WO2024023958A1

WO2024023958A1 - Heat exchanger, and refrigeration cycle device

Info

Publication number: WO2024023958A1
Application number: PCT/JP2022/028884
Authority: WO
Inventors: 悟梁池
Original assignee: 三菱電機株式会社
Priority date: 2022-07-27
Filing date: 2022-07-27
Publication date: 2024-02-01

Abstract

This heat exchanger comprises a first heat exchanging unit, a second heat exchanging unit, and a stacked-type header which connects the first heat exchanging unit and the second heat exchanging unit and which allows a refrigerant to flow between the first heat exchanging unit and the second heat exchanging unit, wherein: the first heat exchanging unit includes a liquid header and first heat transfer pipes; the second heat exchanging unit includes a gas header and second heat transfer pipes; the stacked-type header includes a heat-transfer-pipe-side plate, an end portion plate, a first plate and a second plate; the first plate and the second plate form a flow passage that allows the refrigerant to flow between the first heat transfer pipes and the second heat transfer pipes; the first plate includes a first opening portion forming a portion of the flow passage, a second opening portion forming a portion of the flow passage, and an interfering portion provided between the first opening portion and the second opening portion; and the second plate includes a first communicating hole which forms a portion of the flow passage and which is disposed overlapping the first opening portion, the second opening portion and the interfering portion.

Description

Heat exchanger and refrigeration cycle equipment

The present disclosure relates to a heat exchanger and a refrigeration cycle device including a stacked header.

For example, Patent Document 1 includes a plurality of heat exchange sections having a plurality of heat exchanger tubes provided in a plurality of stages in a direction perpendicular to the air flow direction, and one end side of each of the plurality of heat exchange sections is A heat exchanger connected with one header is disclosed. In Patent Document 1, the refrigerant flowing through the heat exchanger tubes of one heat exchange section flows into a header, and from the header flows into the heat exchanger tubes of another heat exchange section.

International Publication No. 2015/025702

In the heat exchanger described in Patent Document 1, the refrigerant that enters a gas-liquid two-phase state in one heat exchange section and flows into the header is divided into a liquid-rich refrigerant with a high liquid phase ratio and a gas-rich refrigerant with a high gas phase ratio. No consideration was given to sufficient separation. Here, the heat exchange efficiency in other heat exchange parts located downstream of the flow of refrigerant with respect to one heat exchange part differs depending on whether the refrigerant is in a liquid state or a gas state. Therefore, in other heat exchange parts into which refrigerant that has not been separated into liquid-rich refrigerant and gas-rich refrigerant flows, heat exchange between air and refrigerant cannot be performed efficiently, and the heat transfer performance of the heat exchanger deteriorates. There was a problem with not being able to improve.

The present disclosure was made against the background of the above-mentioned problems, and by separating the refrigerant into a liquid-rich refrigerant and a gas-rich refrigerant using a laminated header, it is possible to efficiently exchange heat between air and refrigerant. The purpose of the present invention is to provide a heat exchanger and a refrigeration cycle device that can improve heat transfer performance.

The heat exchanger according to the present disclosure includes a first heat exchange section, a second heat exchange section disposed in parallel with the first heat exchange section in a first direction that is a direction in which air flows, and a second heat exchange section disposed in parallel with the first heat exchange section; A laminated header that connects the first heat exchange part and the second heat exchange part and allows a refrigerant to flow between the first heat exchange part and the second heat exchange part, the first heat exchange part having a laminated type header. a liquid header disposed at a distance from the mold header; and a liquid header extending along a second direction that is directed from the liquid header to the laminated header and intersecting the first direction, the first end being connected to the liquid header. and a first heat exchanger tube having a second end connected to the laminated header, the second heat exchanger having a gas header spaced apart from the laminated header, and a gas header extending along the second direction. , a second heat exchanger tube having a first end connected to the gas header and a second end connected to the laminated header, the laminated header having a heat exchanger tube through which the first heat exchanger tube and the second heat exchanger tube penetrate. a side plate; an end plate forming an end of the laminated header in the second direction; a first plate disposed between the heat exchanger tube side plate and the end plate; a second plate disposed either between the first plate and the end plate, and the first plate and the second plate are arranged between the first heat exchanger tube and the second heat exchanger tube. The first plate has a first opening that penetrates the first plate in the second direction and forms a part of the flow path, and a first plate that is wider than the first opening. a second opening located on the upstream side of the air flow and penetrating the first plate in the second direction to form a part of the flow path; and a second opening provided between the first opening and the second opening. the second plate passes through the second plate in the second direction, and is arranged to overlap the first opening, the second opening, and the obstruction to form a part of the flow path. It has a first communicating hole.

The heat exchanger according to the present disclosure includes a first heat exchange section, a second heat exchange section disposed in parallel with the first heat exchange section in a first direction that is a direction in which air flows, and a second heat exchange section disposed in parallel with the first heat exchange section; A laminated header that connects the first heat exchange part and the second heat exchange part and allows a refrigerant to flow between the first heat exchange part and the second heat exchange part, the first heat exchange part having a laminated type header. a liquid header disposed at a distance from the mold header; and a liquid header extending along a second direction that is directed from the liquid header to the laminated header and intersecting the first direction, the first end being connected to the liquid header. and a first heat exchanger tube having a second end connected to the laminated header, the second heat exchanger having a gas header spaced apart from the laminated header, and a gas header extending along the second direction. , a second heat exchanger tube having a first end connected to the gas header and a second end connected to the laminated header, the laminated header having a heat exchanger tube through which the first heat exchanger tube and the second heat exchanger tube penetrate. a side plate, an end plate forming an end of the laminated header in the second direction, and a first plate disposed between the heat exchanger tube side plate and the end plate; The end plate forms a flow path for circulating a refrigerant between the first heat exchanger tube and the second heat exchanger tube, and the first plate penetrates the first plate in the second direction to form a part of the flow path. a first opening that forms a flow path; a second opening that is located upstream of the first opening in the air flow, penetrates the first plate in the second direction, and forms a part of the flow path; an obstruction provided between the first opening and the second opening; the end plate is recessed in the second direction; the end plate is recessed in the second direction; It has a recessed part that is placed overlapping the part and forms part of the flow path.

A refrigeration cycle device according to the present disclosure includes a compressor that compresses a refrigerant, a radiator that radiates heat from the refrigerant flowing out from the compressor, an expansion mechanism that reduces the pressure of the refrigerant that flows out from the radiator, and a radiator that reduces the pressure of the refrigerant that flows out from the expansion mechanism. It includes an evaporator for evaporating air and a blower for sending air to the evaporator, and the evaporator is the heat exchanger described above.

According to the present disclosure, heat exchange between air and the refrigerant can be efficiently performed by separating the refrigerant into a liquid-rich refrigerant and a gas-rich refrigerant using the laminated header. Therefore, the heat transfer performance of the heat exchanger can be improved.

1 is a schematic configuration diagram of a refrigeration cycle device 100 according to Embodiment 1. FIG. 1 is a plan view of a heat exchanger 1 according to Embodiment 1. FIG. FIG. 2 is a schematic cross-sectional view of the first heat exchange section 10 and the second heat exchange section 20 of the heat exchanger 1 according to the first embodiment. FIG. 3 is a diagram illustrating the configuration of a stacked header 3 according to the first embodiment. FIG. 3 is a developed view of the laminated header 3 according to the first embodiment. FIG. 3 is a schematic exploded perspective view of the laminated header 3 according to the first embodiment. FIG. 3 is a diagram illustrating the configuration of a stacked header 3A according to a first modification of the first embodiment. FIG. 7 is a diagram illustrating the configuration of a laminated header 3B according to a second modification of the first embodiment. FIG. 7 is a diagram illustrating the configuration of a stacked header 3C according to a third modification of the first embodiment. FIG. 3 is a diagram illustrating the configuration of a stacked header 3D according to a second embodiment. FIG. 3 is a developed view of a stacked header 3D according to a second embodiment. FIG. 7 is a diagram illustrating the configuration of a stacked header 3E according to a first modification of the second embodiment. FIG. 7 is a developed view of a stacked header 3E according to a second modification of the second embodiment. FIG. 7 is a diagram illustrating the configuration of a stacked header 3F according to a second modification of the second embodiment. FIG. 7 is a diagram illustrating the configuration of a laminated header 3G according to a third modification of the second embodiment. FIG. 3 is a plan view of a heat exchanger 1 according to a third embodiment. FIG. 3 is a schematic cross-sectional view of a first heat exchange section 10 and a second heat exchange section 20 of a heat exchanger 1 according to a third embodiment. FIG. 7 is a diagram illustrating the configuration of a stacked header 3D according to Embodiment 3. FIG. 7 is a diagram illustrating the configuration of a laminated header 3H according to Modification 1 of Embodiment 3. FIG. 7 is a diagram illustrating the configuration of a stacked header 3I according to a second modification of the third embodiment. FIG. 7 is a diagram illustrating the configuration of a stacked header 3J according to a third modification of the third embodiment.

Hereinafter, a heat exchanger and a refrigeration cycle device according to the present disclosure will be described with reference to the drawings. The present disclosure is not limited to the following embodiments and modifications thereof, and can be variously modified without departing from the gist of the present disclosure. Further, the present disclosure includes all combinations of configurations that can be combined among the configurations shown in each embodiment and each modification example below. Furthermore, the refrigeration cycle device shown in the drawings is an example of equipment to which the refrigeration cycle device of the present disclosure is applied, and the refrigeration cycle device shown in the drawings is not intended to limit the equipment to which the present disclosure is applied. . In addition, in the following explanation, terms indicating directions (for example, "upper", "lower", "right", "left", "front", "rear", etc.) are used as appropriate to facilitate understanding. These are for illustrative purposes only and are not intended to limit this disclosure. Furthermore, in each figure, the same reference numerals are the same or equivalent, and this is common throughout the entire specification. Note that in each drawing, the relative dimensional relationship or shape of each component may differ from the actual one. Furthermore, in the following explanation, the height of temperature and pressure, etc. is not determined in relation to absolute values, but is determined relatively depending on the state or operation of the system or device, etc. do.

Embodiment 1.
(Configuration of refrigeration cycle device)
FIG. 1 is a schematic configuration diagram of a refrigeration cycle device 100 according to the first embodiment. As shown in FIG. 1, the refrigeration cycle device 100 of this embodiment includes a compressor 101, a radiator 102, an expansion mechanism 103, an evaporator 104, a blower 106, and a blower 107. Compressor 101, radiator 102, expansion mechanism 103, and evaporator 104 are connected by refrigerant piping 105, thereby forming a refrigerant circuit in which refrigerant circulates.

The compressor 101 is a fluid machine that sucks in low-pressure gas refrigerant, compresses it, and discharges it as high-pressure gas refrigerant. The compressor 101 is, for example, an inverter-driven compressor whose operating frequency can be adjusted.

The radiator 102 exchanges heat between the refrigerant flowing inside the heat transfer tube and another fluid, and condenses and liquefies the refrigerant. The blower 106 supplies air as a heat exchange fluid to the radiator 102 .

The expansion mechanism 103 is, for example, an electronic expansion valve whose opening degree can be controlled. The expansion mechanism 103 reduces the pressure of the refrigerant flowing out from the radiator 102 and expands it. Note that the expansion mechanism 103 may be a temperature-sensitive expansion valve, or a capillary tube may be provided instead of the expansion mechanism 103.

The evaporator 104 exchanges heat between the refrigerant flowing inside the heat transfer tube and another fluid, and evaporates and gasifies the refrigerant. The blower 107 supplies air as a heat exchange fluid to the evaporator 104 .

(Operation of refrigeration cycle equipment)
The operation of the refrigeration cycle device 100 of this embodiment will be explained based on the flow of refrigerant circulating in the refrigerant circuit. When the refrigeration cycle apparatus 100 is instructed to start operating, the compressor 101 compresses the refrigerant, converts it into a high-temperature, high-pressure gas state, and discharges the refrigerant. The gas refrigerant discharged by the compressor 101 flows into the radiator 102 through the refrigerant pipe 105. In the radiator 102, the refrigerant exchanges heat with other fluids and is condensed and liquefied. At this time, the refrigerant radiates heat to the other fluid, thereby heating the other fluid.

