JP2023158158A - Heat exchanger and refrigeration cycle device - Google Patents

Abstract

To provide a heat exchanger and a refrigeration cycle device that can enhance heat exchange efficiency.SOLUTION: A heat exchanger according to an embodiment comprises a plurality of heat exchange tubes, and a header. In the plurality of heat exchange tubes, refrigerant passages through which a refrigerant flows are formed. The header is provided on end parts of the heat exchange tubes. The plurality of heat exchange tubes includes first and second upstream side heat exchange tubes, and first and second downstream side heat exchange tubes. The header comprises an inner plate body, an outer plate body, and a plurality of intermediate plate bodies. In the intermediate plate bodies, a first transfer flow passage is formed. The first transfer flow passage allows the refrigerant passage of the first upstream side heat exchange tube to communicate with the refrigerant passage of the second downstream side heat exchange tube. The first transfer flow passage comprises a first region, a second region, and a connection region. The first region communicates with the refrigerant passage of the first upstream side heat exchange tube. The second region communicates with the refrigerant passage of the second downstream side heat exchange tube. The connection region connects the first region and the second region.SELECTED DRAWING: Figure 3

Description

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

A header type heat exchanger has a plurality of heat exchange tubes and a header. A refrigerant flow path is formed inside the heat exchange tube. A header is provided at the end of the heat exchange tube. Heat exchangers are required to have improved heat exchange efficiency.

International Publication No. 2015/037641

The problem to be solved by the present invention is to provide a heat exchanger and a refrigeration cycle device that can improve heat exchange efficiency.

The heat exchanger of the embodiment has a plurality of heat exchange tubes and a header. A refrigerant flow path through which a refrigerant flows is formed in the plurality of heat exchange tubes. The header is provided at the end of the heat exchange tube. The plurality of heat exchange tubes include first and second upstream heat exchange tubes arranged in parallel in this order in the first direction, and first and second upstream heat exchange tubes arranged in parallel in this order in the first direction. and a downstream heat exchange tube. At least one header is provided between an inner plate body to which the heat exchange tube is connected, an outer plate body disposed facing the inner plate body, and the inner plate body and the outer plate body. and a plurality of intermediate plate bodies. A first transition flow path is formed in the intermediate plate. The first transition flow path communicates the refrigerant flow path of the first upstream heat exchange tube with the refrigerant flow path of the second downstream heat exchange tube. The first transition flow path has a first region, a second region, and a connection region. The first region communicates with a refrigerant flow path of the first upstream heat exchange tube. The second region communicates with the refrigerant flow path of the second downstream heat exchange tube. The connection area connects the first area and the second area.

The heat exchanger of the embodiment has a plurality of heat exchange tubes and a header. A refrigerant flow path through which a refrigerant flows is formed in the plurality of heat exchange tubes. The header is provided at the end of the heat exchange tube. The plurality of heat exchange tubes include first and second upstream heat exchange tubes arranged in parallel in this order in the first direction, and first and second upstream heat exchange tubes arranged in parallel in this order in the first direction. and a downstream heat exchange tube. At least one header is provided between an inner plate body to which the heat exchange tube is connected, an outer plate body disposed facing the inner plate body, and the inner plate body and the outer plate body. and a plurality of intermediate plate bodies. A first transition flow path and a second transition flow path are formed in the intermediate plate. The first transition flow path communicates the refrigerant flow path of the first upstream heat exchange tube with the refrigerant flow path of the second downstream heat exchange tube. The second transition flow path communicates the refrigerant flow path of the second upstream heat exchange tube with the refrigerant flow path of the first downstream heat exchange tube. At least one of the first transition channels and at least one of the second transition channels are formed in mutually different intermediate plates among the plurality of intermediate plates.

FIG. 1 is a schematic configuration diagram of a refrigeration cycle device in an embodiment. FIG. 2 is a transparent perspective view of a heat exchanger in an embodiment. FIG. 2 is an exploded perspective view of a heat exchanger in an embodiment. FIG. 3 is a sectional view of the first header. FIG. 6 is an exploded perspective view of the second header. FIG. 3 is a cross-sectional view of the second header. FIG. 7 is a sectional view of a first header of a first modification. FIG. 7 is a sectional view of a first header of a second modification. The exploded perspective view of the 1st header of a 3rd modification. FIG. 7 is a sectional view of a first header of a third modification.

