KR20220041165A - Heat exchangers and refrigeration cycle units - Google Patents

Abstract

The heat exchanger of the embodiment has a plurality of heat exchange tubes and headers. In the plurality of heat exchange tubes, a refrigerant passage through which the refrigerant flows is formed. A header is installed at the end of the heat exchange tube. The plurality of heat exchange tubes includes first and second upstream heat exchange tubes disposed in parallel in this order in a first direction, and first and second downstream heat exchange tubes disposed in parallel in this order in the first direction. . At least one header includes an inner plate body to which the heat exchange tube is connected, an outer plate body disposed to face the inner plate body, and an intermediate plate body provided between the inner plate body and the outer plate body. A first transition passage and a second transition passage are formed in the intermediate plate body. The first transition passage connects the refrigerant passage of the first downstream heat exchange tube with the refrigerant passage of the second upstream heat exchange tube. The second transition passage connects the refrigerant passage of the second downstream heat exchange tube with the refrigerant passage of the first upstream heat exchange tube.

Description

Heat exchangers and refrigeration cycle units

An embodiment of the present invention relates to a heat exchanger and a refrigeration cycle device.

The header type heat exchanger has a plurality of heat exchange tubes and headers. A refrigerant passage is formed in the heat exchange tube. A header is installed at the end of the heat exchange tube. The heat exchanger is required to have high heat exchange efficiency.

Patent Document 1: International Publication No. 2015/037641

An object of the present invention is to provide a heat exchanger and a refrigerating cycle device capable of increasing heat exchange efficiency.

The heat exchanger of the embodiment has a plurality of heat exchange tubes and headers. In the plurality of heat exchange tubes, a refrigerant passage through which the refrigerant flows is formed. A header is installed at the end of the heat exchange tube. The plurality of heat exchange tubes includes first and second upstream heat exchange tubes disposed in parallel in this order in a first direction, and first and second downstream heat exchange tubes disposed in parallel in this order in the first direction. . At least one header includes an inner plate body to which the heat exchange tube is connected, an outer plate body disposed to face the inner plate body, and an intermediate plate body installed between the inner plate body and the outer plate body. A first transition passage and a second transition passage are formed in the intermediate plate body. The first transition passage connects the refrigerant passage of the first downstream heat exchange tube with the refrigerant passage of the second upstream heat exchange tube. The second transition passage connects the refrigerant passage of the second downstream heat exchange tube with the refrigerant passage of the first upstream heat exchange tube.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic block diagram of the refrigeration cycle apparatus in embodiment.
Fig. 2 is a perspective view through perspective of the heat exchanger in the embodiment.
It is an exploded perspective view of the heat exchanger in embodiment.
4 is a cross-sectional view of a first header;
5 is an exploded perspective view of a second header;
6 is a cross-sectional view of a second header;
Fig. 7 is a cross-sectional view of a first header of a first modification;
Fig. 8 is a cross-sectional view of a first header of a second modification;
Fig. 9 is an exploded perspective view of a first header of a third modification;
Fig. 10 is a cross-sectional view of a first header of a third modification;

EMBODIMENT OF THE INVENTION Hereinafter, the heat exchanger of embodiment is demonstrated with reference to drawings.

Herein, the X direction, the Y direction, and the Z direction are defined as follows. The Z direction is a longitudinal direction (extension 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 (extension 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. The Y direction is preferably a horizontal direction.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic block diagram of the refrigeration cycle apparatus of embodiment.

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). have The components of the refrigeration cycle device 1 are sequentially connected by a pipe 7 . In FIG. 1 , the circulation direction of the refrigerant (heat medium) during cooling operation is indicated by a solid arrow, and the circulation direction of the refrigerant (heating medium) during heating operation is indicated by a broken arrow.

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

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

The condenser heats the high-temperature/high-pressure gaseous refrigerant discharged from the compressor 2 to the outside air and condenses it to obtain a high-pressure liquid refrigerant.

