JP7590519B2 - Heat exchanger and refrigeration cycle device - Google Patents

Description

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

A header-type heat exchanger has multiple heat exchange tubes and a header. A refrigerant flow path is formed inside the heat exchange tube. The header is provided at the end of the heat exchange tube. It is desirable for the heat exchanger to have high heat exchange efficiency.

International Publication No. 2015/037641

The problem that this invention aims to solve 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. The heat exchange tubes are formed with a refrigerant flow path through which a refrigerant flows. The header is 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 a first direction, first and second downstream heat exchange tubes arranged in parallel in this order in the first direction, and two third heat exchange tubes arranged in parallel in the first direction . At least one of the headers includes an inner plate body to which the heat exchange tubes are connected, an outer plate body arranged opposite to the inner plate body, and a plurality of intermediate plates provided between the inner plate body and the outer plate body. The intermediate plate body is formed with a first transition flow path that communicates the refrigerant flow path of the first upstream heat exchange tube with the refrigerant flow path of the second downstream heat exchange tube, and a third transition flow path that communicates the refrigerant flow paths of the two third heat exchange tubes . The first transition flow passage has a first region communicating with the refrigerant flow passage of the first upstream heat exchange tube, a second region communicating with the refrigerant flow passage of the second downstream heat exchange tube, and a connection region connecting the first region and the second region . A direction perpendicular to the first direction in a plane parallel to the intermediate plate is defined as a second direction, and the first region and the second region are positioned differently in the second direction.

The heat exchanger of the embodiment has a plurality of heat exchange tubes and a header. The plurality of heat exchange tubes are formed with a refrigerant flow path through which a refrigerant flows. 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 a first direction, and first and second downstream heat exchange tubes arranged in parallel in this order in the first direction. At least one of the headers includes an inner plate body to which the heat exchange tubes are connected, an outer plate body arranged opposite the inner plate body, and a plurality of intermediate plates provided between the inner plate body and the outer plate body. A first transition flow path and a second transition flow path are formed in the intermediate plate body. The first transition flow path connects 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 connects 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 flow paths and at least one of the second transition flow paths are formed in different intermediate plates among the plurality of intermediate plates.

1 is a schematic configuration diagram of a refrigeration cycle device according to an embodiment. FIG. 2 is a transparent perspective view of a heat exchanger according to the embodiment. FIG. 2 is an exploded perspective view of a heat exchanger according to an embodiment. FIG. FIG. FIG. FIG. 11 is a cross-sectional view of a first header according to a first modified example. FIG. 11 is a cross-sectional view of a first header according to a second modified example. FIG. 13 is an exploded perspective view of a first header according to a third modified example. FIG. 13 is a cross-sectional view of a first header according to a third modified example.

Hereinafter, a heat exchanger according to an embodiment will be described with reference to the drawings.
In the present application, the X direction, the Y direction, and the Z direction are defined as follows: The Z direction is the longitudinal direction (extension direction) of the first header and the second header. For example, the Z direction is the vertical direction, and the +Z direction is the upward direction. The X direction is the central axis direction (extension 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 the direction perpendicular to the X direction and the Z direction. It is preferable that the Y direction is the horizontal direction.

FIG. 1 is a schematic diagram of a refrigeration cycle device 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 components of the refrigeration cycle apparatus 1 are sequentially connected by piping 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 dashed arrows.

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

The four-way valve 3 reverses the flow direction of the refrigerant to switch between cooling and heating operation. During cooling operation, the refrigerant flows through the compressor 2, four-way valve 3, outdoor heat exchanger 4, expansion device 5, and indoor heat exchanger 6 in that order. At this time, the refrigeration cycle device 1 makes the outdoor heat exchanger 4 function as a condenser and the indoor heat exchanger 6 function as an evaporator to cool the room. During heating operation, the refrigerant flows through the compressor 2, four-way valve 3, indoor heat exchanger 6, expansion device 5, and outdoor heat exchanger 4 in that order. At this time, the refrigeration cycle device 1 makes the indoor heat exchanger 6 function as a condenser and the outdoor heat exchanger 4 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 condensing it through heat dissipation into the outside air.
The expansion device 5 reduces the pressure of the high-pressure liquid refrigerant sent from the condenser to convert it into a low-temperature, low-pressure two-phase gas-liquid refrigerant.
The evaporator absorbs heat from the outside air to vaporize the low-temperature, low-pressure gas-liquid two-phase refrigerant sent from the expansion device 5, thereby converting it into a low-pressure gas refrigerant.