Hereinafter, a heat exchanger according to an embodiment will be described with reference to the drawings.
In this application, the X direction, Y direction, and 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 a vertical direction, and the +Z direction is an upward direction. The X direction is the central axis direction (extending direction) of the heat exchange tube. For example, the X direction is a horizontal direction, and the +X direction is a 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. It is desirable that the Y direction is a horizontal direction.

FIG. 1 is a schematic configuration diagram of a refrigeration cycle device according to an embodiment.
As shown in FIG. 1, 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 and has. The components of the refrigeration cycle device 1 are sequentially connected by piping 7. In FIG. 1, the direction of flow of refrigerant (heat medium) during cooling operation is shown by solid line arrows, and the direction of flow of refrigerant during heating operation is shown by broken line arrows.

The compressor 2 includes a compressor main body 2A and an accumulator 2B. The compressor main body 2A compresses the low-pressure gas refrigerant taken into the interior into a high-temperature, 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 and switches between cooling operation and heating operation. During cooling operation, the refrigerant flows through the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion device 5, and the indoor heat exchanger 6 in this order. 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 room. During heating operation, the refrigerant flows through the compressor 2, the four-way valve 3, the indoor heat exchanger 6, the expansion device 5, and the outdoor heat exchanger 4 in this order. 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 room.

The condenser converts the high-temperature, high-pressure gas refrigerant discharged from the compressor 2 into high-pressure liquid refrigerant by radiating heat to the outside air and condensing it.
The expansion device 5 lowers the pressure of the high-pressure liquid refrigerant sent from the condenser to convert it into a low-temperature, low-pressure gas-liquid two-phase refrigerant.
The evaporator converts the low-temperature, low-pressure gas-liquid two-phase refrigerant sent from the expansion device 5 into a low-pressure gas refrigerant by absorbing heat from the outside air and vaporizing it.

In this way, in the refrigeration cycle device 1, the refrigerant, which is the working fluid, circulates while changing its phase between the gas refrigerant and the liquid refrigerant. A refrigerant releases heat during a phase change from a gas refrigerant to a liquid refrigerant, and absorbs heat during a phase change from a liquid refrigerant to a gas refrigerant. The refrigeration cycle device 1 performs heating, cooling, defrosting, etc. using heat radiation or absorption of refrigerant.

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

The heat exchanger 4 includes a first header 10, a second header 20, and a heat exchange tube (heat transfer tube) 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 along the XZ plane.

As shown in FIG. 3, the first header 10 includes a first inner plate 11, a first intermediate plate 13, a second intermediate plate 14, a third intermediate plate 15, and a first outer plate. The body 12 is laminated in this order.
The first inner plate 11, the first to third intermediate plates 13 to 15, and the first outer plate 12 are made of a material with high thermal conductivity and low specific gravity, such as aluminum or aluminum alloy. The first inner plate 11, the first to third intermediate plates 13 to 15, and the first outer plate 12 are approximately parallel to the YZ plane. The first outer plate body 12 is arranged to face the +X direction side surface (first main surface 11a) of the first inner plate body 11. The first to third intermediate plates 13 to 15 are provided between the first inner plate 11 and the first outer plate 12.

The first main surface 11 a of the first inner plate 11 is a main surface of the first inner plate 11 and is a surface facing the first outer plate 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 plate body 11 . The insertion portion 41 penetrates the first inner plate body 11 in the thickness direction. The insertion portion 41 is formed in a slit shape parallel to the Y direction. The end 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-like channels 16 are formed in the first intermediate plate 13 . The hole-like channel 16 penetrates the first intermediate plate body 13 in the thickness direction. The plurality of hole-shaped channels 16 include a first hole-shaped channel 16A to a sixth hole-shaped channel 16F.
The first hole-shaped channel 16A has an oval shape when viewed from the X direction. The "elliptical shape" is a shape composed of two straight lines that are parallel and facing each other, and a curved convex curve (for example, semicircular shape, elliptical arc shape, etc.) that connects the ends of the two straight lines. The first hole-shaped channel 16A is a long hole extending in the Y direction. The first hole-like flow path 16A is located at the highest position among the first hole-like flow path 16A to the sixth hole-like flow path 16F (that is, located closest to the +Z direction side).