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

The evaporator absorbs heat from the outside air and vaporizes the low-temperature, low-pressure gas-liquid two-phase refrigerant sent from the expansion device 5 to obtain a low-pressure gaseous refrigerant.

In this way, in the refrigeration cycle device 1, the refrigerant, which is a working fluid, circulates while changing a phase between the gaseous refrigerant and the liquid refrigerant. The refrigerant radiates heat during a phase change from a gaseous refrigerant to a liquid refrigerant, and absorbs heat during a phase change from a liquid refrigerant to a gaseous refrigerant. The refrigeration cycle device 1 performs heating, cooling, defrosting, and the like by using heat radiation or endothermic heat of a refrigerant.

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

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

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

3 , the first header 10 includes 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) is laminated in this order, and is comprised.

The first inner plate body 11 , the first to third intermediate plate bodies 13 to 15 , and the first outer plate body 12 are formed of a material having high thermal conductivity and low specific gravity, such as aluminum or an aluminum alloy. The first inner plate body 11 , the first to third intermediate plate bodies 13 to 15 , and the first outer plate body 12 are roughly parallel to the YZ plane. The 1st outer-plate body 12 is arrange|positioned opposingly to the surface (1st main surface 11a) of the +X direction side of the 1st inner-plate body 11 . The first to third intermediate plate bodies 13 to 15 are provided between the first inner plate body 11 and the first outer plate body 12 .

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

A plurality of insertion portions 41 are formed in the first inner plate body 11 . The insertion part 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. An end of the heat exchange tube 30 is inserted into the insertion part 41 . Accordingly, the heat exchange tube 30 is connected to the first inner plate body 11 .

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

The first hole-shaped flow path 16A has an elongated circular shape when viewed from the X direction. The "long circle shape" is a shape composed of two straight lines facing each other in parallel and a curve of a curved convex shape (eg, semicircle shape, elliptical arc shape, etc.) connecting the ends of the two straight lines respectively. The first hole-shaped flow path 16A is a long hole extending in the Y direction. The 1st hole-shaped flow path 16A is at the highest position among the 1st hole-shaped flow paths 16A - the 6th hole-shaped flow path 16F (that is, it is located most at 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 at a low position with respect to the first hole-shaped passage 16A (that is, it is located on the -Z direction side of the first hole-shaped passage 16A). The upper region 16B1 is a long hole extending in the Y direction.

The lower region 16B3 is at a low position with respect to the third hole-shaped passage 16C (that is, it is located on the -Z direction side of the third hole-shaped passage 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 positioned side by side with the fourth hole-shaped flow path 16D in the Y direction. The lower region 16B3 is located on the +Y direction side with respect to the fourth hole-shaped flow path 16D. The lower region 16B3 is 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 an elongated hole that slopes and extends so as to descend in the +Y direction.

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

The fourth hole-shaped flow path 16D is at a low position with respect to the upper region 16B1 (that is, it is located on the -Z direction side of the upper region 16B1). The fourth hole-shaped flow path 16D has an elongated circular shape when viewed from the X direction. The fourth hole-shaped flow path 16D is a long hole extending in the Y direction.

The fifth hole-shaped passage 16E is at a lower position with respect to the fourth hole-shaped passage 16D (that is, it is located on the -Z direction side of the fourth hole-shaped passage 16D). The fifth hole-shaped flow path 16E has an elongated circular shape when viewed from the X direction. The fifth hole-shaped flow path 16E is a long hole extending in the Y direction.

The sixth hole-shaped flow path 16F is at a low position with respect to the lower region 16B3 (that is, it is located on the -Z direction side of the lower region 16B3). The sixth hole-shaped flow path 16F is positioned side by side with the fifth hole-shaped flow path 16E in the Y direction. The 6th hole-shaped flow path 16F is located on the +Y direction side with respect to the 5th hole-shaped flow path 16E. The 5th hole-shaped flow path 16E and the 6th hole-shaped flow path 16F are formed at intervals in the Y direction.