In this way, in the refrigeration cycle device 1, the refrigerant, which is the working fluid, circulates while changing phase between gas refrigerant and liquid refrigerant. The refrigerant releases heat in the process of changing phase from gas refrigerant to liquid refrigerant, and absorbs heat in the process of changing phase from liquid refrigerant to gas refrigerant. The refrigeration cycle device 1 uses the heat release or absorption of the refrigerant to perform heating, cooling, defrosting, etc.

Figure 2 is a perspective view of a heat exchanger according to an embodiment. As shown in Figure 2, the heat exchanger 4 according to an 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. Below, an example will be described in which the heat exchanger 4 is used as the outdoor heat exchanger 4 of the refrigeration cycle device 1 (see Figure 1).

The heat exchanger 4 has 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 along the XZ plane.

As shown in Figure 3, the first header 10 is constructed by stacking a first inner plate body 11, a first intermediate plate body 13, a second intermediate plate body 14, a third intermediate plate body 15, and a first outer plate body 12 in this order.
The first inner plate 11, the first to third intermediate plates 13-15, and the first outer plate 12 are formed of a material having high thermal conductivity and low specific gravity, such as aluminum or an aluminum alloy. The first inner plate 11, the first to third intermediate plates 13-15, and the first outer plate 12 are generally parallel to the YZ plane. The first outer plate 12 is disposed opposite the surface (first main surface 11a) of the first inner plate 11 on the +X direction side. The first to third intermediate plates 13-15 are provided between the first inner plate 11 and the first outer plate 12.

The first main surface 11a of the first inner plate 11 is the main surface of the first inner plate 11 and is the surface facing the first outer plate 12. The second main surface 11b is the 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 portions 41 penetrate the first inner plate body 11 in the thickness direction. The insertion portions 41 are formed in the shape of slits parallel to the Y direction. Ends of the heat exchange tubes 30 are inserted into the insertion portions 41. In this way, the heat exchange tubes 30 are connected to the first inner plate body 11.

A plurality of hole-like flow paths 16 are formed in the first intermediate plate 13. The hole-like flow paths 16 penetrate the first intermediate plate 13 in the thickness direction. The plurality of hole-like flow paths 16 include a first hole-like flow path 16A to a sixth hole-like flow path 16F.
The first hole-like flow passage 16A has an elliptical shape when viewed from the X direction. The "elliptical shape" is a shape formed by two straight lines that are parallel and facing each other, and a curved convex shape (e.g., semicircular, elliptical arc, etc.) that connects the ends of the two straight lines. The first hole-like flow passage 16A is an elongated hole extending in the Y direction. The first hole-like flow passage 16A is located at the highest position among the first hole-like flow passages 16A to 16F (i.e., located furthest from the +Z direction side).

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

The lower region 16B3 is located lower than the third hole-like flow path 16C (i.e., 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 aligned with the fourth hole-like flow path 16D in the Y direction. The lower region 16B3 is located on the +Y direction side of the fourth hole-like flow path 16D. The lower region 16B3 is located lower than the upper region 16B1.
The connection region 16B2 connects the +Y direction end of the upper region 16B1 and the -Y direction end of the lower region 16B3. The connection region 16B2 is a long hole that extends at an angle downward in the +Y direction.

The third hole-like flow path 16C has an elliptical shape when viewed from the X direction. The third hole-like flow path 16C is a long hole extending in the Y direction. The third hole-like flow path 16C is located lower than the first hole-like flow path 16A (i.e., located on the -Z direction side of the first hole-like flow path 16A). The third hole-like flow path 16C is located in line with the upper region 16B1 in the Y direction. The third hole-like flow path 16C is located on the +Y direction side of the upper region 16B1.