The second hole-like channel 16B (second transition channel) has an upper region 16B1, a connection region 16B2, and a lower region 16B3. The upper region 16B1 is located at a lower position than the first hole-like flow path 16A (that is, it is located on the -Z direction side of the first hole-like flow path 16A). The upper region 16B1 is a long hole extending in the Y direction.

The lower region 16B3 is located at a lower position than the third hole-like flow path 16C (that is, it is located on the -Z direction side of the third hole-like flow path 16C). The lower region 16B3 is a long hole extending in the Y direction. The lower region 16B3 is located closer to the +Y direction than the upper region 16B1. The lower region 16B3 is located at a position aligned with the fourth hole-shaped channel 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 region 16B3 is located at a lower position than the upper region 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 that extends downwardly toward the +Y direction.

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

The fourth hole-like channel 16D is located at a lower position than the upper region 16B1 (that is, located on the -Z direction side of the upper region 16B1). The fourth hole-shaped channel 16D has an oval shape when viewed from the X direction. The fourth hole-shaped channel 16D is a long hole extending in the Y direction.
The fifth hole-like flow path 16E is located at a lower position than the fourth hole-like flow path 16D (that is, it is located on the -Z direction side of the fourth hole-like flow path 16D). The fifth hole-shaped channel 16E has an oval shape when viewed from the X direction. The fifth hole-shaped channel 16E is a long hole extending in the Y direction.
The sixth hole-like channel 16F is located at a lower position with respect to the lower region 16B3 (that is, located on the -Z direction side of the lower region 16B3). The sixth hole-like flow path 16F is located in line with the fifth hole-like flow path 16E in the Y direction. The sixth hole-like flow path 16F is located on the +Y direction side with respect to the fifth hole-like flow path 16E. The fifth hole-like flow path 16E and the sixth hole-like flow path 16F are formed at intervals in the Y direction.

A plurality of hole-shaped channels 17 are formed in the second intermediate plate 14 . The hole-like channel 17 penetrates the second intermediate plate body 14 in the thickness direction. The plurality of hole-shaped channels 17 include a first hole-shaped channel 17A to a fifth hole-shaped channel 17E.
The first hole-like flow path 17A has the same shape as the first hole-like flow path 16A. The first hole-like flow path 17A is located at a position that coincides with the first hole-like flow path 16A when viewed from the X direction. The second hole-like flow path 17B has the same shape as the third hole-like flow path 16C. The second hole-like flow path 17B is located at a position that coincides with the third hole-like flow path 16C when viewed from the X direction. The third hole-like flow path 17C has the same shape as the fourth hole-like flow path 16D. The third hole-like flow path 17C is located at a position that coincides with the fourth hole-like flow path 16D when viewed from the X direction. The fourth hole-like flow path 17D has the same shape as the fifth hole-like flow path 16E. The fourth hole-like flow path 17D is located at a position that coincides with the fifth hole-like flow path 16E when viewed from the X direction. The fifth hole-like flow path 17E has the same shape as the sixth hole-like flow path 16F. The fifth hole-like flow path 17E is located at a position that coincides with the sixth hole-like flow path 16F when viewed from the X direction. The fourth hole-like flow path 17D and the fifth hole-like flow path 17E are formed at intervals in the Y direction.

A plurality of hole-shaped channels 18 are formed in the third intermediate plate 15 . The hole-like channel 18 penetrates the third intermediate plate 15 in the thickness direction. The hole-shaped channels 16 to 18 can be formed by punching a flat plate.

The plurality of hole-shaped channels 18 include a first hole-shaped channel 18A to a third hole-shaped channel 18C.
The first hole-like flow path 18A has the same shape as the first hole-like flow path 17A. The first hole-like flow path 18A is located at a position that coincides with the first hole-like flow path 17A when viewed from the X direction. The second hole-like channel 18B (first transition channel) has a lower region 18B1, a connection region 18B2, and an upper region 18B3. The lower region 18B1 is located at a lower position than the first hole-like flow path 18A (that is, it is located on the -Z direction side of the first hole-like flow path 18A). The lower region 18B1 is a long hole extending in the Y direction.

The upper region 18B3 is located at a higher position than the lower region 18B1. The upper region 18B3 is located at a lower position than the first hole-like flow path 18A (that is, it is located on the -Z direction side of the first hole-like flow path 18A). The upper region 18B3 is a long hole extending in the Y direction. The upper region 18B3 is located closer to the +Y direction than 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 that extends upward in the +Y direction.