A plurality of hole-shaped flow paths 17 are formed in the second intermediate plate body 14 . The hole-shaped flow path 17 penetrates the second intermediate plate body 14 in the thickness direction. The plurality of hole-shaped passages 17 include a first hole-shaped passage 17A to a fifth hole-shaped passage 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 in a position coincident with the first hole-shaped flow path 16A when viewed in 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 at a position coincident with the third hole-shaped flow path 16C when viewed in 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 at a position coincident with the fourth hole-shaped flow path 16D when viewed in 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 at a position coincident with the fifth hole-shaped flow path 16E when viewed in 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-shaped flow path 17E is at a position coincident with the sixth hole-shaped flow path 16F when viewed in the X direction. The fourth hole-shaped flow path 17D and the fifth concave portion 17E are formed at intervals in the Y direction.

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

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

The first hole-shaped flow path 18A has the same shape as the first hole-shaped flow path 17A. The first hole-shaped flow path 18A is in a position coincident with the first hole-shaped flow path 17A when viewed in the X direction. The second hole-shaped 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 at a low position with respect to the first hole-shaped passage 18A (that is, it is located on the -Z direction side of the first hole-shaped passage 18A). The lower region 18B1 is a long hole extending in the Y direction.

The upper region 18B3 is at a higher position than the lower region 18B1. The upper region 18B3 is at a low position with respect to the first hole-shaped flow path 18A (that is, it is located on the -Z direction side of the first hole-shaped flow path 18A). The upper region 18B3 is a long hole extending in the Y direction. The upper region 18B3 is located in the vicinity of the +Y direction compared to the lower region 18B1.

The connection region 18B2 connects an end of the lower region 18B1 in the +Y direction and an end of the upper region 18B3 in the -Y direction. The connection area 18B2 is a long hole that is inclined and extends so as to rise in the +Y direction.

The third hole-shaped flow path 18C has an elongated circular 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 at the lowest position among the first hole-shaped flow path 18A to the third hole-shaped flow path 18C (that is, it is located on the most -Z direction side). The third hole-shaped passage 18C has a length including the fourth hole-shaped passage 17D and the fifth concave portion 17E as a group when viewed in the X direction. The -Y-direction end of the 3rd hole-shaped flow path 18C coincides with the -Y direction end of the 4th hole-shaped flow path 17D when viewed in the X direction. The +Y-direction end of the 3rd hole-shaped flow path 18C coincides with the +Y-direction end of the 5th recessed part 17E when seen in the X direction.

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

As shown in FIG. 4 , the hole-shaped flow passages 16 to 18 of the first inner plate body 11 and the intermediate plate body 13 to 15 and the first outer plate body 12 form the head flow passage part 19 (space). to form

Insertion portions 42 and 43 are formed in the first outer plate body 12 . For example, the inserts 42 and 43 are circular in 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 introducing the refrigerant from the heat exchanger (4).

A tubular second refrigerant port 52 is inserted into the insertion portion 43 . The 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 introducing the refrigerant from the heat exchanger (4).

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

5 and 6 , the second header 20 is configured by stacking a second inner plate body 21 , a second intermediate plate body 23 , and a second outer plate body 22 in this order. . The second inner plate body 21 , the second intermediate plate body 23 , and the second outer plate body 22 are formed of a material having high thermal conductivity and low specific gravity, such as aluminum or an aluminum alloy. The second inner plate body 21 , the second intermediate plate body 23 , and the second outer plate body 22 are roughly parallel to the YZ plane. The second outer plate body 22 is disposed to face the surface (the first main surface 21a) on the -X direction side of the second inner plate body 21 . The second intermediate plate body 23 is provided between the second inner plate body 21 and the second outer plate body 22 .

The first main surface 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 opposite to the first main surface 21a.

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

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

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

As shown in FIG. 6 , the hole-shaped flow path 24 and the second outer plate body 22 of the second inner plate body 21 and the second intermediate plate body 23 form a head flow path part 26 (space). do.

