an oval shape. The heat exchange tubes 30 extend along the X direction. A refrigerant flow path 34 (see FIG. 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 .

At least a part of the plurality of heat exchange tubes 30 are arranged at intervals in the Z direction. The end portions of the heat exchange tubes 30 in the +X direction are inserted into the insertion portions 41 (see FIG. 4 ) formed in the first headers 10 . As a result, the ends in the +X direction of the refrigerant flow paths 34 of the heat exchange tubes 30 are opened inside the header flow path portions 19 of the first headers 10 . Therefore, the header flow path portion 19 communicates with the refrigerant flow path 34 of the heat exchange tube 30 .

The ends in the −X direction of the heat exchange tubes 30 are inserted into the insertion portions 44 (see FIG. 6 ) formed in the second header 20 . As a result, the ends in the −X direction of the refrigerant flow paths 34 of the heat exchange tubes 30 are opened inside the header flow path portions 26 of the second headers 20 . Therefore, the header flow path portion 26 communicates with the refrigerant flow path 34 of the heat exchange tube 30 .

For example, the plurality of heat exchange tubes 30 constitute four heat exchange tube pairs 31 . One pair of heat exchange tubes 31 is constituted by a pair of heat exchange tubes 30 and 30 arranged in a row in the +Y direction. The four heat exchange tube pairs 31 are arranged at intervals up and down.

Among the four heat exchange pipe pairs 31, the first heat exchange pipe pair 31A from the top includes two heat exchange pipes 30A and 30B arranged in this order in the +Y direction.

The second heat exchange tube pair 31B from above 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 this order 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.

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 this order in the +Y direction. That is, the two heat exchange tubes 30 constituting 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 toward the +Y direction.

The fourth heat exchange tube pair 31D from the top includes two heat exchange tubes 30G and 30H arranged in order in the +Y direction.

The heat exchange tubes 30A, 30C, 30E, and 30G are arranged on one side in the Y direction (the −Y direction side. That is, the front side in FIG. 2 ). The heat exchange tubes 30B, 30D, 30F, and 30H are arranged on the other side in the Y direction (the +Y direction side. That is, the back side in FIG. 2 ).

The first upstream heat exchange pipe 30E communicates with the second downstream heat exchange pipe 30D through the second hole-shaped flow path 18B (first switching flow path) (see FIG. 3 ).

The second upstream heat exchange pipe 30F communicates with the first downstream heat exchange pipe 30C through the second hole-shaped flow path 16B (second switching flow path) (see FIG. 3 ).

The gaps between the first header 10 and the second header 20 and the heat exchange tubes 30 are 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 exchanger 4 is assembled by inserting the heat exchange tubes 30 into the first header 10 and the second header 20 . The assembled heat exchanger 4 is heated in the furnace. The heating melts the solder on the inner surfaces of the first header 10 and the second header 20 . The molten solder blocks the gaps between the first header 10 and the second header 20 and the heat exchange tubes 30 . The heat exchanger 4 is cooled and the solder solidifies. Thereby, the first header 10, the second header 20, and the heat exchange tubes 30 are fixed.

An external air flow path along the Y direction is formed between the vertically adjacent heat exchange tubes 30 . The heat exchanger 4 circulates the outside air in the outside air flow path by a blower fan (not shown) or the like. The heat exchanger 4 performs heat exchange between the outside air flowing through the outside air flow path and the refrigerant flowing through the refrigerant flow path 34 . The heat exchange is performed indirectly via the heat exchange tubes 30 .

When the refrigeration cycle apparatus 1 shown in FIG. 1 performs a cooling operation, the outdoor heat exchanger 4 functions as a condenser. In this case, the gas refrigerant flowing out of the compressor 2 flows into the outdoor heat exchanger 4 .

As shown in FIG. 2 , the refrigerant flows into the inside of the first header 10 from the first refrigerant port 51 . The refrigerant that has flowed into the header flow path portion 19 (see FIG. 3 ) of the third hole-shaped flow path 18C from the first refrigerant port 51 is distributed to the hole-shaped flow paths 17D and 16E and the hole-shaped flow paths 17E and 16F, and flow. The refrigerant flowing in the hole-shaped flow paths 17D and 16E is referred to as a "first refrigerant". The refrigerant flowing in the hole-shaped flow paths 17E and 16F is referred to as a "second refrigerant".