The refrigerant condensed and liquefied in the radiator 102 passes through the expansion mechanism 103. The expansion mechanism 103 reduces the pressure of the refrigerant. The refrigerant whose pressure has been reduced by the expansion mechanism 103 flows into the evaporator 104 . In the evaporator 104, the refrigerant exchanges heat with other fluids and evaporates into gas. At this time, the other fluid is cooled by the refrigerant absorbing heat from the other fluid. The refrigerant evaporated and gasified in the evaporator 104 is sucked into the compressor 101 again.

The refrigeration cycle device 100 is, for example, an air conditioner that heats or cools a room, a refrigeration device that cools a freezer compartment such as a warehouse, a showcase, or a refrigerator, or a water heater that heats water in a tank.

The heat exchanger 1 described later is employed as either or both of the radiator 102 and the evaporator 104. In each embodiment and each modification shown in this disclosure, a case will be described in which the heat exchanger 1 is employed as the evaporator 104.

(Configuration of heat exchanger 1)
FIG. 2 is a plan view of the heat exchanger 1 according to the first embodiment. FIG. 3 is a schematic cross-sectional view of the first heat exchange section 10 and the second heat exchange section 20 of the heat exchanger 1 according to the first embodiment.

Here, directions used for explanation in this embodiment, subsequent embodiments, and each modification will be defined. The first direction X is the direction in which air flows. In FIG. 2, the first direction X is the direction from the bottom to the top of the page. The second direction Y is a direction orthogonal to the first direction X, and is a direction in which the first heat exchanger tube 11 and the second heat exchanger tube 21 head from the liquid header 12 and the gas header 22 toward the laminated header 3. In FIG. 2, the direction from left to right in the paper is the second direction Y. The third direction Z is a direction perpendicular to the first direction X and the second direction Y, and in this embodiment is the direction of gravity. In FIG. 2, the third direction Z is the direction from the front to the back of the page. In the drawings, the forward directions of the first direction X, the second direction Y, and the third direction Z are indicated by the directions pointed by the arrows. In addition, in the following description, the forward directions of the first direction X, the second direction Y, and the third direction Z are simply referred to as the first direction X, the second direction Y, and the third direction Z. Further, the opposite directions are respectively referred to as a first reverse direction, a second reverse direction, and a third reverse direction.

FIG. 3 shows cross sections of the first heat exchange section 10 and the second heat exchange section 20 along the second direction Y and the third direction Z, arranged one above the other. In addition, in FIG. 2 and the subsequent drawings, the flow of refrigerant is shown by solid line arrows, and the flow of air is shown by broken line arrows.

The heat exchanger 1 includes a first heat exchange section 10, a second heat exchange section 20, and a laminated header 3. The first heat exchange section 10 includes a plurality of first heat exchanger tubes 11 and a liquid header 12. The second heat exchange section 20 includes a plurality of second heat exchanger tubes 21 and a gas header 22. Each of the first heat exchanger tubes 11 has a first end 11a and a second end 11b. The first end 11a is connected to the liquid header 12, and the second end 11b is connected to the laminated header 3. Each of the second heat exchanger tubes 21 has a first end 21a and a second end 21b. The first end 21a is connected to the gas header 22, and the second end 21b is connected to the laminated header 3. The laminated header 3 connects the first heat exchange section 10 and the second heat exchange section 20. The refrigerant passes through the laminated header 3 and flows between the first heat exchange section 10 and the second heat exchange section 20. 2 and 3, the laminated header 3 is illustrated for the purpose of showing the position of the laminated header 3, and the structure of the laminated header 3 will be explained from FIG. 4 onwards.

In the present embodiment, the second heat exchange section 20 is arranged upstream of the first heat exchange section 10 in the first direction X in which the air flows. Air is sent to the heat exchanger 1 from the blower 107 (see FIG. 1). As shown in FIGS. 2 and 3, the first heat exchanger tube 11 and the second heat exchanger tube 21 extend in the second direction Y. The first heat exchanger tube 11 and the second heat exchanger tube 21 are, for example, flat tubes. When the first heat exchanger tube 11 and the second heat exchanger tube 21 are flat tubes, there are no particular limitations on the processing method and shape of the flat tubes. The flat tube may be formed by bending one or more plates multiple times. Alternatively, it may be a flat multi-hole tube in which a plurality of channels are formed by partition walls inside the flat tube. When the flat tube is a multi-hole tube, the refrigerant branches into a plurality of channels formed inside the flat tube and flows in the second direction Y or in the opposite direction to the second direction. Further, when the first heat exchanger tube 11 and the second heat exchanger tube 21 are flat tubes, the flat surfaces of the first heat exchanger tubes 11 located adjacent to each other in the third direction Z are parallel to each other and are arranged in opposite directions, The flat surfaces of the second heat exchanger tubes 21 located adjacent to each other in the third direction Z are parallel to each other and are arranged in opposite directions. Note that the first heat exchanger tube 11 and the second heat exchanger tube 21 are not limited to flat tubes, but may be circular tubes.

Each of the first heat exchange section 10 and the second heat exchange section 20 has a plurality of plate-shaped fins 2. The first heat exchanger tube 11 passes through a plurality of plate-shaped fins 2 that the first heat exchanger 10 has. The second heat exchanger tube 21 passes through the plurality of plate-shaped fins 2 that the second heat exchange section 20 has. The plurality of fins 2 are provided at intervals between the liquid header 12 and the laminated header 3 and between the gas header 22 and the laminated header 3 so that the flat plate surfaces are along the first direction X and the third direction Z. It is being Note that instead of the configuration in which the first heat exchange section 10 and the second heat exchange section 20 each have a plurality of fins 2, the first heat exchange section 10 and the second heat exchange section 20 may have a configuration in which they share a fin. good. Specifically, a plurality of fins 2 thermally connected to both the first heat exchanger tube 11 and the second heat exchanger tube 21 are provided. For example, when plate-shaped fins 2 are employed, the first heat exchanger tube 11 and the second heat exchanger tube 21 can be configured to penetrate the flat plate surface of the fin 2 along the first direction X.

In this embodiment, the refrigerant flows through the first heat exchange section 10, then flows through the second heat exchange section 20, and flows out from the heat exchanger 1. More specifically, the refrigerant flows from the liquid header 12 into the plurality of first heat exchanger tubes 11 , passes through the plurality of first heat exchanger tubes 11 , and flows into the laminated header 3 . The refrigerant that has flowed into the laminated header 3 flows in the opposite direction to the first direction, and then flows into the plurality of second heat exchanger tubes 21 . The refrigerant that has flowed into the plurality of second heat exchanger tubes 21 passes through the gas header 22 and flows out from the second heat exchange section 20 . Since the first heat exchange section 10 is arranged downstream of the second heat exchange section 20 in the flow of air, the refrigerant flowing from the liquid header 12 toward the laminated header 3 flows from the laminated header 3 to the gas header 22. The air flows downstream of the refrigerant flowing towards it. The flow of refrigerant in the laminated header 3 will be described later.

Next, the structure of the laminated header 3 will be explained with reference to FIGS. 4 to 6. FIG. 4 is a diagram illustrating the configuration of the laminated header 3 according to the first embodiment. FIG. 4 shows a cross section of the first heat exchange section 10, the second heat exchange section 20, and the laminated header 3 taken along the line AA shown in FIG. In FIG. 4, the flow path 360 of the laminated header 3 is shown in a dotted pattern for easy visual recognition, and the hatching of each plate constituting the laminated header 3 is omitted. FIG. 5 is a developed view of the laminated header 3 according to the first embodiment. FIG. 6 is a schematic exploded perspective view of the laminated header 3 according to the first embodiment. In addition, in the subsequent diagrams explaining the configuration of each laminated header, the first heat exchange part 10, the second heat exchange part 20, and the position of each laminated header at a position corresponding to line AA of each laminated header are shown. A cross section is shown. In addition, in the subsequent diagrams explaining the configuration of each laminated header, the flow path 360 of each laminated header is shown in a dot pattern to make it easier to see, and the hatching of each plate constituting the laminated header is omitted. .

The laminated header 3 in this embodiment includes a heat exchanger tube side plate 31, a first plate 33, a second plate 34, and an end plate 32. The heat exchanger tube side plate 31 constitutes the end portion of the laminated header 3 on the heat exchanger tube side. The end plate 32 constitutes the end of the laminated header 3 on the second direction side. A first plate 33 and a second plate 34 are provided between the heat exchanger tube side plate 31 and the end plate 32. Each plate of the laminated header 3 makes surface contact with an adjacent plate. In this embodiment, the heat exchanger tube side plate 31, the first plate 33, the second plate 34, and the end plate 32 are arranged along the second direction Y.

As shown in FIG. 4, the first heat exchanger tube 11 and the second heat exchanger tube 21 penetrate the heat exchanger tube side plate 31. In FIG. 4, the interior of the first heat exchanger tube 11 and the second heat exchanger tube 21 is divided by broken lines into an upwind area UWA, which is the upstream side of the air flow, and a leeward area DWA, which is the downstream side of the air flow. It shows. Note that, in the following description, the upstream side of the air flow may be referred to as the windward side, and the downstream side of the air flow may be referred to as the leeward side.

As shown in FIGS. 5 and 6, the heat exchanger tube side plate 31 has a plurality of heat exchanger tube insertion ports 31a and a plurality of heat exchanger tube insertion ports 31b. The plurality of heat exchanger tube insertion ports 31a are provided along the third direction Z at intervals from each other. The plurality of heat exchanger tube insertion ports 31b are provided along the third direction Z at intervals from each other. Each of the plurality of heat exchanger tube insertion ports 31a and the plurality of heat exchanger tube insertion ports 31b penetrates the heat exchanger tube side plate 31 in the second direction Y. A heat exchanger tube arranged on the upstream side of the air flow is inserted into the heat exchanger tube insertion port 31b, and a heat exchanger tube arranged on the downstream side of the air flow is inserted into the heat exchanger tube insertion port 31a. In this embodiment, one second heat exchanger tube 21 is inserted into one heat exchanger tube insertion port 31b, and one first heat exchanger tube 11 is inserted into one heat exchanger tube insertion port 31a.

The first plate 33 has a plurality of first openings 331 and a plurality of second openings 332. The plurality of first openings 331 are provided at intervals along the third direction Z. The plurality of second openings 332 are provided at intervals along the third direction Z. Each of the plurality of first openings and the plurality of second openings 332 penetrates the first plate 33 in the second direction Y. The second end of the heat exchanger tube disposed on the upstream side of the air flow is inserted into the second opening 332, and the second end of the heat exchanger tube disposed on the downstream side of the air flow is inserted into the first opening 331. inserted into. In this embodiment, the second end 21b of one second heat exchanger tube 21 is inserted into one second opening 332, and the second end of one first heat exchanger tube 11 is inserted into one first opening 331. Section 11b is inserted. A blocking portion 333 is provided between the first opening 331 and the second opening 332 that are adjacent to each other in the first direction X.

The outer size of the first opening 331 is larger than the outer size of the second end 11b of the first heat exchanger tube 11, and the outer size of the second opening 332 is larger than the outer size of the second end 11b of the second heat exchanger tube 21. It is larger than the external size of the second end portion 21b. Here, the outer shape of the opening refers to the shape of the edge of the opening when the opening is viewed in the second direction Y or in the opposite direction to the second direction. The outer shape of the second end of the heat exchanger tube refers to the shape of the outer edge when the second end is viewed in the second direction Y or in the opposite direction to the second direction.

The second plate 34 has a plurality of first communication holes 341. The plurality of first communication holes 341 are provided at intervals along the third direction Z. Each of the plurality of first communication holes 341 penetrates the second plate 34 in the second direction Y. The first communication hole 341 overlaps with the first opening 331, the second opening 332, and the obstructing part 333 of the first plate 33, which are oppositely adjacent in the second direction. In other words, one first communication hole 341 faces one first opening 331 , one second opening 332 , and one obstruction portion 333 .

The end plate 32 is arranged adjacent to the second plate 34 in the second direction Y. The end plate 32 has a flat plate shape. The end surface 32a of the end plate 32 on the second direction Y side is the end of the laminated header 3 on the second direction Y side.