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

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

As shown in FIG. 4, the first inner plate 11, the hole-shaped passages 16 to 18 of the intermediate plates 13 to 15, and the first outer plate 12 define a head passage portion 19 (space). Form.

Insert 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 of the first refrigerant port 51 opens into the third hole-shaped flow path 18C. This opening serves as an inlet for introducing the refrigerant into the heat exchanger 4 or an outlet for leading out the refrigerant from the heat exchanger 4.
A tubular second refrigerant port 52 is inserted into the insertion portion 43 . An end of the second refrigerant port 52 opens into the first hole-shaped flow path 18A. This opening serves as an inlet for introducing the refrigerant into the heat exchanger 4 or an outlet for leading 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 along the XZ plane.
As shown in FIGS. 5 and 6, the second header 20 is constructed by laminating a second inner plate 21, a second intermediate plate 23, and a second outer plate 22 in this order. There is. The second inner plate 21, the second intermediate plate 23, and the second outer plate 22 are made of a material with high thermal conductivity and low specific gravity, such as aluminum or aluminum alloy. The second inner plate body 21, the second intermediate plate body 23, and the second outer plate body 22 are generally parallel to the YZ plane. The second outer plate body 22 is arranged to face the -X direction side surface (first main surface 21a) of the second inner plate body 21. The second intermediate plate 23 is provided between the second inner plate 21 and the second outer plate 22.

The first main surface 21 a is a main surface of the second inner plate 21 and is a surface facing the second outer plate 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 of the heat exchange tube 30 is inserted into the insertion portion 44 .

A plurality of hole-shaped channels 24 are formed in the second intermediate plate body 23 . The hole-like channel 24 penetrates the second intermediate plate body 23 in the thickness direction.

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

As shown in FIG. 6, the second inner plate 21, the hole-like flow path 24 of the second intermediate plate 23, and the second outer plate 22 form a head flow path portion 26 (space). .
As shown in FIG. 5, the head flow path portion 26 defined by the first hole-shaped flow path 24A is referred to as a first head flow path portion 26A. The head flow path portion 26 defined by the second hole-shaped flow path 24B is referred to as a second head flow path portion 26B. The head flow path portion 26 defined by the third hole-shaped flow path 24C is referred to as a third head flow path portion 26C. The head flow path portion 26 defined by the fourth hole-like flow path 24D is referred to as a fourth head flow path portion 26D.

As shown in FIG. 2, the first header 10 and the second header 20 are arranged side by side and spaced apart from each other in the X direction.

The heat exchange tube 30 is made of a material with high thermal conductivity and low specific gravity, such as aluminum or aluminum alloy. The heat exchange tube 30 is formed into a flat tube shape. That is, the heat exchange tube 30 has a larger dimension in the Y direction than in the Z direction. The shape of the cross section (YZ cross section) perpendicular to the length direction of the heat exchange tube 30 is an ellipse. Heat exchange tube 30 extends in 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 some of the plurality of heat exchange tubes 30 are arranged in parallel at intervals in the Z direction. The end of the heat exchange tube 30 in the +X direction is inserted into the insertion part 41 formed in the first header 10 (see FIG. 4). As a result, the end of the refrigerant flow path 34 of the heat exchange tube 30 in the +X direction opens into the inside of the head flow path portion 19 of the first header 10 . Therefore, the head passage section 19 communicates with the refrigerant passage 34 of the heat exchange tube 30.

The end of the heat exchange tube 30 in the −X direction is inserted into the insertion portion 44 formed in the second header 20 (see FIG. 6). As a result, the end of the refrigerant flow path 34 of the heat exchange tube 30 in the −X direction opens into the inside of the head flow path portion 26 of the second header 20 . Therefore, the head passage section 26 communicates with the refrigerant passage 34 of the heat exchange tube 30.

For example, the 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 parallel in the +Y direction. The four heat exchange tube pairs 31 are arranged vertically at intervals.

The first heat exchange tube pair 31A from the top among the four heat exchange tube pairs 31 includes two heat exchange tubes 30A and 30B arranged in parallel in this order in the +Y direction.