The fourth hole-like flow passage 16D is located lower than the upper region 16B1 (i.e., located on the −Z direction side of the upper region 16B1). The fourth hole-like flow passage 16D has an elliptical shape when viewed from the X direction. The fourth hole-like flow passage 16D is an elongated hole extending in the Y direction.
The fifth hole-like flow passage 16E is located lower than the fourth hole-like flow passage 16D (i.e., located on the -Z direction side of the fourth hole-like flow passage 16D). The fifth hole-like flow passage 16E has an elliptical shape when viewed from the X direction. The fifth hole-like flow passage 16E is an elongated hole extending in the Y direction.
The sixth hole-like flow paths 16F are located lower than the lower region 16B3 (i.e., located on the -Z direction side of the lower region 16B3). The sixth hole-like flow paths 16F are aligned in the Y direction with the fifth hole-like flow paths 16E. The sixth hole-like flow paths 16F are located on the +Y direction side with respect to the fifth hole-like flow paths 16E. The fifth hole-like flow paths 16E and the sixth hole-like flow paths 16F are formed with an interval in the Y direction.

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

The third intermediate plate 15 has a plurality of hole-like flow paths 18 formed therein. The hole-like flow paths 18 penetrate the third intermediate plate 15 in the thickness direction. The hole-like flow paths 16 to 18 can be formed by punching a flat plate.

The plurality of hole-like flow paths 18 include a first hole-like flow path 18A to a third hole-like flow path 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 flow path 18B (first transition flow path) 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 (i.e., 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 higher than the lower region 18B1. The upper region 18B3 is located lower than the first hole-like flow path 18A (i.e., located on the -Z direction side of the first hole-like flow path 18A). The upper region 18B3 is an elongated 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 +Y direction end of the lower region 18B1 and the -Y direction end of the upper region 18B3. The connection region 18B2 is a long hole that extends at an angle so as to rise in the +Y direction.

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

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

As shown in FIG. 4, the first inner plate 11, the hole-like flow paths 16-18 of the intermediate plates 13-15, and the first outer plate 12 form a head flow path portion 19 (space).

The first outer plate body 12 is formed with insertion portions 42, 43. For example, the insertion portions 42, 43 are circular.
A tubular first refrigerant port 51 is inserted into the insertion portion 42. An end of the first refrigerant port 51 opens into the inside of the third hole-like flow passage 18C. This opening serves as an inlet for introducing the refrigerant into the heat exchanger 4 or an outlet for discharging 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 inside of the first hole-like flow passage 18A. This opening serves as an inlet for introducing the refrigerant into the heat exchanger 4 or an outlet for discharging 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 Figures 5 and 6, the second header 20 is configured by stacking a second inner plate 21, a second intermediate plate 23, and a second outer plate 22 in this order. The second inner plate 21, the second intermediate plate 23, and the second outer plate 22 are formed of a material with high thermal conductivity and low specific gravity, such as aluminum or an aluminum alloy. The second inner plate 21, the second intermediate plate 23, and the second outer plate 22 are generally parallel to the YZ plane. The second outer plate 22 is disposed opposite the surface (first main surface 21a) of the second inner plate 21 on the -X direction side. The second intermediate plate 23 is provided between the second inner plate 21 and the second outer plate 22.

The first main surface 21a is a main surface of the second inner plate body 21 and is a 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 portions 44 penetrate the second inner plate body 21 in the thickness direction. The insertion portions 44 are formed in the shape of slits parallel to the Y direction. Ends of the heat exchange tubes 30 are inserted into the insertion portions 44.

The second intermediate plate 23 has a plurality of hole-like flow paths 24 formed therein. The hole-like flow paths 24 penetrate the second intermediate plate 23 in the thickness direction.

