WO2023119468A1

WO2023119468A1 - Heat exchanger and air conditioner

Info

Publication number: WO2023119468A1
Application number: PCT/JP2021/047498
Authority: WO
Inventors: 良太赤岩; 洋次尾中; 理人足立; 寧彦松尾; 武巳松本; 幸大宮川; 優紀大谷; 央平加藤; 勇太佐藤
Original assignee: 三菱電機株式会社
Priority date: 2021-12-22
Filing date: 2021-12-22
Publication date: 2023-06-29
Also published as: JPWO2023119468A1

Abstract

This heat exchanger is provided with: a plurality of heat transfer pipes arranged vertically at an interval; a first distributor that is formed so as to extend vertically and distributes a refrigerant to the plurality of heat transfer pipes. The first distributor has: an insertion surface part through which the plurality of heat transfer pipes are inserted; an opposite surface part that is opposite to the insertion surface part in a direction in which the plurality of heat transfer pipes extend; a lateral surface part that is a wall extending between the insertion surface part and the opposite surface part in an axially-perpendicular cross-section, being a perpendicular cross-section relative to the longitudinal direction of the first distributor, and that is joined to the opposite surface part. The opposite surface part has: a flat-plate portion connected to the lateral surface part; and a swelling-expansion portion that is formed such that a portion of an inner wall forming the internal space of the first distributor swellingly expands from the flat-plate portion toward the insertion surface part, in the axially-perpendicular cross-section. The first distributor is configured such that, in the axially-perpendicular cross-section, when the minimum distance from the the leading ends of the plurality of the heat transfer pipes to the swelling-expansion portion is defined as a first distance M1 and the distance from the leading ends of the plurality of heat transfer pipes in the extension direction of the plurality of heat transfer pipes to the position of the flat-plate portion is defined as a second distance M2, the relationship of second distance M2 ≥ 1.5×first distance M1 is satisfied.

Description

heat exchangers and air conditioners

The present disclosure relates to a heat exchanger and an air conditioner having heat transfer tubes, and more particularly to a distributor that branches and supplies refrigerant to the heat transfer tubes.

Generally, a vapor compression refrigeration cycle device widely used in heat pump devices such as air conditioners has four components: a compressor, a heat exchanger functioning as a condenser, an expansion valve, and a heat exchanger functioning as an evaporator. Consists of element parts. In this refrigeration cycle device, a refrigerant, which is a first working fluid, flows through these four elemental parts with changes in state. Conventionally, an evaporator provided in a vapor compression refrigeration cycle apparatus includes a plurality of heat transfer tubes to reduce flow loss, and a distributor (header) for distributing the refrigerant to the plurality of heat transfer tubes. There is In order for the evaporator to function with high efficiency, it is necessary to distribute the refrigerant to each of the plurality of heat transfer tubes according to the amount of heat between the refrigerant and the second working fluid, such as air, which exchanges heat with the refrigerant. be.

On the other hand, since the refrigerant flowing out from the expansion valve is in a gas-liquid two-phase refrigerant state in which low-temperature, low-pressure gas refrigerant and liquid refrigerant are mixed, the distribution of the refrigerant to the evaporator tends to become uneven. In particular, when the longitudinal direction of the distributor is arranged vertically, the low-density gas refrigerant and the high-density liquid refrigerant tend to separate under the influence of gravity in the process in which the refrigerant advances in the vertical direction. In addition, in the process in which the refrigerant advances in the vertical direction, the high-density liquid refrigerant may be biased in the traveling direction due to the influence of the inertial force when the refrigerant flows into the distributor.

Therefore, in order to improve the distribution of the refrigerant, there has been proposed a heat exchanger having a distributor provided with a wall member inside a cylindrical tube having a plurality of outflow tube connection ports in the longitudinal direction (see, for example, Patent Document 1). ). In the heat exchanger of Patent Document 1, the refrigerant flowing from the flow passage holes of the plurality of heat transfer tubes gathers in the first space located in the lower part of the distributor and the first space located in the upper part of the distributor. It has a second space for distributing the gas-liquid two-phase refrigerant collected in one space to the passage holes of the plurality of heat transfer tubes. The heat exchanger of Patent Document 1 is provided with a partition plate with a hole called a wall member between the first space and the second space. It is said that the liquid refrigerant, which is biased toward the opposing wall surface due to the influence thereof, is guided to the holes to improve the biased distribution in the second space.

JP 2013-61114 A

However, in the distributor described in Patent Document 1, the liquid refrigerant separates from the gas refrigerant in the downstream part of the distributor where the flow velocity decreases and the liquid refrigerant and the gas refrigerant tend to separate, and the upper part of the distributor falls. There is a risk that the supply of liquid refrigerant to will be insufficient and the performance of the heat exchanger will be degraded.

An object of the present disclosure is to solve the above-described problems, and to provide a heat exchanger and an air conditioner that suppress insufficient supply of liquid refrigerant to the upper portion of the distributor.

The heat exchanger according to the present disclosure includes a plurality of heat transfer tubes arranged at intervals in the vertical direction, and a first distributor formed to extend in the vertical direction and distributing the refrigerant to the plurality of heat transfer tubes. , wherein the first distributor includes an insertion surface portion into which the plurality of heat transfer tubes are inserted, a facing surface portion facing the insertion surface portion in the direction in which the plurality of heat transfer tubes extends, and a cross section perpendicular to the longitudinal direction of the first distributor is a wall extending between the insertion surface portion and the opposing surface portion, the opposing surface portion having a side surface portion joined to the opposing surface portion, the opposing surface portion including a flat plate portion connected to the side surface portion; A portion of the inner wall forming the internal space of the first distributor has a bulging portion that bulges from the flat plate portion toward the insertion surface portion in a perpendicular cross section, and the first distributor has a plurality of The shortest distance from the tip of each of the heat transfer tubes to the bulging portion is the first distance M1, and the distance from the tip of each of the plurality of heat transfer tubes to the position of the flat plate portion in the direction in which the plurality of heat transfer tubes extends is the first When two distances M2 are used, the relationship of second distance M2≧1.5×first distance M1 is satisfied.

An air conditioner according to the present disclosure has a heat exchanger according to the present disclosure and a blower that supplies air to the heat exchanger.

The heat exchanger according to the present disclosure includes a first distributor that satisfies the relationship of second distance M2≧1.5×first distance M1. The first distributor can minimize the cross-sectional area of the internal space of the first distributor by setting the second distance M2 to be 1.5 times or more the first distance M1. Additionally, the wet edge length can be increased. Therefore, the first distributor can have a smaller hydraulic equivalent diameter and, as a result, a larger flooding constant. As a result, in the first distributor, the liquid refrigerant and the gas refrigerant are separated in the gas-liquid two-phase refrigerant in the first distributor, so that the liquid refrigerant can be kept at a flow rate that does not fall, and the liquid refrigerant flows to the upper part of the first distributor. Insufficient supply of liquid refrigerant can be suppressed.

Since the air conditioner according to the present disclosure includes the heat exchanger having the above configuration, the liquid refrigerant and the gas refrigerant are separated in the gas-liquid two-phase refrigerant in the first distributor, and the flow velocity can be maintained so that the liquid refrigerant does not drop. It is possible to suppress insufficient supply of liquid refrigerant to the upper portion of the first distributor.

1 is a configuration diagram of an air conditioner according to Embodiment 1. FIG. 1 is a schematic diagram of a heat exchanger according to Embodiment 1; FIG. 1 is a schematic diagram of a first distributor related to Embodiment 1; FIG. 1 is a perspective view of a first distributor according to Embodiment 1; FIG. FIG. 4 is a cross-sectional view perpendicular to the direction in which the main body extends along line AA shown in FIG. 3; FIG. 4 is a cross-sectional view perpendicular to the direction in which the main body extends along line BB shown in FIG. 3; FIG. 4 is a cross-sectional view perpendicular to the direction in which the main body extends along line CC shown in FIG. 3; It is an explanatory view for explaining an action of a swelling part. FIG. 10 is a diagram showing the relationship between the flooding constant and the height inside the distributor; 4 is a schematic diagram showing the flow of refrigerant in the first distributor in the heat exchanger of Embodiment 1. FIG. FIG. 8 is a conceptual cross-sectional view of a bulging portion according to Embodiment 2; FIG. 11 is a conceptual cross-sectional view of a first alternative form of a bulging portion according to Embodiment 2; FIG. 11 is a conceptual cross-sectional view of a second alternative form of the bulging portion according to the second embodiment; FIG. 11 is a conceptual cross-sectional view of a third alternative form of the bulging portion according to the second embodiment; FIG. 11 is a conceptual cross-sectional view of a fourth alternative form of the bulging portion according to the second embodiment; FIG. 12 is a conceptual cross-sectional view of a fifth alternative form of the bulging portion according to the second embodiment; FIG. 11 is a perspective view of a main body of a first distributor according to Embodiment 2; FIG. 11 is a conceptual cross-sectional view of a first alternative form of an orifice plate used in a first distributor according to Embodiment 3; FIG. 11 is a conceptual cross-sectional view of a second alternative form of the orifice plate used in the first distributor according to Embodiment 3; FIG. 12 is a conceptual cross-sectional view of a third alternative form of the orifice plate used in the first distributor according to Embodiment 3; FIG. 11 is a conceptual diagram illustrating the relationship between orifice holes and heat transfer tubes in the first distributor according to Embodiment 4; FIG. 11 is a schematic diagram of a heat exchanger according to Embodiment 5; FIG. 11 is an explanatory diagram of refrigerant flow paths of a heat exchanger according to Embodiment 5; FIG. 11 is a schematic diagram of a modification of the heat exchanger according to Embodiment 5; FIG. 2 is a first schematic diagram showing the relationship between heat exchangers and outdoor fans according to Embodiments 1 to 5; FIG. 4 is a second schematic diagram showing the relationship between the heat exchanger and the outdoor fan according to Embodiments 1 to 5; FIG. 2 is a first schematic diagram showing the relationship between heat exchangers and indoor fans according to Embodiments 1 to 5; FIG. 4 is a second schematic diagram showing the relationship between the heat exchangers and indoor fans according to Embodiments 1 to 5; FIG. 4 is a third schematic diagram showing the relationship between the heat exchangers and indoor fans according to Embodiments 1 to 5; FIG. 4 is a fourth schematic diagram showing the relationship between the heat exchangers and indoor fans according to Embodiments 1 to 5;

Hereinafter, embodiments for carrying out the present disclosure will be described with reference to the drawings. Here, in the following drawings including FIG. 1, the same reference numerals denote the same or corresponding parts, and are common throughout the embodiments described below. The forms of the constituent elements shown in the entire specification are merely examples, and are not limited to the forms described in the specification.