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 parallel 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 the top 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 parallel 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 pair of heat exchange tubes 31D from the top includes two heat exchange tubes 30G and 30H arranged in parallel in this order in the +Y direction.

The heat exchange tubes 30A, 30C, 30E, and 30G are arranged on one side in the Y direction (-Y direction side, that is, on the near side in FIG. 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, on the back side in FIG. 2).

The first upstream heat exchange tube 30E is communicated with the second downstream heat exchange tube 30D through a second hole-shaped flow path 18B (first transition flow path) (see FIG. 3).
The second upstream heat exchange tube 30F is communicated with the first downstream heat exchange tube 30C through a second hole-like flow path 16B (second transition flow path) (see FIG. 3).

The gaps between the first header 10, the second header 20, and the heat exchange tube 30 are sealed by brazing or the like. The specific procedure for brazing is as follows. The inner surfaces of the first header 10 and the second header 20 are coated with wax. Heat exchange tubes 30 are inserted into the first header 10 and the second header 20, and the heat exchanger 4 is assembled. The assembled heat exchanger 4 is heated in a furnace. The heating melts the wax on the inner surfaces of the first header 10 and the second header 20. The melted wax closes the gaps between the first header 10 and the second header 20 and the heat exchange tube 30. The heat exchanger 4 is cooled and the wax solidifies. Thereby, the first header 10, the second header 20, and the heat exchange tube 30 are fixed.

An outside air flow path along the Y direction is formed between the heat exchange tubes 30 that are vertically adjacent to each other. The heat exchanger 4 circulates outside air through an outside air flow path using a blower fan (not shown) or the like. The heat exchanger 4 exchanges heat between the outside air flowing through the outside air flow path and the refrigerant flowing through the refrigerant flow path 34 . Heat exchange takes place indirectly via heat exchange tubes 30.

When the refrigeration cycle device 1 shown in FIG. 1 performs cooling operation, 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.
As shown in FIG. 2, the refrigerant flows into the first header 10 from the first refrigerant port 51. The refrigerant flowing from the first refrigerant port 51 into the head flow path section 19 (see FIG. 3) of the third hole-like flow path 18C is distributed into the hole-like flow paths 17D, 16E and the hole-like flow paths 17E, 16F. It flows. The refrigerant that has flowed into the hole-like channels 17D and 16E is referred to as a "first refrigerant." The refrigerant that has flowed into the hole-like channels 17E and 16F is referred to as a "second refrigerant."

The first refrigerant flows in the -X direction through the heat exchange tube 30 (30G) from the hole-like channels 17D and 16E (see FIG. 3), and flows into the lower part of the third head channel section 26C of the second header 20. do. The first refrigerant flows from the upper part of the third head passage section 26C through the heat exchange tube 30 (30E) in the +X direction, passes through the hole-shaped passages 16D and 17C of the first header 10, and enters the second hole-shaped passage. 18B (first transition flow path) (see FIG. 3). The first refrigerant passes from the lower region 18B1 of the second hole-like flow path 18B, through the connection region 18B2 and the upper region 18B3, and reaches the hole-like flow paths 17B and 16C. The first refrigerant flows through the heat exchange tubes 30 (30D) in the -X direction from the hole-like channels 17B and 16C, and flows into the lower part of the second head channel section 26B of the second header 20. The first refrigerant flows from the upper part of the second head flow path section 26B through the heat exchange tube 30 (30B) in the +X direction, passes through the hole-like flow paths 16A, 17A, and 18A of the first header 10, and then the second refrigerant flows through the heat exchange tube 30 (30B) in the +X direction. Outflows through port 52.

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 (-Y direction side, the near side in FIG. 2) is 2. It is. The number of heat exchange tubes 30B and 30D arranged on the other side in the Y direction (+Y direction side, that is, on the back side in FIG. 2) is two. Therefore, the number of heat exchange tubes 30 on one side in the Y direction is the same as the number of heat exchange tubes 30 on the other side. Therefore, deviation in heat exchange efficiency in the Y direction can be suppressed.