The first refrigerant flows in the -X direction in the heat exchange tube 30 ( 30G) from the hole-shaped flow paths 17D and 16E (see FIG. 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 +X direction in the heat exchange tubes 30 ( 30E) from the upper portion of the third header flow path portion 26C, and flows into the second hole-shaped flow paths 16D and 17C through the hole-shaped flow paths 16D and 17C of the first header 10 . The flow path 18B (first conversion flow path) (see FIG. 3 ). The first refrigerant passes from the lower region 18B1 of the second hole-shaped flow path 18B, passes through the connecting region 18B2 and the upper region 18B3, and reaches the hole-shaped flow paths 17B and 16C. The first refrigerant flows in the −X direction in the heat exchange tubes 30 ( 30D) from the hole-shaped flow paths 17B and 16C, and flows into the lower portion of the second header flow path portion 26B of the second header 20 . The first refrigerant flows in the +X direction in the heat exchange tube 30 ( 30B) from the upper portion of the second header flow path portion 26B, and passes through the second header 10 through the hole-shaped flow paths 16A, 17A, and 18A of the second header 10 . The refrigerant port 52 flows out.

Among the heat exchange tubes 30G, 30E, 30D, and 30B through which the first refrigerant passes, the number of heat exchange tubes 30E and 30G arranged on one side in the Y direction (the −Y direction side; the near side in FIG. 2 ) is two. indivual. The number of heat exchange tubes 30B and 30D arranged on the other side in the Y direction (+Y direction side. That is, the back side in FIG. 2 ) is two. Therefore, the number of heat exchange tubes 30 on one side in the Y direction and the number of heat exchange tubes 30 on the other side are the same. Therefore, the variation of the heat exchange efficiency in the Y direction can be suppressed.

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

Among the heat exchange tubes 30H, 30F, 30C, and 30A through which the second refrigerant passes, the number of heat exchange tubes 30C and 30A arranged on one side in the Y direction (-Y direction side. The near side in FIG. 2 ) is two. indivual. The number of heat exchange tubes 30H and 30F arranged on the other side in the Y direction (+Y direction side. That is, the back side in FIG. 2 ) is two. Therefore, the number of heat exchange tubes 30 on one side in the Y direction and the number of heat exchange tubes 30 on the other side are the same. Therefore, the variation of the heat exchange efficiency in the Y direction can be suppressed.

The gas refrigerant dissipates heat to the outside air and condenses in the process of flowing through the heat exchange tubes 30 . The condensed refrigerant turns into a liquid refrigerant, and flows out of the heat exchanger 4 from the second refrigerant port 52 .

When the refrigeration cycle apparatus 1 shown in FIG. 1 performs the 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 .

In the heat exchanger 4 of the embodiment, the intermediate plate bodies 13 to 15 are formed with the second hole-shaped flow path 18B (first switching flow path) and the second hole-shaped flow path 16B (second switching flow path). 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 in heat exchange efficiency can be suppressed.

In the heat exchanger 4 of the embodiment, the first header 10 is provided with a refrigerant port 51 having a refrigerant inlet port and a refrigerant port 52 having a refrigerant outlet port (see FIG. 2 ). In the heat exchanger 4, since both the refrigerant ports 51 and 52 are provided in the first header 10, the size can be reduced as compared with the case where the refrigerant ports are distributed in two headers. Therefore, the heat exchanger 4 is excellent in housing property in the casing.

In the heat exchanger 4 of the embodiment, since the first header 10 and the second header 20 are composed of the plates 11 to 14, the structure of the header can be simplified. Therefore, miniaturization and weight reduction can be achieved. Therefore, the heat exchanger 4 is excellent in housing property in the casing.

As a comparison, a heat exchanger without headers is assumed. This heat exchanger uses a meandering heat exchange tube in which straight portions and curved portions are alternately formed. When a flat-shaped heat exchange tube is used, it is necessary to increase the radius of curvature of the curved portion in order to prevent buckling, and it is difficult to reduce the size of the heat exchanger. The radius of curvature can be reduced by using the circular tube-shaped heat exchange tube only in the curved portion. However, in this case, a mechanism for connecting the flat-shaped heat exchange tube and the circular tube-shaped heat exchange tube is required, and thus it is difficult to achieve miniaturization.

7 is a cross-sectional view along the XZ plane of the first header 10A according to the first modification. The same reference numerals are assigned to the components already described, and the description thereof will be omitted.

The first header 10A uses the first inner plate body 111 in place of the first inner plate body 11 (see FIG. 5 ). In the first header 10A, the first outer plate body 112 is used instead of the first outer plate body 12 (see FIG. 5 ).

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

The first outer plate body 112 includes a plate body main portion 115 and a cover layer 116 . For example, the plate body main portion 115 is composed of a material containing aluminum (aluminum, aluminum alloy, etc.). The cover layer 116 is provided on the outer surface 115b (second main surface) of the board main portion 115 . The outer surface 115b is a surface opposite to the first main surface, and the first main surface is a surface opposed to the first inner plate body 111 . The cover layer 116 is composed of a metal material containing Zn. For example, the cover layer 115 is made of a 7000 series aluminum alloy. The Zn content (content ratio) in the cover layer 116 is higher than the Zn content (content ratio) in the plate body main portion 115 .