As shown in FIG. 4, one second opening 332 and one first opening 331 are lined up along the first direction One first communication hole 341 of the two plates forms a flow path 360 through which the refrigerant flows. The end plate 32 becomes a wall surface on the second direction Y side that forms the flow path 360. A surface of the first plate 33 where the obstruction portion 333 contacts the first opening 331, the second opening 332, and the first communication hole 341 becomes a part of the wall surface forming the flow path 360.

(Refrigerant flow and effect of laminated header 3)
The flow of refrigerant in the laminated header 3 according to this embodiment will be described with reference to FIG. 4. The refrigerant that flows into the first heat exchange section 10 from the liquid header 12 (see FIG. 3) and flows through the first heat exchanger tubes 11 in the second direction Y flows from the second end 11b of the first heat exchanger tubes 11 to the laminated header. 3. The refrigerant flowing out from the second end 11b of the first heat exchanger tube 11 flows into the first opening 331 of the first plate 33. The refrigerant that has flowed into the first opening 331 flows in the second direction Y and flows into the first communication hole 341 of the second plate 34 .

The refrigerant flowing into the first communication hole 341 flows in the opposite direction to the first direction. Here, the refrigerant flowing in the opposite direction to the first direction flows in the opposite direction to the flow of air. That is, the refrigerant and air flow in countercurrents to each other. The refrigerant flows in the first communication hole 341 in the opposite direction in the first direction, and then flows in the opposite direction in the second direction. In other words, the refrigerant that has flowed into the laminated header 3 in the second direction Y is turned around at the first communication hole 341 and flows in the opposite direction in the second direction.

Normally, in a heat exchanger, due to the leading edge effect, the extra-tubular heat transfer coefficient is high on the upstream side of the air flow, and the extra-tubular heat transfer coefficient is low on the downstream side of the air flow. Here, the leading edge effect refers to the effect that the heat transfer coefficient is highest at the portion of the heat exchanger tube where air first collides. Moreover, the extra-tube heat transfer coefficient refers to the heat transfer coefficient when the refrigerant flowing through the heat exchanger tube exchanges heat with air. Normally, in an evaporator, the refrigerant gradually evaporates as it flows through the heat exchanger tubes, so that the phase changes from a gas-liquid two-phase refrigerant to a single-phase gas inside the heat exchanger tubes. Furthermore, inside the heat transfer tube, the external heat transfer coefficient is high on the upstream side of the air flow, so the refrigerant flowing on the windward side evaporates more easily than the refrigerant flowing on the leeward side. However, a gas single-phase refrigerant has a lower heat transfer coefficient than a gas-liquid two-phase refrigerant, so if the gas single-phase refrigerant flows on the windward side, where the heat transfer coefficient outside the tube is high, the heat exchanger heats up. Replacement performance will deteriorate. In other words, when the gas-liquid two-phase and liquid single-phase refrigerants flow on the windward side inside the heat exchanger tube, the heat exchange performance of the heat exchanger improves.

Changes in the extratubular heat transfer coefficients of the first heat exchanger tube 11 and the second heat exchanger tube 21 in this embodiment are shown in the diagram on the left side of the paper in FIG. 4. The horizontal axis indicates the extratubular heat transfer coefficient, and the extratubular heat transfer coefficient increases toward the left in the paper. The vertical axis indicates the direction in which air flows, and the plane of the paper is on the downstream side of the air flow. Of the two curves, the curve located on the upper side of the page shows the change in the extra-tubular heat transfer coefficient of the first heat exchanger tube 11, and the curve located on the lower side of the page shows the change in the extra-tube heat transfer coefficient of the second heat exchanger tube 21. It shows the change in In the first heat exchanger tube 11 and the second heat exchanger tube 21, the portion located most upwind has the highest extra-tube heat transfer coefficient, and the extra-tube heat transfer coefficient decreases toward the leeward. Furthermore, due to the leading edge effect, the extra-tube heat transfer coefficient of the portion of the first heat exchanger tube 11 located in the upwind area UWA is higher than the extra-tube heat transfer coefficient of the portion of the second heat exchanger tube 21 located in the leeward area DWA. expensive. In addition, in FIG. 4 and subsequent figures, the structure of the diagram showing the extra-tubular heat transfer coefficient is the same as the diagram showing the extra-tubular heat transfer coefficient in FIG. 4. Therefore, description of the extratubular heat transfer coefficient in the figures after FIG. 4 will be omitted.

In the present embodiment, due to the leading edge effect, the refrigerant flowing in the second direction Y inside the first heat exchanger tube 11 distributes gas-rich refrigerant in the upwind area UWA as it approaches the stacked header 3, and the refrigerant in the leeward area A liquid-rich refrigerant will be distributed in the DWA. In other words, in a state where gas-rich refrigerant is distributed in the upwind area UWA of the first heat transfer tube 11 and liquid-rich refrigerant is distributed in the leeward area DWA, the first opening of the first plate 33 is opened from the second end 11b. Refrigerant flows into 331. When the liquid-rich refrigerant that has flowed into the first opening 331 flows into the first communication hole 341 of the second plate 34 and flows in the opposite direction to the first direction, the liquid-rich refrigerant flows toward the end plate 32 due to the action of centrifugal force. flows. The gas-rich refrigerant that has flowed into the first opening 331 flows on the obstruction portion 333 side. Here, the liquid-rich refrigerant refers to a refrigerant with a high liquid phase ratio, and the gas-rich refrigerant refers to a refrigerant with a high gas phase ratio.

On the downstream side of the first communication hole 341, the refrigerant changes its flow direction to the second opposite direction and flows into the second opening 332 of the first plate 33. The refrigerant flowing into the second opening 332 flows in the opposite second direction and flows into the second end 21b of the second heat exchanger tube 21. Here, the liquid-rich refrigerant that has flowed on the end plate 32 side of the first communication hole 341 flows on the windward side of the second opening 332 and flows into the windward region UWA of the second heat exchanger tube 21 . The gas-rich refrigerant that has flowed on the obstructing portion 333 side of the first communication hole 341 flows on the leeward side of the second opening 332, that is, on the obstructing portion 333 side, and flows into the leeward region DWA of the second heat exchanger tube 21.

In this embodiment, a flow path 360 is formed in the laminated header 3 from the first opening 331 to the second opening 332 via the first communication hole 341. A blocking portion 333 is provided between the second opening portion 332 and the second opening portion 332 . Therefore, the cross-sectional shape of the flow path 360 along the first direction X and the second direction Y is a U-shape having two right-angled corners, or an arch shape. More specifically, the wall surface of the obstructing portion 333 that extends substantially along the second direction Y causes the refrigerant flowing into the first opening 331 to move straight along the second direction Y. The end face of the obstruction portion 333 on the second direction Y side changes the flow direction of the refrigerant from the second direction Y to the opposite direction to the first direction. By forming the flow path 360 having such a shape by the obstruction portion 333, more centrifugal force acts on the refrigerant flowing into the flow path 360. Therefore, the liquid-rich refrigerant that has flowed into the first opening 331 easily flows on the end plate 32 side and on the windward side of the second opening 332 due to the action of centrifugal force.

The refrigerant that has flowed into the second heat exchange section 20 from the second end 21 b of the second heat exchanger tube 21 flows through the second heat exchanger tube 21 in the opposite second direction and flows out from the laminated header 3 . The refrigerant flowing out from the laminated header 3 flows through the second heat exchanger tube 21 in the second opposite direction, passes through the gas header 22 (see FIG. 3), and flows out from the second heat exchange section 20. Note that the refrigerant flows out from the heat exchanger 1 by flowing out from the second heat exchange section 20.

In the heat exchanger 1 according to the present embodiment, the second plate 34 is arranged between the first plate 33 and the end plate 32, and the external size of the first opening 331 of the first plate 33 is , the second end 11b of the first heat exchanger tube 11 is inserted into the first opening 331 of the first plate 33, and the second end 11b of the first heat exchanger tube 11 is inserted into the first opening 331 of the first plate 33. The external size of the second opening 332 of 33 is larger than the external size of the second end 21b of the second heat exchanger tube 21, and the second end 21b of the second heat exchanger tube 21 is It is inserted into the second opening 332. Further, the first heat exchange section 10 is located downstream of the second heat exchange section 20 in the air flow.

In the present embodiment, the refrigerant that has become gas-rich while flowing from the liquid header 12 toward the laminated header 3 flows into the first opening 331 of the first plate 33 on the side of the obstruction portion 333 . On the other hand, the liquid-rich refrigerant flows into the leeward side of the first opening 331 of the first plate 33 . The centrifugal force acts on the refrigerant flowing through the flow path 360 of the laminated header 3 due to the obstruction portion 333 of the first plate 33 . Therefore, the liquid-rich refrigerant flowing through the flow path 360 flows along the wall surface on the end plate 32 side and the wall surface on the windward side of the second opening 332 of the first plate 33, and It becomes easier to flow into the upper area UWA.

In this embodiment, the laminated header 3 allows liquid-rich refrigerant to easily flow into the upwind area UWA of the second heat exchanger tube 21. That is, the liquid-rich refrigerant flows in the opposite direction to the second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

(Modification 1 of Embodiment 1)
FIG. 7 is a diagram illustrating the configuration of a stacked header 3A according to Modification 1 of Embodiment 1. The only difference between this modification and the first embodiment is the shape of the obstructing portion of the first plate. Since the other configurations are the same as those in Embodiment 1, their description will be omitted here.

As shown in FIG. 7, the obstructing portion 333-1 of the first plate 33-1 of the laminated header 3A of Modification 1 has a tip end face in the second direction Y that is curved in the second direction Y. It has become. Therefore, the surface of the obstruction portion 333-1 that is in contact with the first opening 331-1 of the first plate 33-1, that is, a part of the wall surface forming the flow path 360, is oriented in the opposite direction in the first direction and in the second direction. It is curved in direction Y. Further, the surface of the obstruction portion 333-1 in contact with the second opening 332-1 of the first plate 33-1, that is, a part of the wall surface forming the flow path 360 is It is curved towards. In other words, in the cross-sectional shape of the flow path 360 of this modification along the first direction X and the second direction Y, the U-shaped or arch-shaped portion does not have two right-angled corners.

(Operations and effects of Modification 1 of Embodiment 1)
When the obstruction part has a right-angled corner, the refrigerant flowing in the second direction Y through the first opening of the first plate tends to travel straight along the corner, and centrifugal force is suppressed. In this modification, the surface of the obstructing part 333-1 in contact with the first opening 331-1 is curved in the opposite direction to the first direction, so that the refrigerant flowing through the first opening 331-1 flows in the opposite direction to the first direction. It flows easily and generates centrifugal force. That is, the liquid-rich refrigerant that has flowed into the flow path 360 from the leeward region DWA of the first heat exchanger tube 11 is caused by centrifugal force to cause damage to the wall surface on the end plate 32 side and the second opening 332-1 of the first plate 33-2. The heat exchanger flows along the windward wall surface of the heat exchanger tube 21 and easily flows into the windward region UWA of the second heat exchanger tube 21 . Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

(Modification 2 of Embodiment 1)
FIG. 8 is a diagram illustrating the configuration of a stacked header 3B according to a second modification of the first embodiment. The only difference between this modification and Modification 1 of Embodiment 1 is the shape of the end plate. The other configurations are the same as those in Modification 1 of Embodiment 1, so description thereof will be omitted here.

As shown in FIG. 8, the end plate 32-1 of the laminated header 3B of Modification 2 has a recess 321 that is curved in the second direction Y. The recess 321 overlaps the first communication hole 341 of the second plate 34 in the second direction Y, and forms a part of the flow path 360. Further, the end surface 32a of the end plate 32-1 is curved and convex in the second direction Y. That is, the end surface 32a of the end plate 32-1 is convex in the second direction Y, like the wall surface of the recess 321 on the second direction Y side.

(Operations and effects of Modification 2 of Embodiment 1)
In the second modification of the first embodiment, the end plate 32-1 is recessed in a curved shape in the second direction Y, and is arranged to overlap the first communication hole 341 to form a part of the flow path 360. It has a recess 321. The cross-sectional area of the flow path 360 is increased by the recess 321, and the refrigerant can easily flow between the first heat exchanger tube 11 and the second heat exchanger tube 21.