The second refrigerant flows from the hole-like channels 17E and 16F (see FIG. 3) through the heat exchange tube 30 (30H) in the -X direction, and flows into the lower part of the fourth head channel section 26D of the second header 20. do. The second refrigerant flows from the upper part of the fourth head flow path section 26D through the heat exchange tube 30 (30F) in the +X direction, and enters the second hole-like flow path 16B (second transition 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 channel 16B through the connection region 16B2. The second refrigerant flows from the upper region 16B1 through the heat exchange tube 30 (30C) in the -X direction, and flows into the lower part of the first head passage section 26A of the second header 20. The second refrigerant flows from the upper part of the first head flow path section 26A through the heat exchange tube 30 (30A) in the +X direction, passes through the hole-shaped flow paths 16A, 17A, and 18A of the first header 10, and then flows into the second refrigerant. Outflows through port 52.

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 2. It is. The number of heat exchange tubes 30H and 30F arranged on the other side in the Y direction (+Y direction side, that is, on the back side in FIG. 2) is two. Therefore, the number of heat exchange tubes 30 on one side in the Y direction is the same as the number of heat exchange tubes 30 on the other side. Therefore, deviation in heat exchange efficiency in the Y direction can be suppressed.

The gaseous refrigerant radiates heat to the outside air and condenses while flowing through the heat exchange tube 30. The condensed refrigerant becomes a liquid refrigerant and flows out of the heat exchanger 4 from the second refrigerant port 52.
When the refrigeration cycle device 1 shown in FIG. 1 performs 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 second hole-like flow path 18B (first transition flow path) and the second hole-like flow path 16B (second transition flow path) are formed in the intermediate plates 13 to 15. There is. 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, it is possible to suppress the drift of the refrigerant in the Y direction and suppress the decrease in heat exchange efficiency.

In the heat exchanger 4 of the embodiment, the first header 10 is provided with a refrigerant port 51 having a refrigerant inlet and a refrigerant port 52 having a refrigerant outlet (see FIG. 2). Since the refrigerant ports 51 and 52 are both provided in the first header 10, the heat exchanger 4 can be made smaller compared to a case where the refrigerant ports are distributed and provided in two headers. Therefore, the heat exchanger 4 is excellent in terms of storability in the housing.

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, it is possible to reduce the size and weight. Therefore, the heat exchanger 4 is excellent in terms of storability in the housing.
As a comparative example, a heat exchanger without a header is assumed. This heat exchanger uses a meandering heat exchange tube in which straight portions and curved portions are alternately formed. When using a flat heat exchange tube, it is necessary to increase the radius of curvature of the curved portion to prevent buckling, making it difficult to miniaturize the heat exchanger. The radius of curvature can be reduced by using circular heat exchange tubes only in the curved portions. However, in that case, a mechanism for connecting the flat heat exchange tube and the cylindrical heat exchange tube is required, so miniaturization is not easy.

FIG. 7 is a cross-sectional view of the first header 10A of the first modification along the XZ plane. The same reference numerals are given to the configurations that have already been mentioned, and the description thereof will be omitted.
In the first header 10A, a first inner plate body 111 is used instead of the first inner plate body 11 (see FIG. 5). In the first header 10A, a first outer panel 112 is used instead of the first outer panel 12 (see FIG. 5).

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

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

The first inner plate body 111 and the first outer plate body 112 can be manufactured using a clad material (laminated plate material) on which a coating layer containing Zn is formed in advance. The coating layer can also be formed by thermal spraying.
As with the first header 10A, a plate having a coating layer can be used for the second header as well.

In this heat exchanger, since the plates 111 and 112 have the coating layers 114 and 116, the corrosion resistance of the first header 10A can be improved.

FIG. 8 is a cross-sectional view of the first header 10B of the second modification along the XZ plane. The same reference numerals are given to the configurations that have already been mentioned, and the description thereof will be omitted.
As shown in FIG. 8, the first header 10B is connected to other plates among the main surfaces of the first inner plate 11, the first to third intermediate plates 13 to 15, and the first outer plate 12. A low melting point layer 214 is provided on the main surface facing the.
For example, the plates 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 rate) of the low melting point layer 214 is higher than the Si content (content rate) of the plates 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 materials of the plates 11 to 15.

The plate having the low melting point layer 214 can be manufactured using a clad material (laminated plate material) on which a low melting point layer containing Si is formed in advance. The low melting point layer may be formed by laminating a clad sheet made of a low melting point material on the plate.
As for the second header, a plate having a low melting point layer can be used similarly to the first header 10B.