Embodiment 1.
FIG. 1 is a configuration diagram of an air conditioner 10 according to Embodiment 1. FIG. In FIG. 1, the dotted arrow indicates the direction in which the refrigerant flows during the cooling operation of the air conditioner 10, and the solid arrow indicates the direction in which the refrigerant flows during the heating operation of the air conditioner 10. It is. Referring to FIG. 1, the configuration and operation of an air conditioner 10 having one outdoor heat exchanger 5 and one indoor heat exchanger 3, such as a room air conditioner for home use or a packaged air conditioner for stores or offices. will be explained.

[Configuration of air conditioner 10]
The air conditioner 10 has a compressor 1, a flow path switching device 2, an indoor heat exchanger 3, a pressure reducing device 4, and an outdoor heat exchanger 5, which are connected by piping to form a first It constitutes a refrigerant circuit in which a refrigerant, which is a working fluid, circulates. The air conditioner 10 further has an indoor fan 7 that blows air to the indoor heat exchanger 3 and an outdoor fan 6 that blows air to the outdoor heat exchanger 5 .

The compressor 1 is a fluid machine that compresses and discharges the sucked refrigerant. The flow path switching device 2 is, for example, a four-way valve, and is a device that switches the flow path of the refrigerant between the cooling operation and the heating operation of the air conditioner 10 under the control of a control device (not shown). The indoor heat exchanger 3 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the indoor air supplied by the indoor blower 7 . The indoor heat exchanger 3 functions as a condenser during heating operation, and functions as an evaporator during cooling operation.

The decompression device 4 is, for example, an expansion valve, and is a device that decompresses the refrigerant. The decompression device 4 can use an electronic expansion valve whose opening is controlled by a control device (not shown). The outdoor heat exchanger 5 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the air that is the second working fluid supplied by the outdoor fan 6 . The outdoor heat exchanger 5 functions as an evaporator during heating operation, and functions as a condenser during cooling operation.

[Operation of air conditioner 10]
Next, the operating state of the air conditioner 10 during heating operation will be described along the flow of the refrigerant with reference to FIG. The high-temperature and high-pressure gas refrigerant compressed by the compressor 1 reaches the point A after passing through the channel switching device 2 . When the gas refrigerant passes through the indoor heat exchanger 3 after passing through the point A, the indoor heat exchanger 3 acts as a condenser, and the gas refrigerant is cooled by the air flowing by the indoor fan 7 and is liquefied at the point B to reach

The liquefied liquid refrigerant passes through the decompression device 4 and reaches a two-phase refrigerant state in which low-temperature and low-pressure gas refrigerant and liquid refrigerant are mixed, and reaches point C. After that, the two-phase refrigerant that has passed through point C flows through the outdoor heat exchanger 5 and causes the outdoor heat exchanger 5 to act as an evaporator. reach. The gas refrigerant that has passed point D passes through the flow switching device 2 and returns to the compressor 1 . The air conditioner 10 performs a heating operation for heating indoor air by this refrigerant cycle.

Next, using FIG. 1, the operating state of the air conditioner 10 during cooling operation will be described along the flow of the refrigerant. During the cooling operation of the air conditioner 10, the flow direction of the refrigerant is switched using the flow path switching device 2 so that the flow of the refrigerant flows in the opposite direction. The high-temperature and high-pressure gas refrigerant compressed by the compressor 1 passes through the channel switching device 2 and reaches a point D. As shown in FIG. Then, when the gas refrigerant passes through the outdoor heat exchanger 5 after passing through the point D, the outdoor heat exchanger 5 acts as a condenser, and the gas refrigerant is cooled and liquefied by the air flowing by the outdoor fan 6 to point C to reach

The liquefied liquid refrigerant passes through the decompression device 4 and reaches point B in a two-phase refrigerant state in which low-temperature and low-pressure gas refrigerant and liquid refrigerant are mixed. After that, the two-phase refrigerant that has passed through point B flows through the interior of the indoor heat exchanger 3, causing the indoor heat exchanger 3 to act as an evaporator. reach. The gas refrigerant that has passed through point A passes through the flow switching device 2 and returns to the compressor 1 . The air conditioner 10 performs a cooling operation for cooling the indoor air by this refrigerant cycle.

[Heat exchanger 50]
FIG. 2 is a schematic diagram of the heat exchanger 50 according to the first embodiment. The arrows shown in FIG. 2 indicate the direction in which the coolant flows. 2, the horizontal axis indicates the wind speed of the air passing through the heat exchanger 50, and the vertical axis indicates the height of the heat exchanger 50. As shown in FIG. Also, the solid line in FIG. 2 indicates the amount of heat in the air. Next, the heat exchanger 50 according to Embodiment 1 will be described with reference to FIG. In the following description, the heat exchanger 50 will be described as a configuration when it is used as the outdoor heat exchanger 5 functioning as an evaporator when the air conditioner 10 is used for heating operation. Note that the heat exchanger 50 is not limited to being used as the outdoor heat exchanger 5 in the air conditioner 10, and can also be used as the indoor heat exchanger 3.

As shown in FIG. 2, the heat exchanger 50 has a heat exchange section 50a, a first distributor 20, a second distributor 30, and a header 80. The first distributor 20 and the second distributor 30 may be called headers.

(Heat exchange portion 50a)
The heat exchanging portion 50a exchanges heat between the air existing around the heat exchanging portion 50a and the refrigerant flowing inside the heat exchanging portion 50a. The heat exchange section 50 a is arranged between the first distributor 20 and the second distributor 30 in the flow of refrigerant flowing through the heat exchanger 50 . Also, the heat exchange portion 50 a is arranged between the second distributor 30 and the header 80 in the flow of refrigerant flowing through the heat exchanger 50 . The heat exchange section 50a has a plurality of heat transfer tubes 12 and a heat transfer promoting member 13 connecting the heat transfer tubes 12 adjacent to each other.

Each of the plurality of heat transfer tubes 12 is formed in a tubular shape and circulates the refrigerant inside. Each of the plurality of heat transfer tubes 12 is formed to extend in the first direction (X-axis direction). Each of the plurality of heat transfer tubes 12 is arranged at intervals and arranged in parallel in the axial direction (Z-axis direction), which is the extending direction of the first distributor 20 and the second distributor 30 .

The axial direction (Z-axis direction), which is the extending direction of the first distributor 20 and the second distributor 30, is the second direction, and the second direction is the direction crossing the first direction. The plurality of heat transfer tubes 12 are vertically spaced apart from each other in the second direction. Adjacent heat transfer tubes 12 among the plurality of heat transfer tubes 12 are arranged to face each other. Between two adjacent heat transfer tubes 12 among the plurality of heat transfer tubes 12, a gap is formed as an air flow path.

In the heat exchanger 50, the extending direction of the plurality of heat transfer tubes 12, which is the first direction, is the horizontal direction. However, the extending direction of the plurality of heat transfer tubes 12, which is the first direction, is not limited to the horizontal direction, and may be a direction inclined with respect to the horizontal direction. In the heat exchanger 50, the arrangement direction of the plurality of heat transfer tubes 12, which is the second direction, is the vertical direction. However, the direction in which the plurality of heat transfer tubes 12 are arranged is not limited to the vertical direction, and may be inclined with respect to the vertical direction.

The heat transfer tube 12 is, for example, a circular tube with a circular cross-sectional shape or an elliptical tube with an elliptical shape. The heat transfer tubes 12 are not limited to circular tubes and elliptical tubes, and may be flat tubes in which a plurality of flow paths are formed.

Adjacent heat transfer tubes 12 among the plurality of heat transfer tubes 12 are connected to each other by heat transfer promoting members 13 . The heat transfer promoting member 13 is, for example, plate fins or corrugated fins. The heat transfer promoting member 13 improves the efficiency of heat exchange between air and refrigerant. The plurality of heat transfer promoting members 13 are arranged at intervals in the heat exchanging portion 50 a and are arranged in parallel in the extending direction (X-axis direction) of the heat transfer tubes 12 . When the heat transfer promoting members 13 are plate fins, each of the plurality of heat transfer tubes 12 penetrates the plurality of heat transfer promoting members 13 .

It should be noted that the heat exchange section 50a is not limited to having the heat transfer tube 12 and the heat transfer promoting member 13. For example, the heat exchange section 50a may have a plurality of heat transfer tubes 12 and may not have the heat transfer promoting member 13 that connects the adjacent heat transfer tubes 12 to each other.

As shown in FIG. 2, the heat exchange section 50a has an auxiliary heat exchange section 5a positioned upstream of the circulating refrigerant, and a main heat exchange section 5b positioned downstream of the circulating refrigerant.

The auxiliary heat exchange section 5a has the remaining heat transfer tubes 12 among the plurality of heat transfer tubes 12 that do not constitute the main heat exchange section 5b. The auxiliary heat exchange section 5 a is connected to the first distributor 20 at one end in the extending direction (X-axis direction) of the heat transfer tubes 12 and connected to the second distributor 30 at the other end. In addition, the auxiliary heat exchange section 5 a and the second distributor 30 are connected by a pipe 300 . That is, each of the plurality of heat transfer tubes 12 constituting the auxiliary heat exchange section 5a has one end connected to the first distributor 20 in the first direction (X-axis direction), and the other end connected to the first distributor 20. It is connected to the second distributor 30 via a pipe 300 .