As shown in FIG. 5 , the head flow path part 26 partitioned by the first hole-shaped flow path 24A is referred to as a first head flow path part 26A. The head flow path part 26 partitioned by the 2nd hole-shaped flow path 24B is called the 2nd head flow path part 26B. The head flow path part 26 partitioned by the 3rd hole-shaped flow path 24C is called 3rd head flow path part 26C. The head flow path part 26 partitioned by the 4th hole-shaped flow path 24D is called the 4th head flow path part 26D.

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

The heat exchange tube 30 is formed of a material having a high thermal conductivity, such as aluminum or an aluminum alloy, and a low specific gravity. The heat exchange tube 30 is formed in a flat tube shape. That is, the heat exchange tube 30 has a larger dimension in the Y direction than the dimension in the Z direction. The shape of the cross section (YZ cross section) orthogonal to the longitudinal direction of the heat exchange tube 30 is a long circular shape. The heat exchange tube 30 extends in the X direction. A refrigerant passage 34 (refer to FIG. 4 ) is formed inside the heat exchange tube 30 . The refrigerant passage 34 is formed over the entire length of the heat exchange tube 30 .

At least a portion of the plurality of heat exchange tubes 30 are disposed in parallel at intervals in the Z direction. The +X direction end of the heat exchange tube 30 is inserted into the insertion part 41 formed in the first header 10 (see FIG. 4 ). Accordingly, the +X direction end of the refrigerant passage 34 of the heat exchange tube 30 opens into the head passage portion 19 of the first header 10 . For this reason, the head flow path part 19 communicates with the refrigerant flow path 34 of the heat exchange tube 30 .

The -X direction end of the heat exchange tube 30 is inserted into the insertion part 44 formed in the second header 20 (refer to FIG. 6). Accordingly, the -X direction end of the refrigerant passage 34 of the heat exchange tube 30 opens into the head passage portion 26 of the second header 20 . For this reason, the head flow path part 26 communicates with the refrigerant flow path 34 of the heat exchange tube 30 .

For example, the plurality of heat exchange tubes 30 constitutes four heat exchange tube pairs 31 . One pair of heat exchange tubes 31 is composed of a pair of heat exchange tubes 30 and 30 arranged in parallel in the +Y direction. The four heat exchange tube pairs 31 are vertically spaced apart from each other.

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

The second pair of heat exchange tubes 31B from above includes a first downstream heat exchange tube 30C and a second downstream heat exchange tube 30D. The first downstream heat exchange tube 30C and the second downstream heat exchange tube 30D are arranged in 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 pair of heat exchange tubes 31C from above has 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 pair of heat exchange tubes 31C are arranged in the order of the first upstream heat exchange tube 30E and the second upstream heat exchange tube 30F toward the +Y direction.

The fourth heat exchange tube pair 31D from above 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 disposed on one side of the Y direction (-Y direction side, that is, the front side in FIG. 2 ). The heat exchange tubes 30B, 30D, 30F, and 30H are disposed on the other side of the Y direction (+Y direction side, that is, the inner side in FIG. 2 ).

The first upstream side heat exchange tube 30E communicates with the second downstream side heat exchange tube 30D by a second hole-shaped flow path 18B (first transition flow path) (refer to Fig. 3 ).

The second upstream side heat exchange tube 30F communicates with the first downstream side heat exchange tube 30C by a second hole-shaped flow path 16B (second transition flow path) (refer to FIG. 3 ).

A gap between the first header 10 and the second header 20 and the heat exchange tube 30 is sealed by soldering or the like. The specific sequence of soldering is as follows. Lead is applied to inner surfaces of the first header 10 and the second header 20 . The heat exchanger 4 is inserted into the first header 10 and the second header 20 to assemble the heat exchanger 4 . The assembled heat exchanger 4 is heated in the furnace. By heating, the lead inside the first header 10 and the second header 20 is melted. The molten lead closes the gap between the first header 10 and the second header 20 and the heat exchange tube 30 . The heat exchanger 4 is cooled to solidify the lead. Accordingly, the first header 10 and the second header 20 and the heat exchange tube 30 are fixed.