Further, when the refrigerant flowing in the second direction Y through the flow path 360 collides with the opposing surface perpendicularly, the generation of centrifugal force is suppressed. In the configuration of this modified example, since the recess 321 has a curved shape, the refrigerant flowing from the first heat exchanger tube 11 does not collide perpendicularly with the end plate 32-1, but flows into the first heat exchanger along the curved surface of the recess 321. It tends to flow in the opposite direction. Therefore, centrifugal force is more likely to occur. That is, the liquid-rich refrigerant that has flowed into the flow path 360 from the leeward region DWA of the first heat transfer tube 11 easily flows through the recess 321 of the end plate 32-1 due to the centrifugal force. Therefore, the liquid-rich refrigerant flows along the windward wall surface of the second opening 332 and easily flows into the windward region UWA of the second heat exchanger tube 21. Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

Note that in FIG. 8, the first plate 33-1 of Modification 1 is shown as the first plate. However, the first plate may be the first plate 33 of the first embodiment. The laminated header having the first plate 33-1 and the end plate 32-1 has a stronger centrifugal force on the refrigerant flowing through the flow path 360 than the laminated header having the first plate 33 and the end plate 32-1. act.

Furthermore, in the end plate 32-1 of this modification, the end surface 32a opposite to the end surface where the recess 321 is provided is curved and convex in the second direction Y. When forming the recess 321 in the end plate 32-1, the entire end plate 32-1 is bent by press working, thereby forming the recess 321 and the convex end surface 32a. By forming the recess 321 in the end plate 32-1 by press working, the heat exchanger 1 can be manufactured easily and manufacturing costs can be suppressed.

(Variation 3 of Embodiment 1)
FIG. 9 is a diagram illustrating the configuration of a stacked header 3C according to the third modification of the first embodiment. The differences between this modification and the second modification of the first embodiment are that the laminated header 3C does not have the second plate 34, and the end plate 32-1 has a recess 321. It is a point. Regarding the other configurations, the configurations described in Embodiment 1, Modification 1 of Embodiment 1, and Modification 2 of Embodiment 1 can be used, so the description will be omitted here. Further, in FIG. 9, the first plate 33-1 of Modification 1 is shown as the first plate. However, the first plate may be the first plate 33 of the first embodiment.

As shown in FIG. 9, the laminated header 3C of this modification includes a heat exchanger tube side plate 31, a first plate 33, and an end plate 32-1. Along the second direction Y, the heat exchanger tube side plate 31, the first plate 33, and the end plate 32-1 are arranged. In the stacked header 3C, the recess 321 of the end plate 32-1 replaces the first communication hole 341 of the second plate 34. That is, the end plate 32-1 replaces the second plate, and a flow path 360 similar to that of the laminated header 3B according to the second modification is formed in the laminated header 3C. Therefore, although the stacked header 3C does not have a second plate, the refrigerant is separated into a liquid-rich refrigerant and a gas-rich refrigerant in the flow path 360, and the liquid-rich refrigerant has an extra-tube heat transfer coefficient. It can be made to flow into the windward area UWA of the second heat exchanger tube 21, which is high. Furthermore, since the second plate is not required, the manufacturing cost of the laminated header can be lower than the manufacturing cost of the laminated header according to the first embodiment and the first and second modified examples.

Embodiment 2.
In this embodiment, differences between Embodiment 1 and each modification of Embodiment 1 will be mainly described. This embodiment differs from Embodiment 1 and each modification of Embodiment 1 in the structure of the laminated header. The other configurations are the same as those of the first embodiment and each modification of the first embodiment, so the description thereof will be omitted here.

FIG. 10 is a diagram illustrating the configuration of a stacked header 3D according to the second embodiment. FIG. 11 is a developed view of the stacked header 3D according to the second embodiment. As shown in FIGS. 10 and 11, the stacked header 3D includes a heat exchanger tube side plate 31, a second plate 34, a first plate 33-2, a third plate 35, and an end plate 32. Along the second direction Y, the heat exchanger tube side plate 31, the second plate 34, the first plate 33-2, the third plate 35, and the end plate 32 are arranged. The configurations of the heat exchanger tube side plate 31 and the end plate 32 are the same as in the first embodiment.

In this embodiment, the heat exchanger tube side plate 31 and the second plate 34 are arranged adjacent to each other. The second end 11b of the first heat exchanger tube 11 and the second end 21b of the second heat exchanger tube 21 are inserted into the first communication hole 341 of the second plate 34. More specifically, the second end 11b of the first heat exchanger tube 11 is inserted into the leeward side of the first communication hole 341 of the second plate 34, and the second end 21b of the second heat exchanger tube 21 is inserted into the leeward side of the first communication hole 341 of the second plate 34. It is inserted into the windward side of the first communication hole 341 of the plate 34.

The first plate 33-2 is arranged adjacent to the second plate 34 in the second direction Y. The first plate 33-2 has a plurality of first openings 331-2 and a plurality of second openings 332-2. The configuration in which the first plate 33-2 is provided with the plurality of first openings 331-2 and the plurality of second openings 332-2 is different from the configuration in which the first plate 33 of the first embodiment is provided with the plurality of first openings 331 and the plurality of second openings 332-2. This is the same configuration as that in which the second opening 332 is provided. A blocking portion 333-2 is provided between the first opening 331-2 and the second opening 332-2 that are adjacent to each other in the first direction X.

The external size of the first opening 331-2 is smaller than the external size of the second end 11b of the first heat exchanger tube 11, and the external size of the second opening 332-2 is smaller than the external size of the second end 11b of the first heat exchanger tube 11. It is smaller than the external size of the second end portion 21b of the heat tube 21. In FIG. 10, a region of the second end portion 11b of the first heat exchanger tube 11 projected onto the first plate 33-2 is indicated by a dashed dotted line as a projection region 40. In FIG. Further, a region in which the second end portion 21b of the second heat exchanger tube 21 is projected onto the first plate 33-2 is indicated by a dashed dotted line as a projection region 41. As shown in FIG. 10, a portion of the projection area 40 and a portion of the projection area 41 overlap the obstructing portion 333-2 of the first plate 33-2. In other words, the obstructing portion 333-2 of the first plate 33-2 is projected onto a projection area 40 where the upwind area UWA of the first heat exchanger tube 11 is projected and a projection area 41 where the leeward area DWA of the second heat exchanger tube 21 is projected. To position. That is, one obstructing portion 333-2 is arranged across the projection area 40 of the first heat exchanger tube 11 and the projection area 41 of the second heat exchanger tube 21 that are lined up in the first direction X. The first opening 331-2 of the first plate 33-2 is located in the projection area 40 in which the leeward area DWA of the first heat exchanger tube 11 is projected. The second opening 332-2 of the first plate 33-2 is located in a projection area 41 in which the windward area UWA of the second heat exchanger tube 21 is projected.

The third plate 35 has a plurality of second communication holes 351. The plurality of second communication holes 351 are provided at intervals along the third direction Z. Each of the plurality of second communication holes 351 penetrates the third plate 35 in the second direction Y. The second communication hole 351 overlaps with the first opening 331-2, the second opening 332-2, and the obstruction portion 333-2 of the first plate 33-2, which are oppositely adjacent in the second direction. In other words, one second communication hole 351 faces one first opening 331, one second opening 332, and one obstructing portion 333-2.

The end plate 32 is arranged adjacent to the third plate 35 in the second direction Y.

As shown in FIG. 10, the first communication hole 341 of the second plate 34, the first opening 331-2 and the second opening 332-2 of the first plate 33-2, and the second The communication hole 351 forms a flow path 360 through which the refrigerant flows. The end plate 32 becomes a wall surface on the second direction Y side that forms the flow path 360. The surface where the obstruction portion 333-2 of the first plate 33-2 contacts the first communication hole 341, the first opening 331-2, the second opening 332-2, and the second communication hole 351 is It becomes part of the wall surface forming the channel 360.

(Refrigerant flow and effect of 3D stacked header)
With reference to FIG. 10, the flow of refrigerant in the stacked header 3D according to this embodiment will be described. The refrigerant that flows into the first heat exchange section 10 from the liquid header 12 (see FIG. 3) and flows through the first heat exchanger tubes 11 in the second direction Y flows from the second end 11b of the first heat exchanger tubes 11 to the laminated header. Flow into 3D. The refrigerant flowing out from the second end portion 11b of the first heat exchanger tube 11 flows into the first communication hole 341 of the second plate 34. The refrigerant flowing into the first communication hole 341 flows in the opposite direction to the first direction and in the second direction Y. The refrigerant flowing in the opposite direction to the first direction passes through the first communication hole 341 and flows into the second end portion 21b of the second heat exchanger tube 21. The refrigerant flowing in the second direction Y through the first communication hole 341 flows into the first opening 331-2 of the first plate 33-2, continues to flow in the second direction Y, and then flows into the second direction Y of the third plate 35. The water flows into the communication hole 351 and flows in the opposite direction to the first direction. Here, the refrigerant flowing in the opposite direction to the first direction flows in the opposite direction to the flow of air. That is, the refrigerant and air flow in countercurrents to each other.

The refrigerant flowing into the second communication hole 351 flows in the opposite direction to the first direction, and then flows in the opposite direction to the second direction. In other words, the refrigerant that has flowed into the stacked header 3D in the second direction Y is turned around at the second communication hole 351 and flows in the opposite direction in the second direction.

In this embodiment, the liquid-rich refrigerant is distributed in the leeward area DWA of the first heat exchanger tube 11, and the gas-rich refrigerant is distributed in the upwind area UWA, and the second plate 34 is Refrigerant flows into the first communication hole 341 . The liquid-rich refrigerant that has flowed into the first communication hole 341 flows in the second direction Y and flows into the first opening 331-2. On the other hand, the gas-rich refrigerant that has flowed into the first communication hole 341 flows in the second direction Y, but collides with the obstruction portion 333-2 and changes its flow direction to the opposite direction to the first direction.

The liquid-rich refrigerant that has flowed into the first opening 331-2 flows directly in the second direction Y, and flows into the second communication hole 351 of the third plate 35. The liquid-rich refrigerant that has flowed into the second communication hole 351 of the third plate 35 flows on the end plate 32 side due to the action of centrifugal force when flowing in the opposite direction to the first direction. The liquid-rich refrigerant that has flowed on the end plate 32 side of the second communication hole 351 flows into the second opening 332-2 of the first plate 33-2. The liquid-rich refrigerant that has flowed into the second opening 332-2 flows in the opposite second direction and flows into the first communication hole 341 of the second plate 34. The liquid-rich refrigerant travels in the opposite second direction on the windward side of the first communication hole 341 and flows into the second end portion 21b of the second heat exchanger tube 21. Here, since the liquid-rich refrigerant flows in the opposite direction in the second direction through the region of the first communication hole 341 that faces the upwind region UWA of the second heat exchanger tube 21, the upwind region UWA of the second heat exchanger tube 21 easy to flow into. Furthermore, since gas-rich refrigerant flows in the region of the first communication hole 341 facing the leeward region DWA of the second heat exchanger tube 21, liquid-rich refrigerant flows into the leeward region DWA of the second heat exchanger tube 21. It's hard to do.

On the other hand, the gas-rich refrigerant flowing in the first communication hole 341 in the opposite direction to the first direction flows into the second heat exchanger tube 21 from the second end 21b of the second heat exchanger tube 21. Here, the liquid-rich refrigerant that flows into the first communication hole 341 from the second opening 332-2 flows into the upwind area UWA of the second heat transfer tube 21. Therefore, the gas-rich refrigerant more easily flows into the leeward region DWA of the second heat exchanger tube 21 than the windward region UWA.

The liquid-rich refrigerant and the gas-rich refrigerant that have flowed into the second heat exchange section 20 from the second end 21b of the second heat exchanger tube 21 flow through the second heat exchanger tube 21 in the second direction opposite to the stacked header 3D. flows out from. The refrigerant flowing out of the laminated header 3D flows through the second heat exchanger tube 21 in the second opposite direction, passes through the gas header 22 (see FIG. 3), and flows out from the second heat exchange section 20. Note that the refrigerant flows out from the heat exchanger 1 by flowing out from the second heat exchange section 20.