The main heat exchange section 5b has more than half of the heat transfer tubes 12 among the plurality of heat transfer tubes 12. The main heat exchange portion 5b is connected to the second distributor 30 at one end in the extending direction (X-axis direction) of the heat transfer tubes 12, and is connected to the header 80 at the other end. More specifically, each of the plurality of heat transfer tubes 12 constituting the main heat exchange section 5b has one end connected to the second distributor 30 in the first direction (X-axis direction), and the other end connected to the second distributor 30. The ends are connected with headers 80 .

The main heat exchange section 5b includes an upper main heat exchange section 5b1, a middle upper main heat exchange section 5b2, a middle lower main heat exchange section 5b3, and a lower main heat exchange section 5b4. The main heat exchange section 5b is also a general term for the upper main heat exchange section 5b1, the intermediate upper main heat exchange section 5b2, the intermediate lower main heat exchange section 5b3, and the lower main heat exchange section 5b4.

The upper main heat exchange portion 5b1 is a portion located at the upper portion in the vertical direction (Z-axis direction) of the main heat exchange portion 5b, and the middle upper main heat exchange portion 5b2 and the middle lower side are located in the center portion in the direction of gravity. It is a portion located above the main heat exchange portion 5b3. The upper main heat exchange portion 5b1 is a portion of the main heat exchange portion 5b where the heat transfer tubes 12 forming the upper main heat exchange portion 5b1 are connected to the upper second distributor 31 described later. The vertical direction (Z-axis direction) of the main heat exchange portion 5b is also the direction of gravity.

The middle upper main heat exchange portion 5b2 is a portion located in the central portion in the vertical direction (Z-axis direction) of the main heat exchange portion 5b, and is located lower than the upper main heat exchange portion 5b1 in the direction of gravity. It is a portion located above the middle and lower main heat exchange portion 5b3 in the direction. The middle upper main heat exchange portion 5b2 is a portion of the main heat exchange portion 5b where the heat transfer tubes 12 forming the middle upper main heat exchange portion 5b2 are connected to the later-described middle upper second distributor 32 .

The middle-lower main heat exchange portion 5b3 is a portion positioned in the center in the vertical direction (Z-axis direction) of the main heat-exchange portion 5b, and is positioned lower than the middle-upper main heat exchange portion 5b2 in the gravitational direction. , which is located above the lower main heat exchange portion 5b4 in the direction of gravity. The middle and lower main heat exchange section 5b3 is a portion of the main heat exchange section 5b where the heat transfer tubes 12 forming the middle and lower main heat exchange section 5b3 are connected to the later-described middle and lower second distributor 33 .

The middle upper main heat exchange section 5b2 and the middle lower main heat exchange section 5b3 are also referred to as the central main heat exchange section. The center side main heat exchange portion is arranged between the upper side main heat exchange portion 5b1 and the lower side main heat exchange portion 5b4 in the vertical direction (Z-axis direction) of the main heat exchange portion 5b. The center-side main heat exchange section is located on the center side in the vertical direction (Z-axis direction) of the main heat exchange section 5b, and is located on the center side in the gravitational direction (Z-axis direction).

The lower main heat exchange section 5b4 is a portion located below the main heat exchange section 5b in the vertical direction (Z-axis direction), and is positioned in the direction of gravity. This is the portion located below 5b3. The lower main heat exchange portion 5b4 is a portion of the main heat exchange portion 5b where the heat transfer pipes 12 forming the lower main heat exchange portion 5b4 are connected to a second lower distributor 34 described later. The main heat exchange portion 5b and the auxiliary heat exchange portion 5a are thermally separated by a space.

(First distributor 20)
The first distributor 20 is provided on the refrigerant inflow side of the auxiliary heat exchange section 5a when the heat exchanger 50 functions as an evaporator. The first distributor 20 is connected to one end in the extension direction (X-axis direction) of the plurality of heat transfer tubes 12 that constitute the auxiliary heat exchange section 5a. The first distributor 20 is connected to the heat transfer tubes 12 of the auxiliary heat exchange section 5a so that the inside of the first distributor 20 and the pipeline of the heat transfer tubes 12 communicate with each other. The first distributor 20 is arranged on the opposite side of the second distributor 30 via the plurality of heat transfer tubes 12 forming the auxiliary heat exchange section 5a in the refrigerant flow.

The first distributor 20 is elongated so as to extend along the arrangement direction (Z-axis direction) of the plurality of heat transfer tubes 12 . The first distributor 20 is formed to extend in the vertical direction (Z-axis direction) and distributes the refrigerant to the plurality of heat transfer tubes 12 . In the heat exchanger 50 , the first distributor 20 functions as a distribution mechanism that distributes the refrigerant flowing into the auxiliary heat exchange section 5 a of the heat exchange section 50 a to the plurality of heat transfer tubes 12 .

An inflow pipe 201 is provided in the first distributor 20 . The inflow pipe 201 is a pipe for causing the refrigerant distributed to the plurality of heat transfer pipes 12 to flow into the heat exchanger 50 . Note that the inflow pipe 201 is a pipe that constitutes a refrigerant flow path between the heat exchanger 50 and the decompression device 4 . A detailed structure of the first distributor 20 will be described later.

(Second distributor 30)
The second distributor 30 is provided on the refrigerant inflow side of the main heat exchange section 5b when the heat exchanger 50 functions as an evaporator. The second distributor 30 is provided on the refrigerant outflow side of the auxiliary heat exchange section 5a when the heat exchanger 50 functions as an evaporator. The second distributor 30 is connected to the main heat exchange section 5b and distributes the refrigerant flowing out of the auxiliary heat exchange section 5a to the plurality of heat transfer tubes 12 that constitute the main heat exchange section 5b.

The second distributor 30 is connected to one end in the extending direction (X-axis direction) of the plurality of heat transfer tubes 12 that constitute the main heat exchange section 5b. The second distributor 30 is connected to the heat transfer tubes 12 of the main heat exchange section 5b so that the inside of the second distributor 30 and the pipeline of the heat transfer tubes 12 communicate with each other. The second distributor 30 is arranged on the opposite side of the header 80 via the plurality of heat transfer tubes 12 forming the main heat exchange portion 5b in the flow of the refrigerant. Further, the second distributor 30 is connected via piping 300 to a plurality of heat transfer tubes 12 that constitute the auxiliary heat exchange section 5a.

The second distributor 30 is elongated so as to extend along the arrangement direction (Z-axis direction) of the plurality of heat transfer tubes 12 . The second distributor 30 is formed to extend in the vertical direction (Z-axis direction) and distributes the refrigerant to the plurality of heat transfer tubes 12 . In the heat exchanger 50 , the second distributor 30 functions as a distribution mechanism that distributes the refrigerant flowing into the main heat exchange section 5 b of the heat exchange section 50 a to the plurality of heat transfer tubes 12 .

The second distributor 30 includes an upper second distributor 31 , a middle upper second distributor 32 , a middle lower second distributor 33 , and a lower second distributor 34 . The second distributor 30 is also a general term for the upper second distributor 31 , middle upper second distributor 32 , middle lower second distributor 33 , and lower second distributor 34 . In FIG. 2, the four second distributors 30 from the upper second distributor 31 to the lower second distributor 34 are configured, but the number of the second distributors 30 may be four as long as it is plural. is not limited to

The upper second distributor 31 is positioned above the second distributor 30 in the vertical direction (Z-axis direction), and includes a middle upper second distributor 32 positioned at the center in the direction of gravity and a middle lower second distributor 32 . It is positioned above the second distributor 33 . The upper second distributor 31 is connected to the heat transfer tubes 12 that constitute the upper main heat exchange section 5b1.

The middle-upper second distributor 32 is positioned at the central portion in the vertical direction (Z-axis direction) of the second distributor 30, and is positioned lower than the upper second distributor 31 in the direction of gravity. , and is positioned above the second distributor 33 on the middle and lower side. The middle-upper second distributor 32 is connected to the heat transfer tubes 12 that constitute the middle-upper main heat exchange section 5b2.

The middle-lower second distributor 33 is positioned at the central portion in the vertical direction (Z-axis direction) of the second distributor 30, and is positioned lower than the middle-upper second distributor 32 in the direction of gravity. It is located above the second lower distributor 34 in the direction of gravity. The middle lower side second distributor 33 is connected to the heat transfer tubes 12 that constitute the middle lower side main heat exchange section 5b3.

The lower second distributor 34 is positioned below the second distributor 30 in the vertical direction (Z-axis direction), and the middle upper second distributor 32 and the middle lower side are positioned in the center portion in the direction of gravity. It is positioned below the second distributor 33 . The lower second distributor 34 is connected to the heat transfer tubes 12 that constitute the lower main heat exchange section 5b4.

The auxiliary heat exchange section 5a and the second distributor 30 are connected by the pipe 300 as described above. The piping 300 includes an upper piping 301 , a middle upper piping 302 , a middle lower piping 303 and a lower piping 304 . The piping 300 is also a general term for the upper piping 301 , the middle upper piping 302 , the middle lower piping 303 and the lower piping 304 .

The upper pipe 301 is a pipe that connects the auxiliary heat exchange section 5 a and the upper second distributor 31 . The upper pipe 301 communicates the lower space 21 a of the first distributor 20 and the inside of the upper second distributor 31 via the heat transfer pipes 12 . The middle upper pipe 302 is a pipe that connects the auxiliary heat exchange section 5 a and the middle upper second distributor 32 . The middle upper pipe 302 communicates the upper space 21 b of the first distributor 20 with the inside of the middle upper second distributor 32 via the heat transfer pipes 12 .