The first inner plate body 111 and the first outer plate body 112 can be produced using a clad steel material (laminated plate material) in which a Zn-containing coating layer is formed in advance. The cover layer can also be formed by thermal spraying.

For the second header, similarly to the first header 10A, a plate body having a covering layer can be used.

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.

8 is a cross-sectional view along the XZ plane of the first header 10B according to the second modification. The same code|symbol is attached|subjected to the structure already demonstrated, and description is abbreviate|omitted.

As shown in FIG. 8 , among 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 , the first header 10B faces the main surface of the other plate materials. A low melting point layer 214 is provided thereon.

For example, the plate bodies 11 to 15 are made of a material containing aluminum (aluminum, aluminum alloy, etc.). The low melting point layer 214 is made of a metal material containing Si. For example, the low melting point layer 214 is made of a 4000 series aluminum alloy. The Si content (content ratio) in the low melting point layer 214 is higher than the Si content (content ratio) in the plate materials 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 materials 11 to 15 .

The plate material having the low melting point layer 214 can be produced using a clad steel material (laminated plate material) in which a low melting point layer containing Si is 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.

For the second header, similarly to the first header 10B, a plate body having a low melting point layer can be used.

In this heat exchanger, the low melting point layer 214 functions as a solder for sealing the gaps between the first headers 10 and the second headers 20 and the heat exchange tubes 30, so that the work of soldering is facilitated.

FIG. 9 is an exploded perspective view of the first header 10C according to the third modification. 10 is a cross-sectional view along the XZ plane of the first header 10C according to the third modification. The same code|symbol is attached|subjected to the structure already demonstrated, and description is abbreviate|omitted.

As shown in FIGS. 9 and 10 , in the first header 10C, a convex portion 301 protruding into the hole-shaped flow path 18 is formed on the second intermediate plate body 14 . The convex portion 301 may have a wall shape whose thickness is reduced in the protruding direction. Moreover, the shape of a convex part is not specifically limited, A prismatic shape, a rectangular parallelepiped shape, a hemispherical shape, etc. may be sufficient.

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

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

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

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 other various forms, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the scope of the patent claims and the scope equivalent thereto.

Explanation of symbols

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: 1st outer plate body (outer plate body); 12a: 1st main surface; 13: 1st intermediate plate body (intermediate plate body); 14: 2nd intermediate plate body (intermediate plate body); 15 : third intermediate plate body (intermediate plate body); 16B: second hole-shaped flow path (second switching flow path); 18B: second hole-shaped flow path (first switching flow path); 113b: outer surface (first switching flow path) 2 main surface); 115b: outer surface (second main surface); 30: heat exchange pipe; 30C: first downstream heat exchange pipe; 30D: second downstream heat exchange pipe; 30E: first upstream heat exchange tube; 30F: second upstream heat exchange tube; 34: refrigerant flow path; 113b: outer surface (2nd main surface); 114, 116: coating layer; 115b: outer surface (2nd main surface); 301: convex part.

Claims (6)

1. A heat exchanger comprising: a plurality of heat exchange tubes forming a refrigerant flow path for the refrigerant to flow; and headers, arranged at the ends of the above-mentioned 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 the first direction, and a first downstream heat exchange tube arranged in parallel in the first direction. and the second downstream heat exchange tube, 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, The intermediate plate body is formed with a first switching flow path that communicates the refrigerant flow path of the first downstream heat exchange tube and the refrigerant flow path of the second upstream heat exchange tube, and the second downstream flow path. The refrigerant flow path of the side heat exchange tube is a second switching flow path that communicates with the refrigerant flow path of the first upstream side heat exchange tube. 2. The heat exchanger of claim 1, wherein: Among the plurality of heat exchange tubes having a refrigerant flow path communicating with the first switching flow path, the heat exchange pipe arranged on one side in the first direction and the heat exchange tube arranged on the other side in the first direction exchange heat Tubes are the same number, Among the plurality of heat exchange tubes having the refrigerant flow paths communicating with the second switching flow paths, the heat exchange tubes arranged on one side in the first direction exchange heat with the heat exchange tubes arranged on the other side in the first direction. Tubes are the same number. 3. The heat exchanger of claim 1 or 2, wherein, The said outer plate body is provided with the coating layer containing Zn on the 2nd main surface opposite to the 1st main surface, and this 1st main surface opposes the said inner plate body. 4. The heat exchanger according to any one of claims 1 to 3, wherein, In one of the headers provided at one end and the other end of the heat exchange tubes, an introduction port for introducing the refrigerant into the heat exchanger and for leading out the refrigerant from the heat exchanger are formed in one of the headers. export. 5. The heat exchanger of any one of claims 1 to 4, wherein, The intermediate plate body is formed with a convex portion or a concave portion that promotes the diversion of the refrigerant introduced into the heat exchanger. 6. A refrigeration cycle device, wherein, With the heat exchanger of any one of claims 1 to 5.

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