An external air flow path along the Y direction is formed between the heat exchange tubes 30 adjacent to each other up and down. The heat exchanger 4 circulates the outside air to the outside air flow path by a blowing fan (not shown) or the like. The heat exchanger 4 exchanges heat between the outdoor air flowing through the outdoor air flow path and the refrigerant flowing through the refrigerant flow path 34 . The heat exchange is performed indirectly through the heat exchange tube 30 .

When the refrigeration cycle device 1 shown in FIG. 1 performs a cooling operation, the outdoor heat exchanger 4 functions as a condenser. In this case, the gas refrigerant flowing out 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 portion 19 (refer to FIG. 3 ) of the third hole-shaped flow path 18C flows into the hole-shaped flow paths 17D and 16E and the hole-shaped flow paths 17E and 16F. distributed and flowed. The refrigerant flowing through the hole-shaped flow paths 17D and 16E is referred to as a “first refrigerant”. The refrigerant flowing into the hole-shaped flow paths 17E and 16F is referred to as a "second refrigerant".

The first refrigerant flows through the heat exchange tube 30 (30G) in the -X direction in the hole-shaped flow paths 17D and 16E (refer to FIG. 3 ), and flows to the lower part of the third head flow path part 26C of the second header 20 . influx The first refrigerant flows through the heat exchange tube 30 (30E) in the +X direction from the upper portion of the third head flow passage 26C, and passes through the hole-shaped flow passages 16D and 17C of the first header 10 to the second hole. It flows into the shape flow path 18B (the 1st transition flow path) (refer FIG. 3). The first refrigerant reaches the hole-shaped flow paths 17B and 16C from the lower region 18B1 of the second hole-shaped flow path 18B through the connection region 18B2 and the upper region 18B3. The first refrigerant flows from the hole-shaped flow paths 17B and 16C through the heat exchange tube 30 ( 30D) in the -X direction, and flows into the lower portion of the second head flow path part 26B of the second header 20 . The first refrigerant flows through the heat exchange tube 30 (30B) in the +X direction from the upper part of the second head flow path part 26B, passes through the hole-shaped flow paths 16A, 17A, and 18A of the first header 10, 2 flows out through the refrigerant 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 disposed on one side of the Y direction (-Y direction side, the front side in FIG. 2 ) is 2 . The number of heat exchange tubes 30B and 30D disposed on the other side of the Y direction (+Y direction side, that is, the inner side in FIG. 2 ) is two. Accordingly, the number of one side heat exchange tubes 30 and the other side heat exchange tubes 30 in the Y direction is the same. Therefore, the Y-direction bias of heat exchange efficiency can be suppressed.

The second refrigerant flows from the hole-shaped flow paths 17E and 16F (refer to FIG. 3 ) through the heat exchange tube 30 ( 30H) in the -X direction, and the lower portion of the fourth head flow path portion 26D of the second header 20 . flows into The second refrigerant flows through the heat exchange tube 30 (30F) in the +X direction from the upper part of the fourth head flow path part 26D, and the second hole-shaped flow path 16B of the first header 10 (second transition flow path) into (see FIG. 3). The second refrigerant reaches the upper region 16B1 from the lower region 16B3 of the second hole-shaped flow path 16B through the connection region 16B2. The second refrigerant flows from the upper region 16B1 through the heat exchange tube 30 ( 30C) in the -X direction, and flows into the lower portion of the first head passage portion 26A of the second header 20 . The second refrigerant flows through the heat exchange tube 30 (30A) in the +X direction from the upper part of the first head flow path part 26A, and passes through the hole-shaped flow paths 16A, 17A, 18A of the first header 10 to remove the second refrigerant. 2 flows out through the refrigerant 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 disposed on one side of the Y direction (-Y direction side, the front side in FIG. 2 ) is 2 . The number of heat exchange tubes 30H and 30F disposed on the other side of the Y direction (+Y direction side, that is, the inner side in FIG. 2 ) is two. Therefore, the number of one side heat exchange tubes 30 and the other side heat exchange tubes 30 in the Y direction is the same. Therefore, the Y-direction bias of heat exchange efficiency can be suppressed.