In the laminated header 3D according to the present embodiment, the second plate 34 is arranged between the heat exchanger tube side plate 31 and the first plate 33-2, and is arranged between the second end 11b of the first heat exchanger tube 11 and the The second end portion 21 b of the second heat exchanger tube 21 is inserted into the first communication hole 341 of the second plate 34 . In the second direction Y, when the second end 11b of the first heat exchanger tube 11 and the second end 21b of the second heat exchanger tube 21 are projected onto the first plate 33-2, the second end of the first heat exchanger tube 11 A portion of the projection area 40 of the portion 11b and a portion of the projection area 41 of the second end portion 21b of the second heat exchanger tube 21 overlap the obstructing portion 333-2.

According to this embodiment, the gas-rich refrigerant flowing into the stacked header 3D collides with the obstruction portion 333-2 of the first plate 33-2, and moves the first communication hole 341 of the second plate 34 in the first direction. flows in the opposite direction. On the other hand, the liquid-rich refrigerant flowing into the stacked header 3D flows in the second direction Y without colliding with the obstruction portion 333-2. Therefore, separation of the gas-rich refrigerant and the liquid-rich refrigerant is facilitated by the obstruction portion 333-2. Note that the size of the area where the projection area 40 and the obstruction part 333-2 overlap and the size of the area where the projection area 41 and the obstruction part 333-2 overlap are planned in the laminated header of the heat exchanger. It is determined by the ratio of flow rates of gas refrigerant and liquid refrigerant. In the present embodiment, the explanation is given on the assumption that half of the projection area 40 overlaps with the obstructing part 333-2 and half of the projection area 41 overlaps with the obstructing part 333-2, but this is just an example.

Further, in the present embodiment, the stacked header 3D includes a third plate 35 provided between the first plate 33-2 and the end plate 32, and the third plate 35 35 in the second direction Y, and is arranged to overlap the first opening 331-2, the second opening 332-2, and the obstruction part 333-2, and forms a part of the flow path 360. It has a communication hole 351.

With this configuration, the liquid-rich refrigerant can flow through the first communication hole 341 of the second plate 34, the first opening 331-2 of the first plate 33-2, the second communication hole 351 of the third plate 35, and the first communication hole 341 of the second plate 34, the first opening 331-2 of the first plate 33-2, It flows through the second opening 332-2 of the first plate 33-2 and the first communication hole 341 of the second plate 34 in order. The liquid-rich refrigerant easily flows into the upwind area UWA of the second heat exchanger tube 21 due to centrifugal force when flowing through each plate of the stacked header 3D. The gas-rich refrigerant flowing in the opposite direction to the first communication hole 341 flows into the windward area UWA of the second heat exchanger tube 21 because the liquid-rich refrigerant flows into the windward area UWA of the second heat exchanger tube 21. It is easier to flow into the leeward region DWA of the second heat exchanger tube 21 than in the second heat exchanger tube 21 . Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

(Modification 1 of Embodiment 2)
FIG. 12 is a diagram illustrating the configuration of a stacked header 3E according to the first modification of the second embodiment. FIG. 13 is a developed view of a stacked header 3E according to a second modification of the second embodiment. The only difference between this modification and the second embodiment is the thickness of the third plate. The other configurations are the same as those in Embodiment 2, so their description will be omitted here.

As shown in FIG. 12, the thickness of the third plate 35-1 of the laminated header 3E of this modification is the same as that of the heat exchanger tube side plate 31, the first plate 33-2, the second plate 34, and the end plate 32. Thinner than each thickness. Here, the thickness of each plate refers to the length in the second direction Y.

In this modification, since the thickness of the third plate 35-1 is thinner than the thickness of the second plate 34, the area (hereinafter referred to as , simply referred to as flow passage cross-sectional area SA2) is smaller than the area of the first communicating hole 341 of the second plate 34 in the flow passage cross-section SA1 (hereinafter simply referred to as flow passage cross-sectional area SA1). As described in the second embodiment, with the liquid-rich refrigerant distributed in the leeward area DWA of the first heat exchanger tube 11 and the gas-rich refrigerant distributed in the upwind area UWA, the first Refrigerant flows into the communication hole 341 . Here, the pressure loss of the gas-rich refrigerant is greater than the pressure loss of the liquid-rich refrigerant. Since a fluid with a large pressure loss easily flows through a region with low resistance, a gas-rich refrigerant flows through the first communication hole 341, which has a larger flow path cross-sectional area SA1, than the second communication hole 351-1, which has a smaller flow path cross-sectional area SA2. flows easily. Since the gas-rich refrigerant flows through the first communication hole 341, the liquid-rich refrigerant easily flows through the second communication hole 351-1. Therefore, separation of the liquid-rich refrigerant and the gas-rich refrigerant in the flow path 360 is facilitated.

The third plate 35-1 has a different thickness from the other plates, but as shown in FIG. 13, the lengths of the third plate 35-1 in the first direction X and the third direction Z are different from the other plates. do not. Moreover, since the difference between the second embodiment and this modification is only the thickness of the third plate, the developed view of the laminated header 3D according to the second embodiment shown in FIG. 11 and the present modification shown in FIG. There is no difference in the developed view of the laminated header 3E.

Note that in this modification, the thickness of the third plate 35-1 is reduced to reduce the flow passage cross-sectional area SA2 of the second communication hole 351-1. However, the length of the second communication hole in the third direction Z may be changed to reduce the passage cross-sectional area SA2 of the second communication hole.

(Operations and effects of Modification 1 of Embodiment 2)
As explained above, in the configuration of this modification, the thickness of the third plate 35 is thinner than the thickness of the second plate 34 in the second direction Y. Therefore, the passage cross-sectional area SA1 of the first communicating hole 341 of the second plate 34 is larger than the passage cross-sectional area SA2 of the second communicating hole 351-1 of the third plate 35. Since the gas-rich refrigerant, which has a larger pressure loss than the liquid-rich refrigerant, easily flows through the first communication hole 341 having a larger flow path cross-sectional area, separation of the liquid-rich refrigerant and the gas-rich refrigerant can be promoted. Therefore, liquid-rich refrigerant more easily flows into the windward region UWA of the second heat exchanger tube 21. Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

(Modification 2 of Embodiment 2)
FIG. 14 is a diagram illustrating the configuration of a stacked header 3F according to a second modification of the second embodiment. The only difference between this modification and the first modification of the second embodiment is the shape of the first plate. The other configurations are the same as those in Modification 1 of Embodiment 2, so description thereof will be omitted here.

As shown in FIG. 14, the obstructing portion 333-3 of the first plate 33-3 of the laminated header 3F of this modification has a tip end face in the second direction Y that is curved in the second direction Y. It has become. Therefore, the surface of the obstruction portion 333-3 that is in contact with the first opening 331-3 of the first plate 33-3, that is, a part of the wall surface forming the flow path 360, is oriented in the opposite direction in the first direction and in the second direction. It is curved in direction Y. Further, the surface of the obstruction portion 333-3 in contact with the second opening 332-3 of the first plate 33-3, that is, a part of the wall surface forming the flow path 360 is It is curved towards. In other words, in the cross-sectional shape of the flow path 360 of this modification along the first direction X and the second direction Y, the U-shaped or arch-shaped portion does not have two right-angled corners.

(Operations and effects of modification 2 of embodiment 2)
When the obstruction part has a right-angled corner, the refrigerant flowing in the second direction Y through the first opening of the first plate tends to travel straight along the corner, and centrifugal force is suppressed. In this modification, the surface of the obstructing part 333-3 in contact with the first opening 331-3 is curved in the opposite direction to the first direction, so that the refrigerant flowing through the first opening 331-3 flows in the opposite direction to the first direction. It flows easily and generates centrifugal force. That is, the liquid-rich refrigerant that has flowed into the flow path 360 from the leeward region DWA of the first heat exchanger tube 11 is caused by centrifugal force to flow into the wall surface on the end plate 32 side and the second opening 332-3 of the first plate 33-3. The heat exchanger flows along the windward wall surface and easily flows into the region of the first communication hole 341 of the second plate 34 facing the windward region UWA of the second heat exchanger tube 21 . Gas-rich refrigerant flows in the opposite direction to the first direction into the region of the first communication hole 341 facing the leeward region DWA of the second heat exchanger tube 21 . Therefore, the liquid-rich refrigerant flows into the upwind area UWA of the second end portion 21b of the second heat exchanger tube 21 from the area of the first communication hole 341 facing the upwind area UWA of the second heat exchanger tube 21. It's easy to do. Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

(Variation 3 of Embodiment 2)
FIG. 15 is a diagram illustrating the configuration of a stacked header 3G according to a third modification of the second embodiment. The differences between this modification and the second modification of the second embodiment are that the laminated header 3G does not have the third plate 35, and the end plate 32-1 has a recess 321. It is a point. The end plate 32-1 has been described in the second modification of the first embodiment, so its description will be omitted here. For other configurations, the configurations described in Embodiment 2, Modification 1 of Embodiment 2, and Modification 2 of Embodiment 2 can be used, so only the differences of this modification will be described. .

As shown in FIG. 15, the laminated header 3G of this modification includes a heat exchanger tube side plate 31, a second plate 34, a first plate 33-3, and an end plate 32-1. Along the second direction Y, the heat exchanger tube side plate 31, the second plate 34, the first plate 33-3, and the end plate 32-1 are arranged. In the stacked header 3G, the recess 321 of the end plate 32-1 replaces the second communication hole 351-1 of the third plate 35-1. That is, the end plate 32-1 replaces the third plate 35-1 to form the flow path 360 in the laminated header 3G.

(Operations and effects of modification 3 of embodiment 2)
In the flow path 360 of this modification, since the recess 321 of the end plate 32-1 is curved, the refrigerant flowing from the first heat transfer tube 11 does not collide perpendicularly with the end plate 32-1. It tends to flow along the curved surface of the recess 321 in the opposite direction to the first direction. Therefore, centrifugal force is more likely to occur. That is, the liquid-rich refrigerant that has flowed into the flow path 360 from the leeward region DWA of the first heat transfer tube 11 easily flows through the recess 321 of the end plate 32-1 due to the centrifugal force. Therefore, the liquid-rich refrigerant flows along the windward wall surface of the second opening 332-3 of the first plate 33-3, and the liquid-rich refrigerant flows to the second plate facing the windward area UWA of the second heat exchanger tube 21. It becomes easier to flow into the area of the first communication hole 341 of No. 34. Furthermore, gas-rich refrigerant flows in the opposite direction to the first direction into the region of the first communication hole 341 facing the leeward region DWA of the second heat exchanger tube 21 . Therefore, the liquid-rich refrigerant flows into the upwind area UWA of the second end portion 21b of the second heat exchanger tube 21 from the area of the first communication hole 341 facing the upwind area UWA of the second heat exchanger tube 21. It's easy to do. Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

Furthermore, since the laminated header 3G of this modification does not include the third plate 35, manufacturing costs can be suppressed more than the laminated header according to the second embodiment and the first and second modifications of the second embodiment.

Note that in FIG. 15, the first plate 33-3 of Modification 2 is shown as the first plate. However, the first plate may be the first plate 33-2 of the second embodiment. The laminated header having the first plate 33-3 and the end plate 32-1 has a stronger centrifugal force than the laminated header having the first plate 33-2 and the end plate 32-1 because of the refrigerant flowing through the flow path 360. Force acts.

Embodiment 3.
In this embodiment, differences from Embodiment 1, Embodiment 2, and each modification will be mainly described. This embodiment differs from Embodiment 1, Embodiment 2, and each modification in the arrangement of the first heat exchange section 10 and the second heat exchange section 20. Descriptions of configurations similar to those of Embodiment 1, Embodiment 2, and each modification will be omitted or simplified.

FIG. 16 is a plan view of the heat exchanger 1 according to the third embodiment. FIG. 17 is a schematic cross-sectional view of the first heat exchange section 10 and the second heat exchange section 20 of the heat exchanger 1 according to the third embodiment. FIG. 17 shows cross sections of the first heat exchange section 10 and the second heat exchange section 20 along the second direction Y and the third direction Z, arranged vertically.