The multiple hole-like flow paths 24 include a first hole-like flow path 24A to a fourth hole-like flow path 24D. The first hole-like flow path 24A to the fourth hole-like flow path 24D are rectangular 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 flow path 24D is located on the -Z direction side of the second hole-like flow path 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 passages 24 of the second intermediate plate 23, and the second outer plate 22 form a head flow passage portion 26 (space).
5, the head flow path section 26 defined by the first hole-like flow paths 24A is referred to as a first head flow path section 26A. The head flow path section 26 defined by the second hole-like flow paths 24B is referred to as a second head flow path section 26B. The head flow path section 26 defined by the third hole-like flow paths 24C is referred to as a third head flow path section 26C. The head flow path section 26 defined by the fourth hole-like flow paths 24D is referred to as a fourth head flow path section 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 formed of a material with high thermal conductivity and low specific gravity, such as aluminum or an aluminum alloy. The heat exchange tube 30 is formed in a flat tubular shape. That is, the dimension of the heat exchange tube 30 in the Y direction is larger than the dimension in the Z direction. The shape of the cross section (YZ cross section) of the heat exchange tube 30 perpendicular to the longitudinal direction is an ellipse. The 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 heat exchange tubes 30 are arranged in parallel with a gap in the Z direction. The +X-direction ends of the heat exchange tubes 30 are inserted into the insertion portions 41 formed in the first header 10 (see FIG. 4). As a result, the +X-direction ends of the refrigerant flow paths 34 of the heat exchange tubes 30 open into the head flow path portion 19 of the first header 10. Therefore, the head flow path portion 19 communicates with the refrigerant flow paths 34 of the heat exchange tubes 30.

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

For example, the multiple heat exchange tubes 30 form four heat exchange tube pairs 31. Each heat exchange tube pair 31 is formed 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 with a gap between them.

Of the four heat exchange tube pairs 31, the first heat exchange tube pair 31A from the top has 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 +Y direction in the order of the first downstream heat exchange tube 30C and the second downstream heat exchange tube 30D.

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 +Y direction in the order of the first upstream heat exchange tube 30E and the second upstream heat exchange tube 30F.

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

Heat exchange tubes 30A, 30C, 30E, and 30G are arranged on one side in the Y direction (-Y direction side, i.e., the front side in FIG. 2). Heat exchange tubes 30B, 30D, 30F, and 30H are arranged on the other side in the Y direction (+Y direction side, i.e., the back side in FIG. 2).

The first upstream heat exchange tube 30E is in communication with the second downstream heat exchange tube 30D via a second hole-like flow passage 18B (first transition flow passage) (see FIG. 3).
The second upstream heat exchange tube 30F is in communication with the first downstream heat exchange tube 30C via a second hole-like flow passage 16B (second transition flow passage) (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 brazing procedure is as follows. The inner surfaces of the first header 10 and the second header 20 are coated with wax. The heat exchange tubes 30 are inserted into the first header 10 and the second header 20 to assemble the heat exchanger 4. The assembled heat exchanger 4 is heated in a furnace. The wax on the inner surfaces of the first header 10 and the second header 20 melts due to the heating. The molten wax seals 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 wax solidifies. This fixes the first header 10 and the second header 20 to the heat exchange tubes 30.

Between adjacent heat exchange tubes 30 in the vertical direction, an outside air flow path is formed along the Y direction. The heat exchanger 4 circulates outside air through the outside air flow path by 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. The heat exchange is performed indirectly via the heat exchange tubes 30.

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 first header 10 from the first refrigerant port 51. The refrigerant that flows from the first refrigerant port 51 into the head flow passage portion 19 (see Fig. 3) of the third hole flow passage 18C is distributed and flows into the hole flow passages 17D, 16E and the hole flow passages 17E, 16F. The refrigerant that flows into the hole flow passages 17D, 16E is referred to as the "first refrigerant." The refrigerant that flows into the hole flow passages 17E, 16F is referred to as the "second refrigerant."

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

Of 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; near side in FIG. 2) is two. The number of heat exchange tubes 30B and 30D arranged on the other side in the Y direction (+Y direction side; i.e., far 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. This makes it possible to suppress bias in the heat exchange efficiency in the Y direction.