The gaseous refrigerant is condensed by radiating heat to the outside air in the process of circulating 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 a heating operation, the refrigerant flows in the opposite direction to the above. That is, the liquid refrigerant flows into the first header 10 from the second refrigerant port 52 , and the gas-liquid two-phase refrigerant flows out from the first refrigerant port 51 .

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

In the heat exchanger 4 of the embodiment, a refrigerant port 51 having a refrigerant inlet and a refrigerant port 52 having a refrigerant outlet are provided in the first header 10 (refer to FIG. 2 ). Since the refrigerant ports 51 and 52 are both installed in the first header 10, the heat exchanger 4 can be downsized compared to a case in which the refrigerant ports are distributed and installed in two headers. Accordingly, the heat exchanger 4 is excellent in terms of storage in the case.

In the heat exchanger 4 of embodiment, since the 1st header 10 and the 2nd header 20 are comprised from the board|plate materials 11-14, the structure of a header can be simplified. Therefore, miniaturization and weight reduction are possible. Accordingly, the heat exchanger 4 is excellent in terms of storage in the case.

As a comparative form, a heat exchanger without a header is assumed. This heat exchanger uses a heat exchange tube in a zigzag form in which a straight part and a curved part are alternately formed. When a flat heat exchange tube is used, it is necessary to increase the radius of curvature in the curved portion to prevent buckling, and it is difficult to reduce the size of the heat exchanger. The radius of curvature can be reduced by using the heat exchange tube in the shape of a circular tube only in the curved part. However, in that case, since a mechanism for connecting the flat heat exchange tube and the cylindrical heat exchange tube is required, downsizing is not easy.

7 is a cross-sectional view taken along the XZ plane of the first header 10A of the first modification. For the components already described, the same reference numerals are used and descriptions thereof are omitted.

As the first header 10A, the first inner plate body 111 is used instead of the first inner plate body 11 (see FIG. 5 ). In the first header 10A, the first outer plate body 112 is used instead of the first outer plate body 12 (refer to FIG. 5 ).

The first inner plate body 111 includes 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 (2nd main surface) of the plate body main part 113. The outer surface 113b is a surface opposite to the first main surface facing the first outer plate body 112 . The coating layer 114 is made of a metal material including Zn. For example, the coating layer 115 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 part 113 .

The first outer plate body 112 includes 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 (2nd main surface) of the plate body main part 115. The outer surface 115b is a surface opposite to the first main surface facing the first inner plate body 111 . The coating layer 116 is made of a metal material including Zn. For example, the coating layer 115 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 part 115 .

The first inner plate body 111 and the first outer plate body 112 may be manufactured using a clad material (laminated plate material) on which a coating layer containing Zn is previously formed. The coating layer can also be formed by thermal spraying.

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

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

8 is a cross-sectional view taken along the XZ plane of the first header 10B of the second modification. For the components already described, the same reference numerals are used and descriptions thereof are omitted.

As shown in FIG. 8 , the first header 10B is disposed on another plate among the main surfaces of the first inner plate body 11 , the first to third intermediate plate bodies 13 to 15 , and the first outer plate body 12 . A low-melting-point layer 214 is provided on the opposite main surface.

For example, the plate bodies 11-15 are comprised from the material (aluminum, aluminum alloy, etc.) containing aluminum. 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 material of the plate members 11 to 15 .

The plate material having the low melting point layer 214 can be manufactured using a clad material (laminated plate material) in which a low melting point layer containing Si is previously formed. You may form a low-melting-point layer by laminating|stacking the covering sheet comprised from a low-melting-point material on a plate body.

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

In this heat exchanger, the low-melting-point layer 214 functions as a solder that seals the gap between the first header 10 and the second header 20 and the heat exchange tube 30 , so that the soldering operation becomes easy.

9 is an exploded perspective view of the first header 10C of the third modification. 10 is a cross-sectional view taken along the XZ plane of the first header 10C of the third modification. The same reference numerals are used for the existing components, and descriptions thereof are omitted.