In the present embodiment, the first heat exchange section 10 is arranged upstream of the second heat exchange section 20 in the first direction X in which the air flows. The first heat exchange section 10 and the second heat exchange section 20 are connected by the same laminated header 3D as in the second embodiment. The refrigerant that has flowed into the first heat exchange section 10 from the liquid header 12 passes through the plurality of first heat exchanger tubes 11 and flows into the stacked header 3D. The refrigerant that has flowed into the stacked header 3D flows in the first direction X, and then flows into the plurality of second heat exchanger tubes 21. The refrigerant that has flowed into the plurality of second heat exchanger tubes 21 passes through the gas header 22 and flows out from the second heat exchange section 20 . Since the first heat exchange section 10 is arranged upstream of the second heat exchange section 20 in the air flow, the refrigerant flowing from the liquid header 12 toward the laminated header 3D flows from the laminated header 3D to the gas header 22. The refrigerant flows upwind from the refrigerant flowing towards it. The flow of refrigerant in the stacked header 3D will be described later.

FIG. 18 is a diagram illustrating the configuration of a stacked header 3D according to the third embodiment. The stacked header 3D is the stacked header 3D of the second embodiment. In the present embodiment, the first heat exchanger tube 11 disposed on the upstream side of the air flow is inserted into the heat exchanger tube insertion port 31b (see FIG. 11) of the heat exchanger tube side plate 31, and the first heat exchanger tube 11 is placed on the downstream side of the air flow. The second heat exchanger tube 21 to be arranged is inserted into the heat exchanger tube insertion opening 31a (see FIG. 11) of the heat exchanger tube side plate 31. The difference between the laminated header 3D of this embodiment and the laminated header 3D of Embodiment 2 is that in this embodiment, the first heat exchanger tube 11 is connected to the windward side of the laminated header 3D, and the first heat exchanger tube 11 is connected to the leeward side of the laminated header 3D. This is the point where the second heat exchanger tube 21 is connected.

The second end portion 11b of the first heat exchanger tube 11 inserted into the heat exchanger tube insertion port 31b is inserted into the windward side of the first communication hole 341 of the second plate 34. The second end portion 21b of the second heat exchanger tube 21 inserted into the heat exchanger tube insertion port 31a is inserted into the leeward side of the first communication hole 341 of the second plate 34.

The external size of the first opening 331-2 is smaller than the external size of the second end 21b of the second heat transfer tube 21, and the external size of the second opening 332-2 is smaller than the external size of the second end 21b of the second heat transfer tube 21. It is smaller than the external size of the second end portion 11b of the heat tube 11. In FIG. 18, a region of the second end portion 21b of the second heat exchanger tube 21 projected onto the first plate 33-2 is indicated by a dashed dotted line as a projection region 40. In FIG. Further, a region where the second end portion 11b of the first heat exchanger tube 11 is projected onto the first plate 33-2 is indicated by a dashed dotted line as a projection region 41. As shown in FIG. 18, a portion of the projection area 40 and a portion of the projection area 41 overlap the obstructing portion 333-2 of the first plate 33-2. In other words, the obstructing portion 333-2 of the first plate 33-2 is projected onto a projection area 40 where the upwind area UWA of the second heat exchanger tube 21 is projected and a projection area 41 where the leeward area DWA of the first heat exchanger tube 11 is projected. To position. That is, one obstructing portion 333-2 is arranged across the projection area 40 of the second heat exchanger tube 21 and the projection area 41 of the first heat exchanger tube 11 that are lined up in the first direction X. The first opening 331-2 of the first plate 33-2 is located in the projection area 40 in which the leeward area DWA of the second heat exchanger tube 21 is projected. The second opening 332-2 of the first plate 33-2 is located in a projection area 41 in which the windward area UWA of the first heat exchanger tube 11 is projected.

(Refrigerant flow and effect of 3D stacked header)
The flow of refrigerant in the stacked header 3D according to this embodiment will be described with reference to FIG. 18. The refrigerant flows from the liquid header 12 (see FIG. 17) into the first heat exchange section 10 and flows through the first heat exchanger tubes 11 in the second direction Y from the second end 11b of the first heat exchanger tubes 11 to the laminated header. Flow into 3D. The refrigerant flowing out from the second end portion 11b of the first heat exchanger tube 11 flows into the first communication hole 341 of the second plate 34. The refrigerant flowing into the first communication hole 341 branches into a first direction X and a second direction Y to flow. The refrigerant flowing in the first direction X passes through the first communication hole 341 and flows into the second end portion 21b of the second heat exchanger tube 21. The refrigerant flowing in the second direction Y through the first communication hole 341 flows into the second opening 332-2 of the first plate 33-2, continues to flow in the second direction Y, and then flows into the second opening 332-2 of the third plate 35. The water flows into the communication hole 351 and flows in the first direction X. Here, the refrigerant flowing in the first direction X flows in parallel with the flow of air. That is, the refrigerant and air flow in parallel to each other.

The refrigerant flowing into the second communication hole 351 flows in the first direction X, and then flows in the opposite direction in the second direction. In other words, the refrigerant that has flowed into the stacked header 3D in the second direction Y is turned around at the second communication hole 351 and flows in the opposite direction in the second direction.

In this embodiment, the liquid-rich refrigerant is distributed in the leeward area DWA of the first heat exchanger tube 11, and the gas-rich refrigerant is distributed in the upwind area UWA, and the second plate 34 is Refrigerant flows into the first communication hole 341 . The gas-rich refrigerant that has flowed into the first communication hole 341 flows in the second direction Y and flows into the second opening 332-2 of the first plate 33-2. On the other hand, the liquid-rich refrigerant that has flowed into the first communication hole 341 flows in the second direction Y, but collides with the obstruction portion 333-2 and changes its flow direction to the first direction X.

The gas-rich refrigerant that has flowed into the second opening 332-2 flows directly in the second direction Y, and flows into the second communication hole 351 of the third plate 35. When the gas-rich refrigerant that has flowed into the second communication hole 351 of the third plate 35 flows in the first direction X, it flows on the end plate 32 side due to the action of centrifugal force. The gas-rich refrigerant that has flowed on the end plate 32 side of the second communication hole 351 flows into the first opening 331-2 of the first plate 33-2. The gas-rich refrigerant that has flowed into the first opening 331-2 flows in the opposite second direction and flows into the first communication hole 341 of the second plate 34. The gas-rich refrigerant travels in the opposite second direction on the leeward side of the first communication hole 341 and flows into the second end portion 21b of the second heat exchanger tube 21. Here, the gas-rich refrigerant flows in the opposite direction in the second direction through the region of the first communication hole 341 facing the leeward region DWA of the second heat exchanger tube 21 , so it flows into the leeward region DWA of the second heat exchanger tube 21 . Cheap. In addition, since the liquid-rich refrigerant flows in the region of the first communication hole 341 facing the windward region UWA of the second heat exchanger tube 21, the gas-rich refrigerant flows into the windward region UWA of the second heat exchanger tube 21. is difficult to enter.

On the other hand, the liquid-rich refrigerant flowing in the first direction X through the first communication hole 341 flows into the second heat exchanger tube 21 from the second end 21b of the second heat exchanger tube 21. Here, the gas-rich refrigerant that flows into the first communication hole 341 from the first opening 331-2 flows into the leeward region DWA of the second heat transfer tube 21. Therefore, the liquid-rich refrigerant more easily flows into the upwind area UWA of the second heat transfer tube 21 than the leeward area DWA.

The liquid-rich refrigerant and the gas-rich refrigerant that have flowed into the second heat exchange section 20 from the second end 21b of the second heat exchanger tube 21 flow through the second heat exchanger tube 21 in the second direction opposite to the stacked header 3D. flows out from. The refrigerant flowing out of the laminated header 3D flows through the second heat exchanger tube 21 in the second opposite direction, passes through the gas header 22 (see FIG. 17), and flows out from the second heat exchange section 20. Note that the refrigerant flows out from the heat exchanger 1 by flowing out from the second heat exchange section 20.

As explained above, in the laminated header 3D of the heat exchanger 1 according to the present embodiment, the second plate 34 is arranged between the heat exchanger tube side plate 31 and the first plate 33-2, and the second plate 34 is arranged between the heat exchanger tube side plate 31 and the first plate 33-2. The second end 11b of the heat exchanger tube 11 and the second end 21b of the second heat exchanger tube 21 are inserted into the first communication hole 341 of the second plate 34. In the second direction Y, when the second end portion 11b of the first heat exchanger tube 11 and the second end portion 21b of the second heat exchanger tube 21 are projected onto the first plate 33-2, the second end portion 11b of the first heat exchanger tube 11 A portion of the projection area 41 of the end portion 11b and a portion of the projection area 40 of the second end portion 21b of the second heat exchanger tube 21 overlap the obstructing portion 333-2.

In this embodiment, the liquid-rich refrigerant flowing into the stacked header 3D collides with the obstruction portion 333-2 of the first plate 33-2, and the first communication hole 341 of the second plate 34 is moved in the first direction flows to On the other hand, the gas-rich refrigerant flowing into the stacked header 3D flows in the second direction Y without colliding with the obstruction portion 333-2. Therefore, separation of the gas-rich refrigerant and the liquid-rich refrigerant is facilitated by the obstruction portion 333-2.

With this configuration, the gas-rich refrigerant can flow through the first communication hole 341 of the second plate 34, the second opening 332-2 of the first plate 33-2, the second communication hole 351 of the third plate 35, and the first The water flows through the first opening 331-2 of the plate 33-2 and the first communication hole 341 of the second plate 34 in this order. Therefore, the gas-rich refrigerant easily flows into the leeward region DWA of the second heat exchanger tube 21 due to the centrifugal force when flowing through each plate of the laminated header 3D. The liquid-rich refrigerant flowing through the first communication hole 341 in the first direction It is easy to flow into the windward area UWA of the second heat exchanger tube 21. Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

(Modification 1 of Embodiment 3)
FIG. 19 is a diagram illustrating the configuration of a stacked header 3H according to Modification 1 of Embodiment 3. The only difference between this modification and the third embodiment is the thickness of the second plate. The other configurations are the same as those in Embodiment 3, so their description will be omitted here.

As shown in FIG. 19, the thickness of the second plate 34-1 of the laminated header 3H of this modification is the same as that of the heat exchanger tube side plate 31, the first plate 33-2, the third plate 35, and the end plate 32. Thinner than each thickness. Here, the thickness of each plate refers to the length in the second direction Y.

In this modification, since the thickness of the second plate 34-1 is thinner than the thickness of the third plate 35, the flow passage cross-sectional area SA1 of the first communication hole 341-1 of the second plate 34-1 is It is smaller than the flow passage cross-sectional area SA2 of the second communication hole 351 of the third plate 35. As described in the third embodiment, with the liquid-rich refrigerant distributed in the leeward area DWA of the first heat exchanger tube 11 and the gas-rich refrigerant distributed in the upwind area UWA, the second plate 34-1 Refrigerant flows into the communication hole 341-1 of No. 1. Here, the pressure loss of the gas-rich refrigerant is greater than the pressure loss of the liquid-rich refrigerant. Since a fluid with a large pressure loss easily flows through a region with low resistance, a gas-rich refrigerant flows through the second communication hole 351, which has a larger flow path cross-sectional area SA2 than the first communication hole 341-1, which has a smaller flow path cross-sectional area SA1. flows easily. Since the gas-rich refrigerant flows through the second communication hole 351, the liquid-rich refrigerant easily flows through the first communication hole 341-1. Therefore, separation of the liquid-rich refrigerant and the gas-rich refrigerant in the flow path 360 is facilitated.

Although the second plate 34-1 has a different thickness from the other plates, the lengths of the second plate 34-1 in the first direction X and the third direction Z are the same as those of the other plates. Moreover, the only difference between the laminated header 3D according to the third embodiment and the laminated header 3D according to this modification is the thickness of the second plate. Therefore, there is no difference between the developed view of the laminated header 3D according to the second embodiment shown in FIG. 11 and the developed view (not shown) of the laminated header 3H according to this modification.