The middle-lower pipe 303 is a pipe that connects the auxiliary heat exchange section 5 a and the middle-lower second distributor 33 . The middle-lower pipe 303 communicates the upper space 21 b of the first distributor 20 with the inside of the second middle-lower distributor 33 via the heat transfer pipes 12 . The lower pipe 304 is a pipe that connects the auxiliary heat exchange section 5 a and the lower second distributor 34 . The lower pipe 304 communicates the lower space 21 a of the first distributor 20 with the inside of the second lower distributor 34 via the heat transfer pipes 12 . The number of pipes 300 is not limited to four, and may be the same number as the number of second distributors 30 .

(Header 80)
The header 80 is connected to the other ends in the extending direction (X-axis direction) of the plurality of heat transfer tubes 12 forming the main heat exchange section 5b. The header 80 is connected to the heat transfer tubes 12 of the main heat exchange section 5b so that the inside of the header 80 and the inside of the heat transfer tubes 12 communicate with each other. The header 80 is elongated to extend along the arrangement direction (Z-axis direction) of the plurality of heat transfer tubes 12 .

In the heat exchanger 50, the header 80 functions as a merging mechanism for merging the refrigerants flowing out from the plurality of heat transfer tubes 12 of the main heat exchange section 5b. In the heat exchanger 50, the header 80 functions as a merging mechanism for merging the refrigerants flowing out from the heat exchange section 50a.

The header 80 is provided with an outflow pipe 801 . The outflow pipe 801 is a pipe for discharging from the heat exchanger 50 the refrigerant that has flowed out from the plurality of heat transfer pipes 12 and merged.

[Example of operation of heat exchanger 50]
The operation of the heat exchanger 50 according to Embodiment 1 will be described by taking as an example the operation when the heat exchanger 50 functions as the evaporator of the air conditioner 10 . The gas-liquid two-phase refrigerant decompressed by the decompression device 4 flows into the heat exchanger 50 that functions as an evaporator. At this time, the refrigerant flows from the first distributor 20 of the heat exchanger 50, flows through the passages in the plurality of heat transfer tubes 12, absorbs heat, and evaporates. After that, the refrigerant flows out from the header 80 and is sucked into the compressor 1 via the flow switching device 2 .

An operation example of the heat exchanger 50 will be described in more detail using FIG. In the heat exchanger 50, refrigerant flows through the first distributor 20, the auxiliary heat exchange section 5a, the second distributor 30, the main heat exchange section 5b, and the header 80 in this order. When the dryness x, which is an expression indicating the mass velocity ratio of the gas to the total mass velocity of the gas-liquid two-phase refrigerant, is used, the refrigerant flowing through the heat exchanger 50 constituting the outdoor heat exchanger 5 has a dryness x of x = 0.05 to 0.30, and flows into the first distributor 20 from the inflow pipe 201 in the drawing.

The gas-liquid two-phase refrigerant that has passed through the inflow pipe 201 passes through an insertion surface portion 25 into which the heat transfer pipe 12 is inserted, a facing surface 27a (see FIG. 4) facing the end surface of the heat transfer pipe 12, a lid 41, a lid 42, and an orifice. It flows into the first distributor 20 constituted by the plate 91 . A detailed configuration of the first distributor 20 will be described later. Inside the first distributor 20 , the orifice plate 91 regulates the flow of refrigerant so that gas-rich two-phase gas-liquid refrigerant exists in the lower space 21 a located below the orifice plate 91 . Inside the first distributor 20 , the orifice plate 91 adjusts the flow of the refrigerant so that the liquid-rich two-phase gas-liquid refrigerant exists in the upper space 21 b located above the orifice plate 91 . The gas-liquid two-phase refrigerant is distributed to the heat transfer tubes 12 communicating with the lower space 21a and the heat transfer tubes 12 communicating with the upper space 21b, and flows through the auxiliary heat exchange section 5a, which is a part of the outdoor heat exchanger 5. flow.

At this time, heat is exchanged between the gas-liquid two-phase refrigerant flowing through the heat transfer tubes 12 of the auxiliary heat exchange section 5a and the air flowing by the outdoor fan 6 (see FIG. 1). By exchanging heat between the gas-liquid two-phase refrigerant and the air, the liquid refrigerant in the gas-liquid two-phase refrigerant evaporates, and the ratio of the gas mass velocity to the total mass velocity changes. , and finishes passing through the auxiliary heat exchange section 5a.

The gas-liquid two-phase refrigerant that has passed through the auxiliary heat exchange section 5 a flows to the second distributor 30 via the pipe 300 . More specifically, a part of the refrigerant that has passed through the lower space 21a of the first distributor 20 passes through the heat transfer pipes 12 and the upper piping 301 that constitute the auxiliary heat exchange section 5a, and flows inside the upper second distributor 31. flow to Also, part of the refrigerant that has passed through the lower space 21a of the first distributor 20 passes through the heat transfer pipes 12 and the lower piping 304 that constitute the auxiliary heat exchange section 5a, and enters the lower second distributor 34. flow. Also, part of the refrigerant that has passed through the upper space 21b of the first distributor 20 passes through the heat transfer tubes 12 and the middle upper pipe 302 that constitute the auxiliary heat exchange section 5a, and enters the middle upper second distributor 32. flow. Also, part of the refrigerant that has passed through the upper space 21b of the first distributor 20 passes through the heat transfer pipes 12 and the middle and lower side pipes 303 that constitute the auxiliary heat exchange section 5a, and flows through the middle and lower side second distributor 33. flow inside.

At this time, the dryness x of the gas-liquid two-phase refrigerant flowing through the upper pipe 301, the middle upper pipe 302, the middle lower pipe 303, and the lower pipe 304 is in the range of 0.05 to 0.60. It can be done to some extent. The value of the dryness x varies depending on the ratio of the auxiliary heat exchange section 5a to the entire heat exchange section 50a, the air volume passing through the auxiliary heat exchange section 5a, or the pressure loss from the inflow pipe 201 to the pipe 300. do.

The gas-liquid two-phase refrigerant flowing into the upper second distributor 31 to the lower second distributor 34 is distributed into four branches, respectively, and the main heat exchange section 5b as a whole is distributed into a total of 16 branches to each heat transfer tube 12 flow into The gas-liquid two-phase refrigerant distributed to 16 branches flows through the main heat exchange section 5b, and heat exchange is performed between the gas-liquid two-phase refrigerant and the air flowing by the outdoor fan 6 (see FIG. 1).

The gas-liquid two-phase refrigerant distributed into four branches by the upper second distributor 31 flows through the upper main heat exchange portion 5b1, and the air flowing by the outdoor fan 6 (see FIG. 1) and the gas-liquid two-phase refrigerant exchange heat. I do. The gas-liquid two-phase refrigerant distributed into four branches by the middle-upper second distributor 32 flows through the middle-upper main heat exchange section 5b2, and the air flowing by the outdoor fan 6 (see FIG. 1) and the gas-liquid two-phase refrigerant are mixed. heat exchange. The gas-liquid two-phase refrigerant distributed into four branches by the middle-lower side second distributor 33 flows through the middle-lower side main heat exchange portion 5b3, and the air and the gas-liquid two-phase refrigerant flowing by the outdoor fan 6 (see FIG. 1) and perform heat exchange. The gas-liquid two-phase refrigerant distributed into four branches by the lower second distributor 34 flows through the lower main heat exchange portion 5b4, and the air and the gas-liquid two-phase refrigerant flowing by the outdoor fan 6 (see FIG. 1) are mixed. heat exchange.

Here, the amount of heat of the air passing through the upper main heat exchange portion 5b1 to the lower main heat exchange portion 5b4 varies depending on the magnitude of the wind speed distributed in the height direction as shown on the left side of FIG. The middle upper main heat exchange portion 5b2 and the middle lower main heat exchange portion 5b3, in which the heat quantity of the air is larger than the other portions, are smaller in the heat quantity of the air than the middle upper main heat exchange portion 5b2, and the middle lower main heat exchange portion 5b3. More liquid refrigerant can be evaporated than in the upper main heat exchange portion 5b1 and the lower main heat exchange portion 5b4.

Therefore, in the heat exchanger 50, the middle upper main heat exchange portion 5b2 is connected to the middle upper second distributor 32, and the middle upper second distributor 32 adjusts the liquid-rich gas-liquid two-phase refrigerant. It is connected to the upper space 21 b of the 1 distributor 20 . That is, the heat exchanger 50 includes the middle upper main heat exchange section 5b2 that evaporates a large amount of liquid refrigerant via the middle upper second distributor 32, and the first distributor 20 that contains liquid-rich gas-liquid two-phase refrigerant. It connects with the upper space 21b.

In the heat exchanger 50, the lower middle main heat exchange portion 5b3 is connected to the second middle lower distributor 33, and the second middle lower distributor 33 converts the liquid-rich gas-liquid two-phase refrigerant. It is connected to the upper space 21b of the first distributor 20 to be adjusted. That is, the heat exchanger 50 includes a middle-lower main heat exchange section 5b3 that evaporates a large amount of liquid refrigerant via the middle-lower second distributor 33, and a first distributor that contains liquid-rich gas-liquid two-phase refrigerant. 20 is connected to the upper space 21b.

The refrigerant passing through the main heat exchange portion 5b is in a state of gas refrigerant in which all of the liquid refrigerant is vaporized by heat exchange with the air, or in a gas-liquid state in which most of the liquid refrigerant is vaporized and the dryness x is 0.85 or more. It becomes a two-phase refrigerant and flows out to the header 80 . The 16-branched refrigerant in the main heat exchange portion 5 b joins in the header 80 and flows out of the heat exchanger 50 through the outflow pipe 801 .

In the heat exchanger 50, for example, the refrigerant is branched into four at the first distributor 20 and flows through a part of the evaporator (auxiliary heat exchange section 5a), then from the upper second distributor 31 to the lower second distributor. After being branched into 16 via the evaporator 34, it is configured to flow through a part of the evaporator (main heat exchange section 5b). Note that the heat exchanger 50 is not limited to this configuration. In the heat exchanger 50, the number of branches of the auxiliary heat exchange section 5a and the main heat exchange section 5b may differ from the above embodiment.