The second refrigerant flows from the hole-shaped flow paths 17E, 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 flow path section 26D of the second header 20. 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 flows into the second hole-shaped flow path 16B (second transition flow path) of the first header 10 (see FIG. 3). The second refrigerant passes through the lower region 16B3 of the second hole-shaped flow path 16B through the connection region 16B2 to the upper region 16B1. 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 flow path section 26A of the second header 20. The second refrigerant flows from the top of the first head flow passage section 26A through the heat exchange tube 30 (30A) in the +X direction, passes through the hole-like flow passages 16A, 17A, and 18A of the first header 10, and flows out through the second refrigerant port 52.

Of 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; near side in FIG. 2) is two. The number of heat exchange tubes 30H and 30F arranged on the other side in the Y direction (+Y direction side; i.e., far 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. This makes it possible to suppress bias in the heat exchange efficiency in the Y direction.

The gas refrigerant radiates heat to the outside air and condenses while flowing through the heat exchange tubes 30. The condensed refrigerant becomes a liquid refrigerant and flows out of the heat exchanger 4 from the second refrigerant port 52.
1 performs a heating operation, the refrigerant flows in the opposite direction to the above. That is, the liquid refrigerant flows into the first header 10 from the second refrigerant port 52, and the gas-liquid two-phase refrigerant flows out of the first refrigerant port 51.

In the heat exchanger 4 of the embodiment, the second hole-shaped flow passage 18B (first transition flow passage) and the second hole-shaped flow passage 16B (second transition flow passage) are formed in the intermediate plates 13 to 15. Therefore, the first refrigerant flows from the upstream heat exchange tube 30E on the -Y direction side to the downstream heat exchange tube 30D on the +Y direction side. The second refrigerant flows from the upstream heat exchange tube 30F on the +Y direction side to the downstream heat exchange tube 30C on the -Y direction side. This makes it possible to suppress refrigerant drift in the Y direction and suppress a decrease in heat exchange efficiency.

In the embodiment of the heat exchanger 4, a refrigerant port 51 having a refrigerant inlet and a refrigerant port 52 having a refrigerant outlet are provided in the first header 10 (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 than when the refrigerant ports are provided separately in two headers. Therefore, the heat exchanger 4 is excellent in terms of storability in a housing.

In the heat exchanger 4 of the embodiment, the first header 10 and the second header 20 are composed of the plates 11 to 14, so the structure of the headers can be simplified. This allows for miniaturization and weight reduction. Therefore, the heat exchanger 4 is excellent in terms of ease of storage in a housing.
As a comparative example, a heat exchanger without a header is assumed. This heat exchanger uses serpentine heat exchange tubes in which straight and curved sections are alternately formed. When flat heat exchange tubes are used, the radius of curvature must be large in the curved sections to prevent buckling, making it difficult to miniaturize the heat exchanger. If circular tubular heat exchange tubes are used only in the curved sections, the radius of curvature can be reduced. However, in that case, a mechanism is required to connect the flat heat exchange tubes and the circular tubular heat exchange tubes, making it difficult to miniaturize the heat exchanger.

7 is a cross-sectional view of the first header 10A of the first modified example taken along the XZ plane. The same reference numerals are used for the same components as those described above, 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 plate body 112 is used instead of the first outer plate body 12 (see FIG. 5).

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

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

The first inner plate 111 and the first outer plate 112 can be produced using a clad material (laminated plate material) on which a coating layer containing Zn has been formed in advance. The coating layer can also be formed by thermal spraying.
Similarly to the first header 10A, a plate having a coating layer can be used for the second header.

In this heat exchanger, the plates 111 and 112 have coating layers 114 and 116, which improves the corrosion resistance of the first header 10A.

8 is a cross-sectional view of the first header 10B of the second modified example taken along the XZ plane. The same reference numerals are used for the same components as those described above, and the description thereof will be omitted.
As shown in Figure 8, the first header 10B has a low melting point layer 214 provided on the main surfaces of the first inner plate body 11, the first to third intermediate plate bodies 13 to 15, and the first outer plate body 12 that face the other plate bodies.
For example, the plates 11-15 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) of the low melting point layer 214 is higher than the Si content (content) of the plates 11-15. 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 plates 11-15.