Note that in this modification, the flow passage cross-sectional area SA1 of the first communication hole 341-1 is reduced by reducing the thickness of the second plate 34-1. However, the length of the first communication hole in the third direction Z may be changed to reduce the flow passage cross-sectional area of the first communication hole.

(Operations and effects of Modification 1 of Embodiment 3)
As explained above, in the configuration of this modification, the thickness of the second plate 34-1 is thinner than the thickness of the third plate 35 in the second direction Y. Therefore, the passage cross-sectional area SA2 of the second communicating hole 351 of the third plate 35 is larger than the passage cross-sectional area SA1 of the first communicating hole 341-1 of the second plate 34-1. Since the gas-rich refrigerant, which has a larger pressure loss than the liquid-rich refrigerant, easily flows through the second communication hole 351, which has a larger flow path cross-sectional area SA2, separation of the liquid-rich refrigerant and the gas-rich refrigerant can be promoted. Therefore, liquid-rich refrigerant more easily flows into the windward region UWA of the second heat exchanger tube 21. Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

(Modification 2 of Embodiment 3)
FIG. 20 is a diagram illustrating the configuration of a stacked header 3I according to a second modification of the third embodiment. The only difference between this modification and the first modification of the third embodiment is the shape of the first plate. The other configurations are the same as those in Modification 1 of Embodiment 3, so descriptions thereof will be omitted here.

The first plate 33-3 of this modification is the same as the first plate 33-1 described in the second modification of the second embodiment. That is, as shown in FIG. 20, the obstructing portion 333-3 of the first plate 33-3 of the laminated header 3I of this modification has a tip end face in the second direction Y that is curved in the second direction Y. It is convex. Therefore, the surface of the obstruction portion 333-3 that is in contact with the first opening 331-3 of the first plate 33-3, that is, a part of the wall surface forming the flow path 360, is oriented in the opposite direction in the first direction and in the second direction. It is curved in direction Y. Further, the surface of the obstruction portion 333-3 in contact with the second opening 332-3 of the first plate 33-3, that is, a part of the wall surface forming the flow path 360 is It is curved towards. In other words, in the cross-sectional shape of the flow path 360 of this modification along the first direction X and the second direction Y, the U-shaped or arch-shaped portion does not have two right-angled corners.

(Operations and effects of Modification 2 of Embodiment 3)
When the obstruction part has a right-angled corner, the refrigerant flowing in the second direction Y through the second opening of the first plate tends to travel straight along the corner, and centrifugal force is suppressed. In this modification, the surface of the obstruction part 333-3 that the second opening 332-3 contacts is curved in the first direction X, so the refrigerant flowing through the second opening 332-3 flows in the first direction X. centrifugal force is likely to occur. That is, the gas-rich refrigerant flowing into the flow path 360 from the windward area UWA of the first heat exchanger tube 11 is caused by centrifugal force to cause the gas-rich refrigerant to flow into the wall surface on the end plate 32 side and the first opening 331-3 of the first plate 33-3. It flows along the leeward wall surface of the heat exchanger tube 21 and easily flows into the region of the first communication hole 341 of the second plate 34-1 facing the leeward region DWA of the second heat exchanger tube 21. Liquid-rich refrigerant flows in the first direction X into the region of the first communication hole 341-1 facing the upwind region UWA of the second heat exchanger tube 21. Therefore, the gas-rich refrigerant flows into the leeward area DWA of the second end portion 21b of the second heat exchanger tube 21 from the area of the first communication hole 341-1 facing the leeward area DWA of the second heat exchanger tube 21. Cheap. Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

(Variation 3 of Embodiment 3)
FIG. 21 is a diagram illustrating the configuration of a stacked header 3J according to a third modification of the third embodiment. The differences between this modification and the second modification of the third embodiment are that the laminated header 3J does not have the third plate 35, and the end plate 32-1 has a recess 321. It is a point. The end plate 32-1 has been described in the second modification of the first embodiment, so its description will be omitted here. In addition, for other configurations, the configurations described in Embodiment 3, Modification 1 of Embodiment 3, and Modification 2 of Embodiment 3 can be used, so only the differences of this modification will be explained. .

As shown in FIG. 21, the laminated header 3J of this modification includes a heat exchanger tube side plate 31, a second plate 34-1, a first plate 33-3, and an end plate 32-1. Along the second direction Y, the heat exchanger tube side plate 31, the second plate 34-1, the first plate 33-3, and the end plate 32-1 are arranged. In the stacked header 3J, the recess 321 of the end plate 32-1 replaces the second communication hole 351 of the third plate 35. That is, the end plate 32-1 replaces the third plate 35 and forms the flow path 360 in the laminated header 3J.

(Operations and effects of modification 3 of embodiment 3)
In the flow path 360 of this modification, since the recess 321 has a curved shape, the refrigerant flowing from the first heat exchanger tube 11 does not collide perpendicularly with the end plate 32-1, but flows along the curved surface of the recess 321. It tends to flow in the first direction X. Therefore, centrifugal force is more likely to occur. That is, the gas-rich refrigerant flowing into the flow path 360 from the windward area UWA of the first heat transfer tube 11 easily flows through the recess 321 of the end plate 32-1 due to centrifugal force. Therefore, the gas-rich refrigerant flows along the leeward wall surface of the first opening 331-3 of the first plate 33-3, and the second plate 34-, which faces the leeward area DWA of the second heat exchanger tube 21, flows along the leeward wall surface of the first opening 331-3 of the first plate 33-3. It becomes easier to flow into the region of the first communication hole 341-1. Furthermore, liquid-rich refrigerant flows in the first direction X into the region of the first communication hole 341-1 facing the upwind region UWA of the second heat transfer tube 21. Therefore, the gas-rich refrigerant flows into the leeward area DWA of the second end portion 21b of the second heat exchanger tube 21 from the area of the first communication hole 341-1 facing the leeward area DWA of the second heat exchanger tube 21. Cheap. Therefore, the liquid-rich refrigerant flows in the opposite second direction through the upwind region UWA of the second heat exchanger tube 21 where the extra-tube heat transfer coefficient is high, and the heat exchange performance of the heat exchanger 1 is improved.

Moreover, since the laminated header 3J of this modification does not have the third plate 35, manufacturing costs can be suppressed more than the laminated header according to the third embodiment and the first and second modifications of the third embodiment.

Note that in FIG. 21, the first plate 33-3 of Modification 2 is shown as the first plate. However, the first plate may be the first plate 33-2 of the third embodiment. The laminated header having the first plate 33-3 and the end plate 32-1 has a stronger centrifugal force than the laminated header having the first plate 33-2 and the end plate 32-1 because of the refrigerant flowing through the flow path 360. Force acts.

(Other variations of Embodiment 3)
In the arrangement of the first heat exchange section 10 and the second heat exchange section 20 of the third embodiment, the laminated header 3C described in the third modification of the first embodiment may be applied. In this case, the second end 21b of the second heat exchanger tube 21 is inserted into the first opening 331-1 of the first plate 33-1 of the laminated header 3C, and -1, the second end portion 11b of the first heat exchanger tube 11 is inserted.

As explained above, the heat exchanger 1 according to Embodiments 1 to 3, Modification 1 and Modification 2 of Embodiment 1, and Modifications of

Embodiments

2 and 3 has a first heat exchange section. 10, a second heat exchange section 20 arranged side by side with the first heat exchange section 10 in the first direction X, which is the direction in which air flows; It includes

stacked headers

3, 3A, 3B, 3D to 3J that connect the heat exchange section 20 and allow the refrigerant to flow between the first heat exchange section 10 and the second heat exchange section 20. The first heat exchange section 10 includes a liquid header 12 arranged at a distance from the

laminated headers

3, 3A, 3B, 3D to 3J, and a liquid header 12 that connects the liquid header 12 to the

laminated headers

3, 3A, 3B, 3D to 3J. The first end 11a is connected to the liquid header 12, and the second end 11b is connected to the

laminated header

3, 3A, 3B, 3D. ~3J. The second heat exchange section 20 extends along the second direction Y with a gas header 22 arranged at intervals from the stacked

headers

3, 3A, 3B, 3D to 3J, and has a first end 21a connected to the gas header 22. and a second heat transfer tube 21 whose second end portion 21b is connected to the

laminated header

3, 3A, 3B, 3D to 3J. The

laminated headers

3, 3A, 3B, 3D to 3J have a heat exchanger tube side plate 31 through which the first heat exchanger tube 11 and the second heat exchanger tube 21 penetrate, and in the second direction Y, the

laminated header

3, 3A, 3B, End plates 32, 32-1 forming the ends of 3D to 3J, and first plates 33, 33-1, 33 arranged between the heat exchanger tube side plate 31 and the end plates 32, 32-1. -2, 33-3 and between the heat exchanger tube side plate 31 and the first plate 33, 33-1, 33-2, 33-3, or the first plate 33, 33-1, 33-2, 33- and a second plate 34, 34-1 disposed between the end plate 32, 32-1, and the first plate 33, 33-1, 33-2, 33-3. The second plates 34 and 34-1 form a flow path 360 through which the refrigerant flows between the first heat exchanger tube 11 and the second heat exchanger tube 21. The first plates 33, 33-1, 33-2, 33-3 penetrate the first plates 33, 33-1, 33-2, 33-3 in the second direction Y to partially form the flow path 360. The first openings 331, 331-1, 331-2, 331-3 to be formed are located upstream of the air flow than the first openings 331, 331-1, 331-2, 331-3, Second openings 332, 332-1, 332-2, 332- that penetrate the first plates 33, 33-1, 33-2, 33-3 in the second direction Y and form part of the flow path 360. 3, and interfering

parts

333, 333 provided between the first openings 331, 331-1, 331-2, 331-3 and the second openings 332, 332-1, 332-2, 332-3. -1, 333-2, and 333-3. The second plate 34, 34-1 penetrates the second plate 34, 34-1 in the second direction Y, and includes the first openings 331, 331-1, 331-2, 331-3, and the second opening 332. , 332-1, 332-2, 332-3, and the first communication hole 341 that is arranged to overlap the obstructing parts 333, 333-1, 333-2, 333-3 and forms a part of the flow path 360. , 341-1.

With this configuration, the refrigerant can be separated into liquid-rich refrigerant and gas-rich refrigerant using the stacked header. Therefore, heat exchange between air and refrigerant can be performed efficiently. Therefore, the heat transfer performance of the heat exchanger 1 can be improved.

Further, in the heat exchanger 1 according to the first embodiment, the first and second modifications of the first embodiment, and the second embodiment and each modification thereof, the first heat exchange section 10 is different from the second heat exchange section 20. located downstream of the air flow. The refrigerant that has become gas-rich while flowing from the liquid header 12 toward the

laminated headers

3, 3A, 3B, 3D to 3G is transferred to the lee of the second heat transfer tube 21 by the

laminated headers

3, 3A, 3B, 3D to 3G. It flows into area DWA. On the other hand, the liquid-rich refrigerant is transferred upwind of the second heat transfer tube 21, which is located on the windward side of the heat exchanger 1 and has the highest extra-tube heat transfer coefficient, by the

laminated headers

3, 3A, 3B, 3D to 3G. It flows through area UWA. Therefore, in the second heat exchanger tube 21, heat exchange between the liquid-rich refrigerant and air is performed more efficiently, and the heat exchange performance of the heat exchanger 1 is improved.

Furthermore, in the heat exchanger 1 according to the third embodiment, the first heat exchange section 10 is located upstream of the second heat exchange section 20 in the air flow. In the process of flowing from the liquid header 12 toward the

laminated headers

3D, 3H to 3J, the windward area UWA of the first heat exchanger tube 11, which is located on the windward side of the heat exchanger 1 and has the highest extra-tube heat transfer coefficient, is The flowing refrigerant flows into the

stacked headers

3D, 3H to 3J in a gas-rich state. The gas-rich refrigerant flows into the leeward region DWA of the second heat transfer tube 21 on the most leeward side of the heat exchanger 1 through the stacked

headers

3D, 3H to 3J. On the other hand, the liquid-rich refrigerant flows through the upwind region UWA of the second heat transfer tube 21 through the

laminated headers

3D, 3H to 3J. Therefore, in the second heat exchanger tube 21, heat exchange between the liquid-rich refrigerant and air is performed more efficiently, and the heat exchange performance of the heat exchanger 1 is improved.