(Detailed Configuration of First Distributor 20)
FIG. 3 is a schematic diagram of first distributor 20 according to the first embodiment. 4 is a perspective view of the first distributor 20 according to Embodiment 1. FIG. FIG. 5 is a cross-sectional view perpendicular to the direction in which the main body 20a extends along line AA shown in FIG. FIG. 6 is a cross-sectional view perpendicular to the direction in which the body portion 20a extends along line BB shown in FIG. FIG. 7 is a cross-sectional view perpendicular to the extending direction of the main body portion 20a along line CC shown in FIG.

FIG. 4 omits illustration of the lid 41 in order to explain the internal structure of the first distributor 20 . The X-axis direction shown in FIG. 4 is the direction in which the heat transfer tubes 12 extend, and the Z-axis direction is the direction in which the body portion 20a of the first distributor 20 extends. The Z-axis direction is also the direction in which the heat transfer tubes 12 are arranged. The Y-axis direction shown in FIG. 4 is a direction perpendicular to the X-axis direction and the Z-axis direction. The first distributor 20 will be described with reference to FIGS. 3 to 7. FIG. The first distributor 20, as shown in FIG. 3, has a body portion 20a and an inflow pipe 201 attached to the body portion 20a.

(Body portion 20a)
The body portion 20a is a member formed in a long tubular shape with both ends closed, and a space is formed inside. The main body part 20a of the first distributor 20 is in a state in which the central axis of the longitudinal direction (Z-axis direction) of the first distributor 20 is oriented vertically, or in which the central axis of the longitudinal direction of the first distributor 20 is oriented vertically. It is installed in a tilted state within a range having a vector component. An inlet 44 and an internal space 21 are formed in the body portion 20a.

The inflow port 44 is an inflow port that is connected to the inflow pipe 201 and into which the refrigerant flows from the inflow pipe 201 . The internal space 21 communicates with the inner space of the heat transfer tube 12 and the inner space of the inflow pipe 201 , and is a space through which the refrigerant flowing from the inflow port 44 flows upward through the inflow pipe 201 .

The body part 20 a has a first part 23 , a second part 24 ,

lids

41 and 42 , and an orifice plate 91 . The first part 23 and the second part 24 are arranged so as to face each other in the direction in which the heat transfer tubes 12 extend (the X-axis direction). The body portion 20a of the first distributor 20 includes a first component 23 having an insertion surface portion 25 and a side surface portion 26, which will be described later, and a second component 24, which is a facing surface portion. 24 are combined to form a cylindrical shape.

As shown in FIG. 4, the body portion 20a is formed in a tubular shape by combining a first part 23 and a second part 24, and as shown in FIG. Both ends of the two parts 24 in the longitudinal direction (Z-axis direction) are closed with

lids

41 and 42 . The body portion 20 a is formed in a columnar shape by combining the first part 23 , the second part 24 , and the

lids

41 and 42 .

The first part 23 is an elongated member, and has a U-shaped cross section perpendicular to the longitudinal direction (Z-axis direction). A cross section perpendicular to the longitudinal direction (Z-axis direction) of the first distributor 20 including the first component 23 may be referred to as an axis-perpendicular cross section. As shown in FIGS. 4 and 5, the first component 23 has an insertion surface portion 25 forming a U-shaped curved portion and a side surface portion 26 forming a flat portion. Note that the side surface portion 26 is not limited to a flat plate-like portion, and may be, for example, a plate-like portion formed in an arc that draws a gentler curve than the insertion surface portion 25 in an axis-perpendicular cross section. . The insertion surface portion 25 and the two side surface portions 26 are integrally formed.

In a cross section perpendicular to the longitudinal direction (Z-axis direction) of the first component 23, the insertion surface portion 25 is formed in an arc shape, and the side surface portion 26 is formed in a substantially linear shape. At least a part of the insertion surface portion 25 is curved so as to be convex toward the side on which the plurality of heat transfer tubes 12 are arranged in an axis-perpendicular cross section. At least a part of the first component 23 is curved so as to protrude on the side opposite to the second component 24 which is the facing surface portion.

The first part 23 is formed such that two side surface parts 26 face each other in the Y-axis direction. A side surface portion 26 is provided at both ends of each. The side portion 26 is connected to a later-described flat plate portion 28 of the second component 24 . The side surface portion 26 is a wall extending between the insertion surface portion 25 and the flat plate portion 28 of the opposing surface portion that is the second component 24 in the main body portion 20a, and is a portion that connects the insertion surface portion 25 and the flat plate portion 28 . The side surface portion 26 is formed integrally with the insertion surface portion 25 and is joined to the flat plate portion 28 of the opposing surface portion, which is the second component 24 .

A plurality of heat transfer tubes 12 are inserted into the insertion surface portion 25 of the first component 23 . As shown in FIGS. 3 and 4, the insertion surface portion 25 of the first component 23 is formed with a connection port 43 into which the heat transfer tube 12 is inserted. The connection port 43 is a through hole and is formed in plurality along the longitudinal direction (Z-axis direction) of the first component 23 . A plurality of connection ports 43 into which a plurality of heat transfer tubes 12 are inserted are formed at intervals in the vertical direction in the body portion 20a. The heat transfer tube 12 is inserted into the connection port 43 and penetrates the wall of the first component 23 . The heat transfer tube 12 inserted into the connection port 43 is held by the first component 23 .

The second part 24 is a facing surface portion that faces the insertion surface portion 25 in the direction in which the heat transfer tubes 12 extend, as shown in FIGS. The second part 24 is an elongated member, and has a substantially Ω-shaped cross section perpendicular to the longitudinal direction (Z-axis direction). The second component 24, which is the facing surface portion, includes a flat plate portion 28 connected to the side surface portion 26 and a part of the inner wall forming the inner space 21 of the first distributor 20 in the cross section perpendicular to the axis of the first distributor 20. and a bulging portion 27 that bulges from the flat plate portion 28 toward the surface portion 25 . In other words, the second component 24, which is the facing surface portion, has a bulging portion 27 forming a curved portion and a flat plate portion 28 forming a flat portion. The bulging portion 27 and two flat plate portions 28 located on both sides of the bulging portion 27 in a cross section perpendicular to the longitudinal direction (Z-axis direction) of the second part 24 are integrally formed.

In a cross section perpendicular to the longitudinal direction (Z-axis direction) of the second part 24, the bulging portion 27 is formed in an arc shape, and the flat plate portion 28 is formed in a straight line. In the second part 24, two flat plate parts 28 form the same flat plane F, and flat plates are formed on both ends of the bulging part 27 in a cross section perpendicular to the longitudinal direction (Z-axis direction) of the second part 24, respectively. A section 28 is provided. The same plane F is a plane formed by the Z-axis direction and the Y-axis direction, as shown in FIG. It should be noted that the flat plate portions 28 are not limited to being provided at both ends of the bulging portion 27. For example, the flat plate portions 28 located at both ends of the bulging portion 27 are integrally formed. It may be formed as a single plate-like member.

The bulging portion 27 is a portion in which at least a portion of the second component 24 that is the facing surface portion bulges toward the insertion surface portion 25 in the axis-perpendicular cross section of the first distributor 20 . The bulging portion 27 is provided between two flat plate portions 28 and bulges from the flat plate portion 28 so as to protrude from the side where the insertion surface portion 25 is formed, that is, the side where the heat transfer tubes 12 are arranged. The bulging portion 27 may be configured as a portion in which at least a portion of the flat plate portion 28 bulges toward the insertion surface portion 25 . The bulging portion 27 is formed along the longitudinal direction of the main body portion 20 a , that is, along the longitudinal direction of the second component 24 .

The bulging portion 27 has a facing surface 27 a that faces the inner wall of the insertion surface portion 25 . Although the bulging portion 27 is formed in a U shape in FIG. 4, the shape of the bulging portion 27 is not limited to this shape. The bulging portion 27 may be formed so as to protrude from the flat plate portion 28 toward the side where the insertion surface portion 25 is formed, that is, toward the side where the heat transfer tubes 12 are arranged. good.

At least one inflow port through which the coolant flows into the internal space 21 is formed in the bulging portion 27 of the second part 24 which is the facing surface portion. The inflow port 44 is a through hole into which the inflow pipe 201 is inserted. The inflow pipe 201 is inserted into the inflow port 44 and penetrates the wall of the second part 24 . The inflow tube 201 inserted into the inflow port 44 is held by the second part 24 .

The inflow port 44 is formed in the internal space 21 of the main body 20a at a position facing the lowermost heat transfer tube 12 among the plurality of heat transfer tubes 12 . Alternatively, as shown in FIG. 3 , the inlet 44 is formed so as to be positioned below the lowermost heat transfer tube 12 among the plurality of heat transfer tubes 12 in the internal space 21 of the main body 20a. there is

The main body portion 20a is formed so that the bulging portion 27 is positioned between two side surface portions 26 facing each other. The body portion 20 a has an internal space 21 formed by an insertion surface portion 25 , two side surface portions 26 , a bulging portion 27 , two flat plate portions 28 , a lid 41 , and an inner wall surface of the lid 42 . As shown in FIG. 4, the internal space 21 is formed in a substantially U shape in a vertical cross section with respect to the longitudinal direction (Z-axis direction) of the body portion 20a.

A representative manufacturing method of the main body 20a is as follows. The first part 23 is formed with a connection port 43 that serves as an insertion port for the heat transfer tube 12, and is formed so that a cross section perpendicular to the longitudinal direction has an arc shape. Therefore, the first component 23 is formed by press work for forming the connection port 43 and bending work for forming the curved surface, and is formed as a semicircular pressed plate component.

The second part 24 forms an inflow port 44 that serves as a connection port for the inflow pipe 201, and then forms a bulging portion 27 having an arc-shaped cross section perpendicular to the longitudinal direction. Therefore, the second part 24 is molded by pressing for forming the inlet 44 and bending for forming a curved surface, and is molded as a pressed plate part having the bulging portion 27 .