In this heat exchanger, the low melting point layer 214 functions as a solder that seals the gaps between the first header 10, the second header 20, and the heat exchange tube 30, so that the brazing work is facilitated.

FIG. 9 is an exploded perspective view of the first header 10C of the third modification. FIG. 10 is a cross-sectional view of the first header 10C of the third modification along the XZ plane. The same reference numerals are given to the configurations that have already been mentioned, and the description thereof will be omitted.
As shown in FIGS. 9 and 10, in the first header 10C, a convex portion 301 that protrudes into the hole-like flow path 18 is formed on the second intermediate plate body 14. The convex portion 301 may have a wall shape whose thickness decreases in the protruding direction. Note that the shape of the convex portion is not particularly limited, and may be prismatic, rectangular parallelepiped, hemispherical, or the like.

According to the first header 10C, the refrigerant that has flowed into the hole-like channel 18 through the first refrigerant port 51 is easily divided into two by the convex portion 301.
In the illustrated example, a convex portion is illustrated as a structure that promotes the division of the refrigerant, but the recessed portion formed in the second intermediate plate body 14 also has the effect of promoting the division of the refrigerant.

According to at least one embodiment described above, since the first transition flow path and the second transition flow path are formed in the intermediate plate of the header, uneven flow of the refrigerant in the first direction is suppressed, and heat exchange Efficiency can be increased.

Although several embodiments of the invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. These embodiments and their modifications are included within the scope and gist of the invention as well as within the scope of the invention described in the claims and its equivalents.

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 (intermediate plate)
14 Second intermediate plate (intermediate plate)
15 Third intermediate plate (intermediate plate)
16B Second hole-shaped channel (second transition channel)
18B Second hole-shaped channel (first transition channel)
113b Outer surface (second principal surface)
115b Outer surface (second principal 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 principal surface)
301 Convex part

Claims (8)

a plurality of heat exchange tubes each having a refrigerant flow path through which a refrigerant flows;
a header provided at an end of the heat exchange tube,
The plurality of heat exchange tubes include first and second upstream heat exchange tubes arranged in parallel in this order in the first direction, and first and second upstream heat exchange tubes arranged in parallel in this order in the first direction. a downstream heat exchange tube;
At least one header is provided between an inner plate body to which the heat exchange tube is connected, an outer plate body disposed facing the inner plate body, and the inner plate body and the outer plate body. and a plurality of intermediate plate bodies,
A first transition flow path is formed in the intermediate plate, which communicates the refrigerant flow path of the first upstream heat exchange tube with the refrigerant flow path of the second downstream heat exchange tube,
The first transition flow path has a first region that communicates with the refrigerant flow path of the first upstream heat exchange tube, and a second region that communicates with the refrigerant flow path of the second downstream heat exchange tube. a connection area connecting the first area and the second area;
Heat exchanger. The heat exchanger according to claim 1, wherein the refrigerant flowing into the first region and the refrigerant flowing out from the second region flow in opposite directions. A second transition flow path is formed in the intermediate plate, which communicates the refrigerant flow path of the second upstream heat exchange tube with the refrigerant flow path of the first downstream heat exchange tube.
The heat exchanger according to claim 1 or 2. In a plurality of heat exchange tubes having a refrigerant flow path communicating with the first transition flow path, a heat exchange tube disposed on one side in the first direction and a heat exchange tube disposed on the other side in the first direction. The same number of tubes,
In a plurality of heat exchange tubes having a refrigerant flow path communicating with the second transition flow path, a heat exchange tube disposed on one side in the first direction and a heat exchange tube disposed on the other side in the first direction. 4. The heat exchanger according to claim 3, wherein the number of tubes is the same. The heat treatment according to any one of claims 1 to 4, wherein the outer plate includes a coating layer containing Zn on a second main surface opposite to the first main surface facing the inner plate. exchanger. One of the headers provided at one end and the other end of the heat exchange tube has an inlet for introducing the refrigerant into the heat exchanger and an outlet for leading out the refrigerant from the heat exchanger. A heat exchanger according to any one of claims 1 to 5, wherein the heat exchanger is formed. The heat exchanger according to any one of claims 1 to 6, wherein the intermediate plate has a convex portion or a concave portion formed therein to promote branching of the refrigerant introduced into the heat exchanger. A refrigeration cycle device comprising the heat exchanger according to any one of claims 1 to 7.

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