The plate having the low melting point layer 214 can be produced using a clad material (laminated plate material) on which a low melting point layer containing Si has been 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.
Similarly to the first header 10B, a plate having a low melting point layer can be used for the second header.

In this heat exchanger, the low melting point layer 214 functions as a solder that seals the gaps between the first header 10 and the second header 20 and the heat exchange tubes 30, making the brazing process easier.

Fig. 9 is an exploded perspective view of the first header 10C of the third modified example. Fig. 10 is a cross-sectional view of the first header 10C of the third modified example along the XZ plane. The same reference numerals are used for the already-mentioned configurations, and the description thereof will be omitted.
9 and 10, in the first header 10C, a convex portion 301 is formed on the second intermediate plate 14, which protrudes into the hole-like flow passage 18. The convex portion 301 may be a wall-like portion whose thickness decreases in the protruding direction. The shape of the convex portion is not particularly limited, and may be a prism, a rectangular parallelepiped, a hemisphere, or the like.

According to the first header 10C, the refrigerant that has flowed into the hole-like flow passages 18 through the first refrigerant port 51 is easily divided into two flows by the convex portion 301.
In the illustrated example, the convex portion is exemplified as a configuration for promoting the division of the refrigerant, but the concave portion formed in the second intermediate plate 14 also has the effect of promoting the division of the refrigerant.

According to at least one of the embodiments described above, the first and second transition flow paths are formed in the intermediate plate of the header, which suppresses refrigerant drift in the first direction and improves heat exchange efficiency.

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

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 (outer plate)
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-like flow path (second transition flow path)
18B Second hole-like flow path (first transition flow path)
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 a first direction, first and second downstream heat exchange tubes arranged in parallel in this order in the first direction, and two third heat exchange tubes arranged in parallel in the first direction ,
At least one of the headers includes an inner plate body to which the heat exchange tubes are connected, an outer plate body arranged opposite to the inner plate body, and a plurality of intermediate plates provided between the inner plate body and the outer plate body,
The intermediate plate is formed with a first transition passage that connects the refrigerant flow path of the first upstream heat exchange tube with the refrigerant flow path of the second downstream heat exchange tube, and a third transition passage that connects the refrigerant flow paths of the two third heat exchange tubes ,
The first transition flow passage has a first region communicating with a refrigerant flow passage of the first upstream heat exchange tube, a second region communicating with a refrigerant flow passage of the second downstream heat exchange tube, and a connection region connecting the first region and the second region ,
A direction perpendicular to the first direction in a plane parallel to the intermediate plate is defined as a second direction, and the first region and the second region are positioned differently in the second direction.
Heat exchanger. The heat exchanger of claim 1, wherein the refrigerant flowing into the first region and the refrigerant flowing out of the second region flow in opposite directions. A second transition flow passage is formed in the intermediate plate body, which connects the refrigerant flow passage of the second upstream heat exchange tube with the refrigerant flow passage of the first downstream heat exchange tube.
3. The heat exchanger according to claim 1 or 2. In the plurality of heat exchange tubes having a refrigerant flow path communicating with the first transition flow path, the number of heat exchange tubes arranged on one side in the first direction is equal to the number of heat exchange tubes arranged on the other side in the first direction,
4. The heat exchanger according to claim 3, wherein the number of heat exchange tubes arranged on one side of the first direction and the number of heat exchange tubes arranged on the other side of the first direction in the plurality of heat exchange tubes having a refrigerant flow path communicating with the second transition flow path are equal to each other. The heat exchanger according to any one of claims 1 to 4, wherein the outer plate body has a coating layer containing Zn on a second main surface opposite to a first main surface facing the inner plate body. The heat exchanger according to any one of claims 1 to 5, wherein one of the headers provided at one end and the other end of the heat exchange tube is provided with an inlet for introducing the refrigerant into the heat exchanger and an outlet for discharging the refrigerant from the heat exchanger. The heat exchanger according to any one of claims 1 to 6, wherein the intermediate plate body has a convex portion or a concave portion formed thereon to promote division of the refrigerant introduced into the heat exchanger. A refrigeration cycle device having a heat exchanger according to any one of claims 1 to 7.

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