The manufacturing method of the main body portion 20a is not limited to the molding method described above. For example, after extrusion molding of the body portion 20a in which the first part 23 and the second part 24 are integrated, the body portion 20a is drilled to form the connection port 43 and the inlet port 44, thereby manufacturing the body portion 20a. may Alternatively, the main body portion 20a may be manufactured by combining the first part 23 and the second part 24 formed by press working and extrusion, or may be manufactured by using another means such as electric resistance welding pipe processing. may

The first distributor 20 closes both ends in the longitudinal direction (Z-axis direction) of the first distributor 20 , and defines an internal space 21 together with an insertion surface portion 25 , a second component 24 that is a facing surface portion, and a side surface portion 26 . It has

lids

41 and 42 that form. The

lids

41 and 42 are members that close both ends of the first component 23 and the second component 24 that are formed in a cylindrical shape. The

lids

41 and 42 are plate-shaped. The

lids

41 and 42 close both ends of the body portion 20a in the longitudinal direction (Z-axis direction) so as to form the internal space 21 in the body portion 20a.

As shown in FIGS. 3 and 7, at least one orifice plate 91 is provided inside the main body 20a to divide the internal space 21 of the main body 20a into upper and lower spaces. A lower space 21a positioned below the orifice plate 91 and an upper space 21b positioned above the orifice plate 91 are formed by the orifice plate 91 inside the body portion 20a. An orifice plate 91 is provided inside the body portion 20a, and the internal space 21 is separated by the orifice plate 91 into a lower space 21a and an upper space 21b. In the internal space 21 of the body portion 20 a , the lower space 21 a is a space formed below the orifice plate 91 and the upper space 21 b is a space formed above the orifice plate 91 .

As shown in FIGS. 3 and 7, orifice holes 92 are formed in the orifice plate 91 . The orifice hole 92 is a through hole formed in the orifice plate 91 and allows the upper and lower spaces of the orifice plate 91 to communicate with each other. The internal space 21 of the body portion 20a communicates with the lower space 21a and the upper space 21b through the orifice hole 92 of the orifice plate 91 . In the body portion 20a, the refrigerant flows through the orifice holes 92 of the orifice plate 91, and moves through the orifice holes 92 from the lower space 21a to the upper space 21b. By using the orifice plate 91 having such a configuration, the first distributor 20 can suppress non-uniformity of the gas refrigerant when the flow rate is low.

The upper space 21b of the first distributor 20 passes through the auxiliary heat exchange section 5a and one or more of the plurality of second distributors 30, the middle upper main heat exchange section 5b2, the middle lower main heat exchange section 5b3, and the like. It communicates with a plurality of heat transfer tubes 12 that constitute the central side main heat exchange section. The lower space 21a of the first distributor 20 passes through the auxiliary heat exchange section 5a and one or more of the plurality of other second distributors 30 that do not communicate with the central side main heat exchange section 5b1. and a plurality of heat transfer tubes 12 forming the lower main heat exchange section 5b4.

The orifice plate 91 has one circular orifice hole 92 formed near the center of the orifice plate 91 in FIG. However, the formation position of the orifice hole 92 is not limited to the vicinity of the center of the orifice plate 91 . Also, the number of orifice holes 92 formed is not limited to one, and two or more orifice holes 92 may be formed in the orifice plate 91 . Further, the hole shape of the orifice hole 92 is not limited to a circular shape, and may be, for example, a rectangular shape or an elliptical shape.

As shown in FIG. 3, in the body part 20a, the part forming the lower space 21a is the lower body part 20a1, and the part forming the upper space 21b is the upper body part 20a2. A connection port 43 is formed in each of the lower body portion 20a1 and the upper body portion 20a2. As shown in FIG. 2, two connection ports 43 are formed in each of the upper body portion 20a2 and the lower body portion 20a1, and four connection ports 43 are formed in the body portion 20a as a whole.

A plurality of heat transfer tubes 12 are attached to the lower body portion 20a1, and a plurality of other heat transfer tubes 12 are attached to the upper body portion 20a2. A plurality of heat transfer tubes 12 pass through the connection port 43 of the lower main body portion 20a1, and a plurality of other heat transfer tubes 12 pass through the connection port 43 of the upper main body portion 20a2. Note that the number of connection ports 43 formed in the body portion 20a is not limited to four. The number of connection ports 43 to be formed is determined by the number of heat transfer tubes 12 included in the heat exchange section 50a.

(Inflow pipe 201)
An inflow pipe 201 is attached to the body portion 20a. The inflow pipe 201 is attached to the lower body portion 20a1. The inflow pipe 201 communicates with the internal space 21 of the body portion 20a. The inflow pipe 201 communicates with the lower space 21a. The gas-liquid two-phase refrigerant flowing through the internal space 21 of the main body 20 a flows into the inflow pipe 201 when the heat exchanger 50 functions as an evaporator.

Next, the attachment position of the inflow pipe 201 will be described using FIG. The inflow pipe 201 is located at a position facing the heat transfer tube 12 located at the bottom of the lower space 21a, or at a position where the gas-liquid two-phase refrigerant flows into the space below the heat transfer tube 12 located at the bottom. It is desirable to attach along the direction (X-axis direction) in which the heat pipe 12 extends.

If the installation position of the inflow pipe 201 is set at an intermediate point between the heat transfer tubes 12 in the lower space 21a, an upward flow of the refrigerant and a downward flow of the refrigerant will occur, resulting in a gas-liquid two-phase refrigerant. The flow velocity that flows upward decreases. If the flow velocity of the gas-liquid two-phase refrigerant is lowered, separation between the gas refrigerant and the liquid refrigerant is likely to occur. Therefore, the inflow pipe 201 is desirably attached to the position described above.

Next, the characteristics of the working fluid when using the first distributor 20 of the present embodiment are shown. Because the gas-liquid two-phase refrigerant flowing from the inflow pipe 201 is sequentially discharged to the plurality of heat transfer tubes 12 connected to the first component 23 when flowing vertically upward in the lower space 21a in the first distributor 20. , the upward flow velocity decreases stepwise.

Here, the cross-sectional area of the internal space 21 of the first distributor 20 in the cross-sectional view along line AA shown in FIG. 5 is defined as cross-sectional area A ₁ [m ² ]. Further, the cross-sectional area of the internal space 21 of the first distributor 20 in the cross-sectional view taken along line BB shown in FIG. 6 is defined as cross-sectional area A ₂ [m ² ].

Also, the peripheral length of the cross section of the first distributor 20 forming the cross-sectional area A ₁ is defined as the wetting edge length L ₁ [m]. Also, the peripheral length of the cross section of the first distributor 20 forming the cross-sectional area _A2 is defined as the wet edge length _L2 [m]. Also, the equivalent hydraulic diameter in the cross section of the first distributor 20 forming the cross-sectional area A ₁ is assumed to be the equivalent hydraulic diameter D ₁ [m]. Also, the equivalent hydraulic diameter in the cross section of the first distributor 20 forming the cross-sectional area _A2 is assumed to be the equivalent hydraulic diameter _D2 [m]. Then, the circulation amount of the gas-liquid two-phase refrigerant flowing through the internal space 21 is defined as the circulation amount Gr [kg/s], the dryness is defined as the dryness x [−], and the density is density ρ [kg/m ³ ] and the apparent velocity is defined as velocity u [m/s]. When each value is defined as above, the dimensionless flooding speed j ^* [-] and the flooding constant C _N [-] are calculated by the following relational expressions. In the following formula, the suffix [_N] is N=1 or 2 or 3, the suffix [_G] is gas, and the suffix [_L] is liquid.

Here, if the flooding constant C ₂ [−] in the cross-sectional area A ₂ is less than 0.4, the gas refrigerant and the liquid refrigerant are likely to separate. Therefore, it is preferable to configure the internal space 21 so that the flooding constant C ₂ [-] has a flow velocity of 0.4 or more.

As shown in FIGS. 5 and 6, the body portion 20a of the first distributor 20 is formed with a corner portion 21c and a corner portion 21d. The first distributor 20 may have only one of the

corners

21c and 21d, or may have both the

corners

21c and 21d. The corner 21 c and the corner 21 d are spaces surrounded by the flat plate portion 28 , the bulging portion 27 and the side portion 26 and are part of the internal space 21 . The

corners

21 c and 21 d are spaces near the flat plate portion 28 in the internal space 21 . Surface tension acts between the

corners

21 c and 21 d and the liquid refrigerant due to the surrounding wall surfaces formed by the flat plate portion 28 , the bulging portion 27 , and the side surface portion 26 . Therefore, the first distributor 20 can prevent the liquid refrigerant from falling due to the surface tension acting on the

corners

21c and 21d.

In addition, by providing the

corners

21c and 21d of the first distributor 20, the distance between the heat transfer tubes 12 and the joints 28a between the side surface portion 26 and the flat plate portion 28 can be increased. Therefore, when the side portion 26 and the flat plate portion 28 are connected by brazing, even if the brazing material supplied to the joint portion 28a becomes excessive, the distance between the joint portion 28a and the heat transfer tube 12 is increased. Therefore, the refrigerant flow path in the heat transfer tube 12 is not clogged with the brazing filler metal. In order to improve the joint strength between the side surface portion 26 and the flat plate portion 28, a brazing fillet may be formed at the joint portion 28a between the side surface portion 26 and the flat plate portion 28. FIG. A brazing filler metal fillet is a solidified brazing filler material that is thickly attached to the corners of the joints between members and spreads out from the corners so as to draw a skirt.

FIG. 8 is an explanatory diagram for explaining the action of the bulging portion 27. FIG. In a cross section perpendicular to the longitudinal direction (Z-axis direction) of the main body 20a, a first tangent line P is defined as a tangent line of a portion of the heat transfer tube 12 that is closest to the second component 24, which is the facing surface portion. The first tangent line P is perpendicular to the extending direction (X-axis direction) of the plurality of heat transfer tubes 12 when viewed in a direction parallel to the longitudinal direction (Z-axis direction) of the first distributor 20 and the main body portion 20a. becomes.