Furthermore, the heat exchanger 1 according to the third modification of the first embodiment includes a first heat exchange section 10 and a first heat exchange section 10 arranged in parallel with the first heat exchange section 10 in the first direction X, which is the direction in which air flows. The first heat exchange section 10 and the second heat exchange section 20 are connected along the first direction X, and the refrigerant is transferred between the first heat exchange section 10 and the second heat exchange section 20. It is equipped with a laminated header 3C for circulating the flow. The first heat exchange section 10 includes a liquid header 12 arranged at a distance from the laminated header 3C, and a second direction which is directed from the liquid header 12 toward the laminated header 3C and intersects with the first direction X. It has a first heat exchanger tube 11 that extends along Y, and has a first end 11a connected to the liquid header 12 and a second end 11b connected to the laminated header 3C. The second heat exchange section 20 extends along the second direction Y with a gas header 22 arranged at a distance from the stacked header 3C, and has a first end 21a connected to the gas header 22 and a second end 21b. It has a second heat exchanger tube 21 connected to the laminated header 3C. The laminated header 3C includes a heat exchanger tube side plate 31 through which the first heat exchanger tube 11 and the second heat exchanger tube 21 pass, and an end plate 32-1 forming an end of the laminated header 3C in the second direction Y. , has first plates 33, 33-1 disposed between the heat exchanger tube side plate 31 and the end plate 32-1, and the first plates 33, 33-1 and the end plate 32-1 are , a flow path 360 is formed between the first heat exchanger tube 11 and the second heat exchanger tube 21 to allow the refrigerant to flow therethrough. The first plate 33, 33-1 has a first opening 331, 331-1 that penetrates the first plate 33, 33-1 in the second direction Y and forms a part of the flow path 360, and a first opening a second opening 332 located on the upstream side of the air flow than the sections 331, 331-1, penetrating the first plates 33, 33-1 in the second direction Y and forming a part of the flow path 360; 332-1, and obstructing portions 333, 333-1 provided between the first openings 331, 331-1 and the second openings 332, 332-1. The end plate 32-1 is recessed in the second direction Y, and is arranged to overlap the first openings 331, 331-1, the second openings 332, 332-1, and the obstructing parts 333, 333-1. It has a recess 321 that forms a part of the flow path 360.

With this configuration, the laminated header 3C can separate the refrigerant into liquid-rich refrigerant and gas-rich refrigerant. Therefore, heat exchange between air and refrigerant can be performed efficiently. Therefore, the heat transfer performance of the heat exchanger 1 can be improved. In addition, since the laminated header 3C can be constructed from a total of three plates: the heat exchanger tube side plate, the first plate, and the end plate, it is easier to manufacture than the laminated header that is composed of four or more plates. Costs can be controlled.

In addition, the refrigeration cycle device 100 according to each of the above embodiments and modifications includes a compressor 101 that compresses refrigerant, a radiator 102 that radiates heat from the refrigerant flowing out from the compressor 101, and a radiator 102 that radiates heat from the refrigerant flowing out from the radiator 102. The evaporator 104 includes an expansion mechanism 103 that reduces the pressure of the refrigerant, an evaporator 104 that evaporates the refrigerant flowing out from the expansion mechanism 103, and a blower 107 that sends air to the evaporator 104. This is a heat exchanger 1 according to a modification. By separating the refrigerant into a liquid-rich refrigerant and a gas-rich refrigerant using the laminated header of the evaporator 104, heat exchange between the air and the refrigerant in the evaporator 104 is performed efficiently. Therefore, it is possible to provide a refrigeration cycle device 100 having an evaporator 104 with improved heat transfer performance.

The heat exchanger according to the present disclosure is not limited to the embodiments and modifications described above, and can be modified in various ways. For example, in each of the above embodiments and modifications, the third direction Z is the gravity direction, and the second direction Y in which the plurality of first heat exchanger tubes 11 and the plurality of second heat exchanger tubes 21 extend is the horizontal direction. The heat exchanger 1 has been described. However, the second direction Y in which the plurality of heat exchanger tubes extend may be in the direction of gravity or opposite to the direction of gravity, and the third direction Z may be the horizontal direction. Furthermore, in each of the above embodiments and modifications, the first heat exchange section 10 and the second heat exchange section 20 each have a plurality of plate-shaped fins 2. However, the plurality of fins may be corrugated fins having a corrugated shape. Furthermore, the first heat exchange section and the second heat exchange section may be finless heat exchangers that do not have fins.

1 heat exchanger, 2 fins, 3 laminated header, 3A laminated header, 3B laminated header, 3C laminated header, 3D laminated header, 3E laminated header, 3F laminated header, 3G laminated header, 3H laminated Type header, 3I Stacked header, 3J Stacked header, 10 First heat exchange section, 11 First heat exchanger tube, 11a First end, 11b Second end, 12 Liquid header, 20 Second heat exchange section, 21 2nd heat exchanger tube, 21a first end, 21b second end, 22 gas header, 31 heat exchanger tube side plate, 31a heat exchanger tube insertion port, 31b heat exchanger tube insertion port, 32 end plate, 32a end face, 32-1 end part plate, 33 first plate, 33-1 first plate, 33-2 first plate, 33-3 first plate, 34 second plate, 34-1 second plate, 35 third plate, 35-1 second plate 3 plates, 40 projection area, 41 projection area, 100 refrigeration cycle device, 101 compressor, 102 radiator, 103 expansion mechanism, 104 evaporator, 105 refrigerant piping, 106 blower, 107 blower, 321 recess, 331 first opening , 331-1 first opening, 331-2 first opening, 331-3 first opening, 332 second opening, 332-1 second opening, 332-2 second opening, 332-3 2nd opening, 333 obstruction part, 333-1 obstruction part, 333-2 obstruction part, 333-3 obstruction part, 341 first communication hole, 341-1 first communication hole, 351 second communication hole, 351-1 second communication hole, 360 flow path, X first direction, Y second direction, Z third direction, SA1 flow path cross section, SA2 flow path cross section, UWA windward area, DWA leeward area.

Claims

a first heat exchange section;
a second heat exchange section arranged in parallel with the first heat exchange section in a first direction, which is the direction in which air flows;
a stacked header that connects the first heat exchange section and the second heat exchange section along the first direction and allows a refrigerant to flow between the first heat exchange section and the second heat exchange section; Equipped with
The first heat exchange section includes:
a liquid header spaced apart from the laminated header;
A direction extending from the liquid header toward the laminated header and extending along a second direction intersecting the first direction, with a first end connected to the liquid header and a second end connected to the laminated header. a first heat exchanger tube connected to the
The second heat exchange section includes:
a gas header spaced apart from the stacked header;
a second heat exchanger tube extending along the second direction, having a first end connected to the gas header and a second end connected to the laminated header;
The laminated header includes:
a heat exchanger tube side plate through which the first heat exchanger tube and the second heat exchanger tube pass;
an end plate forming an end of the stacked header in the second direction;
a first plate disposed between the heat exchanger tube side plate and the end plate;
a second plate disposed either between the heat exchanger tube side plate and the first plate or between the first plate and the end plate;
The first plate and the second plate form a flow path through which the refrigerant flows between the first heat exchanger tube and the second heat exchanger tube,
The first plate is
a first opening that penetrates the first plate in the second direction and forms a part of the flow path;
a second opening located upstream of the air flow than the first opening, penetrating the first plate in the second direction and forming a part of the flow path;
a blocking portion provided between the first opening and the second opening;
The second plate passes through the second plate in the second direction, and is disposed overlapping the first opening, the second opening, and the obstruction portion to form a part of the flow path. A heat exchanger having a first communication hole.
The heat exchanger according to claim 1, wherein the first heat exchange section is located downstream of the air flow than the second heat exchange section.
the second plate is disposed between the first plate and the end plate;
The outer size of the first opening of the first plate is larger than the outer size of the second end of the first heat exchanger tube,
the second end of the first heat exchanger tube is inserted into the first opening of the first plate;
The outer size of the second opening of the first plate is larger than the outer size of the second end of the second heat exchanger tube,
The heat exchanger according to claim 1 or 2, wherein the second end of the second heat exchanger tube is inserted into the second opening of the first plate.
The end plate is
The heat exchanger according to claim 3, further comprising a recess that is curved in the second direction and that is arranged to overlap the first communication hole and forms a part of the flow path.
The heat exchanger according to claim 4, wherein the end plate has an end face opposite to the end face where the recess is provided, which is curved and convex in the second direction.
The heat exchanger according to claim 1, wherein the first heat exchange section is located on the upstream side of the air flow than the second heat exchange section.
The second plate is arranged between the heat exchanger tube side plate and the first plate,
The second end of the first heat exchanger tube and the second end of the second heat exchanger tube are inserted into the first communication hole of the second plate,
In the second direction, when the second end of the first heat exchanger tube and the second end of the second heat exchanger tube are projected onto the first plate, the second end of the first heat exchanger tube The heat exchanger according to claim 2 or 6, wherein a part of the projected area of the second end of the second heat exchanger tube and a part of the projected area of the second end of the second heat exchanger tube overlap with the obstructing part.
The laminated header includes:
a third plate provided between the first plate and the end plate;
The third plate passes through the third plate in the second direction, and is disposed overlapping the first opening, the second opening, and the obstruction part to form a part of the flow path. The heat exchanger according to claim 7, having a second communication hole.
The heat exchanger according to claim 8, wherein the thickness of the third plate is thinner than the thickness of the second plate in the second direction.
The heat exchanger according to claim 8, wherein the thickness of the second plate is thinner than the thickness of the third plate in the second direction.
The end plate is
According to claim 7, the recess is curved in the second direction, and has a recess that is arranged to overlap the first opening, the second opening, and the obstruction part to form a part of the flow path. Heat exchanger as described.
The heat exchanger according to claim 11, wherein the end plate has an end face opposite to the end face where the recess is provided, which is curved and convex in the second direction.
The heat exchanger according to any one of claims 1 to 12, wherein the end face of the distal end of the obstruction portion in the second direction is curved and convex in the second direction.
a first heat exchange section;
a second heat exchange section arranged in parallel with the first heat exchange section in a first direction, which is the direction in which air flows;
a stacked header that connects the first heat exchange section and the second heat exchange section along the first direction and allows a refrigerant to flow between the first heat exchange section and the second heat exchange section; Equipped with
The first heat exchange section includes:
a liquid header spaced apart from the laminated header;
A direction extending from the liquid header toward the laminated header and extending along a second direction intersecting the first direction, with a first end connected to the liquid header and a second end connected to the laminated header. a first heat exchanger tube connected to the
The second heat exchange section includes:
a gas header spaced apart from the stacked header;
a second heat exchanger tube extending along the second direction, having a first end connected to the gas header and a second end connected to the laminated header;
The laminated header includes:
a heat exchanger tube side plate through which the first heat exchanger tube and the second heat exchanger tube pass;
an end plate forming an end of the stacked header in the second direction;
a first plate disposed between the heat exchanger tube side plate and the end plate;
The first plate and the end plate form a flow path through which the refrigerant flows between the first heat exchanger tube and the second heat exchanger tube,
The first plate is
a first opening that penetrates the first plate in the second direction and forms a part of the flow path;
a second opening located upstream of the air flow than the first opening, penetrating the first plate in the second direction and forming a part of the flow path;
and a blocking portion provided between the first opening and the second opening,
The end plate has a recess that is recessed in the second direction and is disposed overlapping the first opening, the second opening, and the obstruction part to form a part of the flow path. exchanger.
a compressor that compresses refrigerant;
a radiator that radiates heat from the refrigerant flowing out from the compressor;
an expansion mechanism that reduces the pressure of the refrigerant flowing out from the radiator;
an evaporator that evaporates the refrigerant flowing out from the expansion mechanism;
a blower that sends air to the evaporator;
The evaporator is a heat exchanger according to any one of claims 1 to 14. A refrigeration cycle device.