9 and 10 , in the first header 10C, a convex portion 301 protruding into the hole-shaped flow passage 18 is formed on the second intermediate plate body 14 . The convex portion 301 may have a wall shape that reduces the thickness in the protruding direction. In addition, the shape of the convex portion is not particularly limited, and may be a prismatic shape, a rectangular parallelepiped shape, a hemispherical shape, or the like.

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

Moreover, although the convex part is illustrated as a structure which accelerates|stimulates refrigerant flow in the example of illustration, the recessed part formed in the 2nd intermediate|middle plate body 14 also exhibits the effect of promoting refrigerant|coolant flow division.

According to at least one embodiment described above, since the first transition passage and the second transition passage are formed in the intermediate plate body of the header, it is possible to suppress the drift of the refrigerant in the first direction and increase the heat exchange efficiency.

Although various embodiments of the present invention have been described, these embodiments have been presented as examples and are not intended to limit the scope of the present invention. These embodiments can be implemented in other various forms, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. These embodiments and modifications thereof are included in the scope of the invention and the scope of equivalents thereof, as well as those included in the scope and gist of the invention.

1 refrigeration cycle unit
4 Outdoor heat exchanger (heat exchanger)
10 first header (header)
11,111 First inner plate body (inner plate body)
11a 1st main surface
12,112 The first outer plate body (outer plate body)
12a 1st main surface
13 1st intermediate plate body (middle plate body)
14 2nd intermediate plate body (intermediate plate body)
15 3rd intermediate plate body (intermediate plate body)
16B 2nd hole-shaped flow path (second transition flow path)
18B 2nd hole-shaped flow path (first transition flow path)
113b outer surface (2nd main surface)
115b outer surface (second main surface)
30 heat exchange tube
30C first downstream heat exchange tube
30D second downstream heat exchange tube
30E first upstream heat exchange tube
30F second upstream heat exchange tube
34 Refrigerant Euro
113b outer surface (second main surface)
114, 116 coating layer
115b outer surface (second main surface)
301 convex

Claims (6)

A plurality of heat exchange tubes having a refrigerant flow path through which the refrigerant flows;
and a header installed at an end of the heat exchange tube,
The plurality of heat exchange tubes includes 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. and
At least one header includes an inner plate body to which the heat exchange tube is connected, an outer plate body disposed to face the inner plate body, and an intermediate plate body provided between the inner plate body and the outer plate body,
A first transition flow path for communicating the refrigerant flow path of the first downstream side heat exchange tube with the refrigerant flow path of the second upstream side heat exchange tube in the intermediate plate body, and a refrigerant flow path of the second downstream side heat exchange tube to the first upstream side A heat exchanger having a second transition passage communicating with the refrigerant passage of the heat exchange tube. According to claim 1,
The number of heat exchange tubes disposed on one side in the first direction and the heat exchange tubes disposed on the other side of the first direction in the plurality of heat exchange tubes having a refrigerant flow passage communicating with the first transition flow passage is the same;
The number of heat exchange tubes disposed on one side in the first direction in a plurality of heat exchange tubes having a refrigerant flow path communicating with the second transition flow path and the number of heat exchange tubes disposed on the other side in the first direction is the same as the number of heat exchangers. . 3. The method of claim 1 or 2,
The heat exchanger, wherein the outer plate body is provided with a coating layer containing Zn on a second main surface opposite to the first main surface opposite to the inner plate body. 4. The method according to any one of claims 1 to 3,
An inlet for introducing the refrigerant into the heat exchanger and an outlet for taking out the refrigerant from the heat exchanger are formed in one of the heads installed at one end and the other end of the heat exchanger tube. 5. The method according to any one of claims 1 to 4,
A heat exchanger, wherein a convex portion or a concave portion is formed in the intermediate plate body for accelerating the flow of the refrigerant introduced into the heat exchanger. The refrigeration cycle apparatus which has the heat exchanger in any one of Claims 1-5.

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