A second tangent line Q is defined as a tangent line in contact with the topmost portion 27b of the bulging portion 27 in a cross section perpendicular to the longitudinal direction (Z-axis direction) of the main body portion 20a. A second tangent line Q is a tangent line of a portion of the bulging portion 27 that is closest to the heat transfer tube 12 when viewed in a direction parallel to the longitudinal direction (Z-axis direction) of the first distributor 20 and the main body portion 20a. be. The second tangent line Q is perpendicular to the extending direction (X-axis direction) of the plurality of heat transfer tubes 12 when viewed in a direction parallel to the longitudinal direction (Z-axis direction) of the first distributor 20 and the main body portion 20a. becomes. The first tangent line P and the second tangent line Q are parallel when viewed in a direction parallel to the longitudinal direction (Z-axis direction) of the first distributor 20 and the main body portion 20a.

The top portion 27b is the portion closest to the heat transfer tube 12 in the direction in which the heat transfer tube 12 extends (the X-axis direction), and is the portion that protrudes most from the flat plate portion 28 . That is, the top portion 27b is the portion closest to the connection port 43 in the second component 24 in the direction in which the heat transfer tube 12 extends (the X-axis direction).

A third tangent line R is defined as a tangent line to a portion of the second part 24 that is farthest from the insertion surface portion 25 and forms the internal space 21 in a cross section perpendicular to the longitudinal direction (Z-axis direction) of the main body portion 20a. The third tangent line R contacts the portion of the flat plate portion 28 that forms the inner wall of the internal space 21 when viewed in a direction parallel to the longitudinal direction (Z-axis direction) of the first distributor 20 and the main body portion 20a. line parallel to the first tangent line P and the second tangent line Q;

In the direction in which the heat transfer tube 12 extends (the X-axis direction), the distance between the first tangent line P and the second tangent line Q is defined as a first distance M1, and the distance between the first tangent line P and the third tangent line R is defined as a first distance M1. In the case of two distances M2, the second distance M2 is 1.5 times or more the first distance M1. The first distributor 20 is formed so as to satisfy the relationship of second distance M2≧1.5×first distance M1 in a cross section perpendicular to the longitudinal direction (Z-axis direction) of the main body 20a.

In other words, in the axis-perpendicular cross section of the first distributor 20, the shortest distance from the tip end portion 12b of each of the plurality of heat transfer tubes 12 to the bulging portion 27 is the first distance M1. Further, in the first distributor 20, the distance from the distal end portion 12b of each of the plurality of heat transfer tubes 12 to the position of the flat plate portion 28 in the direction in which the plurality of heat transfer tubes 12 extend is defined as a second distance M2. In such a case, the first distributor 20 is formed so as to satisfy the relationship of second distance M2≧1.5×first distance M1.

In the first distributor 20, the second distance M2 is 1.5 times or more the first distance M1, so that the cross-sectional area _A2 of the internal space 21 can be minimized. In addition, the wet edge length _L2 can be increased. Therefore, the first distributor 20 can reduce the hydraulic equivalent diameter _D2 , and as a result, can also increase the flooding constant _C2 .

FIG. 9 is a diagram showing the relationship between the flooding constant _CN and the height inside the distributor. "Conventional" shown in FIG. 9 indicates a distributor that does not have the first distributor 20 of the present disclosure, and "Embodiment" indicates the first distributor 20 of this embodiment. The "conventional" distributor is a distributor in which the main body has a perfectly circular cross section in a cross section perpendicular to the longitudinal direction (Z-axis direction) of the main body. As shown in FIG. 9, as the height inside the first distributor 20 increases, the gas-liquid two-phase refrigerant is sequentially discharged to the heat transfer tubes 12, so the flooding constant _CN decreases.

In the conventional distributor, since the hydraulic equivalent diameter _D2 of the internal space 21 becomes large, the flooding constant _C2 becomes small and the flooding constant _C2 falls below 0.4, so that the gas refrigerant and the liquid refrigerant cannot be separated. occur. Therefore, in the conventional distributor, only the gas refrigerant is supplied to the top of the height inside the distributor, and the distribution of the gas-liquid two-phase refrigerant becomes uneven, resulting in a decrease in heat exchanger performance. Cheap.

On the other hand, in the first distributor 20 of the present disclosure, since the second distance M2 is 1.5 times or more the first distance M1, the flooding constant _C2 can be increased as described above, The gas-liquid two-phase refrigerant can be distributed while the flooding constant _C2 is set to 0.4 or more. Therefore, the first distributor 20 can prevent separation of the gas refrigerant and the liquid refrigerant, and can suppress insufficient supply of the liquid refrigerant to the upper portion of the first distributor. In addition, the first distributor 20 can prevent the separation of the gas refrigerant and the liquid refrigerant, and in the heat exchange section 50a located downstream of the first distributor 20, the liquid refrigerant is also supplied to the upper portion of the heat exchange section 50a. can supply. Since the heat exchanger 50 has the first distributor 20, the liquid refrigerant can be supplied to the upper portion of the heat exchange section 50a as well, and deterioration of the heat exchanger performance of the heat exchanger 50 can be suppressed.

FIG. 10 is a schematic diagram showing the flow of refrigerant in the first distributor 20 in the heat exchanger 50 of Embodiment 1. FIG. The role of the orifice plate 91 in the first distributor 20 will be described with reference to FIG. The gas-liquid two-phase refrigerant 35 supplied from the inflow pipe 201 becomes a liquid refrigerant that rises while adhering to the inner wall surface of the lower body portion 20a1 in the lower space 21a, and becomes a gas that rises without adhering to the inner wall surface. It becomes a state of refrigerant and a state of dispersed liquid refrigerant particles.

As described with reference to FIG. 9, when the flooding constant _C2 in the first distributor 20 is 0.4 or more, the liquid refrigerant rising while adhering to the wall surface can proceed upward without falling, and the orifice Plate 91 is reached. The liquid refrigerant and gas refrigerant that have reached the orifice plate 91 are divided into a flow that passes through the orifice holes 92 and a flow that does not pass through the orifice holes 92 due to pressure loss caused by passing through the orifice holes 92 .

When passing through a nozzle space such as the orifice hole 92, the gas refrigerant, which has a larger volume than the liquid refrigerant when compared with the same mass, causes a large pressure loss. Therefore, the refrigerant passing through the orifice hole 92 is distributed at a large mass flow rate of the liquid refrigerant with a small pressure loss, and the gas-liquid two-phase refrigerant occupying the upper space 21b accounts for about 50.1% or more of the gas-liquid two-phase refrigerant. 58.0% mass flow rate tends to be a liquid-rich refrigerant. Therefore, in the first distributor 20, in the main body portion 20a, as shown in FIG. The gas-liquid two-phase refrigerant flowing into 12 tends to be a liquid-rich refrigerant with a large liquid refrigerant content. The third and fourth heat transfer tubes 12 from the bottom communicate with the upper space 21b.

The liquid refrigerant and gas refrigerant that do not pass through the orifice holes 92 are divided into four branches by the four heat transfer tubes 12 in the main body 20a as shown in FIG. It flows into the first heat transfer tube 12 . The gas refrigerant, which is difficult to pass through the orifice holes 92 due to the pressure loss caused by passing through the orifice holes 92, is branched into four branches by the four heat transfer tubes 12 in the main body 20a as shown in FIG. In the configuration, it is easy to flow into the first and second heat transfer tubes 12 from below. Therefore, in the first distributor 20, the gas-liquid two-phase refrigerant flowing into the first and second heat transfer tubes 12 from the bottom tends to be a gas-rich refrigerant with a large gas refrigerant content. The first and second heat transfer tubes 12 from the bottom communicate with the lower space 21a.

The orifice hole 92 formed in the orifice plate 91 is a hole corresponding to a Cv value of about 0.05 to 2.0, which is generally treated as a capacity coefficient of a valve or the like. In determining the hole size of the orifice hole 92, for example, in the first distributor 20, R32 refrigerant flows as a gas-liquid two-phase refrigerant having a mass flow rate of 140 [kg/h] and a dryness of 0.10. Consider the case of flowing from pipe 201 into interior space 21 . Further, in the first distributor 20, among the configuration in which the flow of the refrigerant is branched into four branches by the four heat transfer tubes 12, an orifice plate is provided between the second heat transfer tube 12 and the third heat transfer tube 12 from the bottom. Consider the case with 91 . When the R32 refrigerant described above is used and the orifice plate 91 is provided between the second heat transfer tube 12 and the third heat transfer tube 12 from the bottom of the four branches, the orifice hole 92 has a diameter of Φ2.2 [mm ] to Φ6.0 [mm].

[Action and effect of heat exchanger 50]
The heat exchanger 50 according to the present disclosure includes the first distributor 20 that satisfies the relationship of second distance M2≧1.5×first distance M1. The first distributor 20 minimizes the cross-sectional area _A2 of the internal space 21 of the first distributor 20 by setting the second distance M2 to be 1.5 times or more the first distance M1. In addition, the wetting edge length _L2 can be increased. Therefore, the first distributor 20 can reduce the hydraulic equivalent diameter _D2 , and as a result, can also increase the flooding constant _C2 . As a result, the first distributor 20 can separate the liquid refrigerant and the gas refrigerant in the gas-liquid two-phase refrigerant in the first distributor 20 and maintain a flow velocity at which the liquid refrigerant does not drop. Insufficient supply of liquid refrigerant to the upper part of the can be suppressed.

In addition, at least a part of the insertion surface portion 25 is curved so as to be convex toward the side on which the plurality of heat transfer tubes 12 are arranged in an axis-perpendicular cross section. Since the pressure resistance in the first distributor 20 increases as the body portion 20a of the first distributor 20 is closer to a circular shape, the heat exchanger 50 is configured such that the insertion surface portion 25 is formed with the above-described structure. The withstand voltage of the container 20 can be improved.

In addition, the first distributor 20 closes both ends in the longitudinal direction (Z-axis direction) of the first distributor 20, and has an internal space with an insertion surface portion 25, a second component 24 that is a facing surface portion, and a side surface portion 26. It has a lid 41 and a lid 42 forming 21 . Without the

lids

41 and 42 above and below the first distributor 20, the refrigerant leaks to the outside and a closed space cannot be created. The first distributor 20 can be easily closed by closing the upper and lower ends with the

lids

41 and 42 rather than bending the upper and lower ends of the first distributor 20 at right angles and crushing the ends to form a closed space. Space can be formed.

In addition, the first distributor 20 has at least one or more partitions that separate the internal space 21 into an upper space 21b positioned above and a lower space 21a positioned below in the longitudinal direction (Z-axis direction) of the first distributor 20. It has an orifice plate 91 . The orifice plate 91 is formed with an orifice hole 92 which is a through hole and communicates the upper space 21b and the lower space 21a. When passing through a nozzle space such as the orifice hole 92, the gas refrigerant, which has a larger volume than the liquid refrigerant when compared with the same mass, causes a large pressure loss. Therefore, the refrigerant passing through the orifice hole 92 is distributed at a large mass flow rate of liquid refrigerant with a small pressure loss, and the gas-liquid two-phase refrigerant occupying the upper space 21b tends to be a liquid-rich refrigerant. As a result, the first distributor 20 can suppress insufficient supply of liquid refrigerant to the upper portion of the first distributor 20 .

In addition, the inlet 44 is formed in the internal space 21 of the main body 20a at a position facing the lowermost heat transfer tube 12 among the plurality of heat transfer tubes 12 . Alternatively, as shown in FIG. 3 , the inlet 44 is formed so as to be positioned below the lowermost heat transfer tube 12 among the plurality of heat transfer tubes 12 in the internal space 21 of the main body 20a. there is If the installation position of the inflow pipe 201 connected to the inflow port 44 is set at the middle point between the heat transfer tubes 12 in the internal space 21, an upward flow of the refrigerant and a downward flow of the refrigerant will occur. , the flow velocity at which the gas-liquid two-phase refrigerant flows upward decreases. If the flow velocity of the gas-liquid two-phase refrigerant is lowered, separation between the gas refrigerant and the liquid refrigerant is likely to occur. Therefore, the formation position of the inflow port 44 to which the inflow pipe 201 is connected is desirably formed at the position described above, and the generation of the refrigerant flow that is divided into the upward flow of the refrigerant and the downward flow of the refrigerant can be suppressed. .

Further, the first distributor 20 includes a first component 23 having an insertion surface portion 25 and a side surface portion 26, and a second component 24 which is a facing surface portion, and the first component 23 and the second component 24 are combined. Therefore, it is formed in a cylindrical shape. The first distributor 20 can be made by extrusion molding a cylinder in which the insertion surface portion 25, the side surface portion 26, and the opposing surface portion are all integrated. It is expensive to manufacture because it needs to be Since the first distributor 20 is composed of two halves, the first part 23 and the second part 24, the first part 23 and the second part 24 can be manufactured by press working, and the manufacturing cost can be reduced. You can keep it cheap.

Further, the main body portion 20a of the first distributor 20 is in a state in which the central axis of the longitudinal direction (Z-axis direction) of the first distributor 20 is vertical, or the central axis of the longitudinal direction of the first distributor 20 is vertical. It is installed in a tilted state within a range having a directional vector component. The first distributor 20 is a distributor that extends in the vertical direction (the Z-axis direction), but by providing the above-described configuration, it is possible to suppress insufficient supply of liquid refrigerant to the upper portion of the first distributor 20 .

In addition, the upper space 21b of the first distributor 20 passes through the auxiliary heat exchange section 5a and one or more of the plurality of second distributors 30, the middle upper main heat exchange section 5b2 and the middle lower main heat exchange section 5b2. It communicates with a plurality of heat transfer tubes 12 that constitute the central side main heat exchange section such as 5b3. The lower space 21a of the first distributor 20 passes through the auxiliary heat exchange section 5a and one or more of the plurality of other second distributors 30 that do not communicate with the central side main heat exchange section 5b1. and a plurality of heat transfer tubes 12 forming the lower main heat exchange portion 5b4.

Here, in the heat exchange between the first working fluid and the second working fluid in the heat exchanger located downstream of the distributor, the heat exchanger has the first This can result in inefficient distribution of the working fluid, reducing the efficiency of the heat exchanger. For example, in the heat exchanger of Patent Document 1, in the heat exchanger located downstream of the distributor, the refrigerant, which is the first working fluid, is distributed appropriately with respect to the heat amount of the air, which is the second working fluid. may not be For this reason, in the heat exchanger of Patent Document 1, the liquid refrigerant is evenly supplied to the heat transfer tubes in which the liquid refrigerant is excessive with respect to the amount of heat exchanged, and the performance of the heat exchanger may be deteriorated.

The first distributor 20 utilizes the characteristics of the liquid-rich gas-liquid two-phase refrigerant that passes through the orifice holes 92 of the orifice plate 91, and as shown in FIG. The amount of liquid refrigerant supplied to the heat exchange portions 50a such as the side main heat exchange portion 5b3 can be increased. Therefore, the heat exchanger 50 having the first distributor 20 can improve the heat exchanger performance by appropriately distributing the liquid refrigerant with respect to the heat amount of the second working fluid. The heat exchanger 50 maintains a flow velocity at which liquid refrigerant and gas refrigerant are separated in the gas-liquid two-phase refrigerant in the first distributor 20 so that the liquid refrigerant does not drop, and the main heat exchanger 50 located downstream of the first distributor 20 In the heat exchanging portion 5b, the liquid refrigerant can be appropriately distributed to the heat amount with the second working fluid.

As described above, the first distributor 20 supplies the gas-liquid two-phase refrigerant to the appropriate distribution of the liquid refrigerant according to the heat amount in the heat exchanger 50 with only simple components even at the upper part of the distributor. It is possible to contribute to the improvement of heat exchanger performance while suppressing material costs.

Embodiment 2.
FIG. 11 is a conceptual cross-sectional view of the bulging portion 27 according to the second embodiment. Components having the same functions and actions as those of the first distributor 20 and the like according to Embodiment 1 are denoted by the same reference numerals, and descriptions thereof are omitted. FIG. 11 is a vertical cross section of the bulging portion 27 with respect to the longitudinal direction (Z-axis direction) of the body portion 20a, and is a sectional view conceptually showing the bulging portion 27 shown in the first embodiment. The bulging portion 27 may be formed in a semicircular shape as shown in FIG. 11 .

FIG. 12 is a conceptual cross-sectional view of a first alternative form of the bulging portion 27 according to the second embodiment. FIG. 13 is a conceptual cross-sectional view of a second alternative form of the bulging portion 27 according to the second embodiment. The shape of the vertical cross section of the bulging portion 27 with respect to the longitudinal direction (Z-axis direction) of the body portion 20a is not limited to a semicircular shape. The shape of the vertical cross section of the bulging portion 27 with respect to the longitudinal direction (Z-axis direction) of the body portion 20a may be formed in a square shape as shown in FIG. 12, or may be formed in a triangular shape as shown in FIG. good too.

FIG. 14 is a conceptual cross-sectional view of a third alternative form of the bulging portion 27 according to the second embodiment. FIG. 15 is a conceptual cross-sectional view of a fourth alternative form of the bulging portion 27 according to the second embodiment. FIG. 16 is a conceptual cross-sectional view of a fifth alternative form of the bulging portion 27 according to the second embodiment. As shown in FIG. 14, the shape of the vertical cross section of the bulging portion 27 with respect to the longitudinal direction (Z-axis direction) of the main body portion 20a may be formed such that a plurality of small semicircular circular protrusions 27c are continuous. . Moreover, as shown in FIG. 15, the shape of the vertical cross section of the bulging portion 27 may be formed such that a plurality of small square-shaped square convex portions 27d are continuous. Moreover, as shown in FIG. 16, the shape of the vertical cross section of the bulging portion 27 may be formed in a sawtooth shape in which a plurality of small triangular mountain-like convex portions 27e are continuous.

The bulging portion 27 has one semicircular shape, one square shape, one triangular shape, a shape in which a plurality of semicircles are continuous, a shape in which a plurality of squares are continuous, or a shape in which a plurality of triangles are formed in an axis-perpendicular cross section. It is formed in a cross-sectional shape of any one of continuous shapes. In addition, the bulging portion 27 has, in an axis-perpendicular cross-section, a single semicircular shape, a single square shape, a single triangular shape, a shape in which a plurality of semicircles are continuous, a shape in which a plurality of squares are continuous, or a shape in which a plurality of squares are continuous. A groove having a cross-sectional shape in which triangles are continuous is formed. Note that the cross-sectional shape of the bulging portion 27 is not limited to these shapes, and may be formed by combining the above-described shapes, for example.

FIG. 17 is a perspective view of the main body portion 20a of the first distributor 20 according to Embodiment 2. FIG. As an example of the first distributor 20, the first distributor 20 having the fourth different form of the bulging portion 27 shown in FIG. 15 will be described with reference to FIG. The first distributor 20 shown in FIG. 17 is different from the semicircular bulging portion 27 described in the first embodiment, and has a bulging portion in which a plurality of small square convex portions 27d are continuously formed. 27. Therefore, in the first distributor 20 shown in FIG. 17, a plurality of projecting surfaces are formed by a plurality of square projections 27d projecting into the internal space 21. As shown in FIG.

[Action and effect of heat exchanger 50]
In general, in the gas-liquid two-phase refrigerant that flows upward in the inner space of the distributor, the liquid refrigerant tends to concentrate on the wall surface inside the distributor, and the gas refrigerant tends to concentrate on the central portion of the hollow inside the distributor. In the first distributor 20 of FIG. 17, the wall surface of the bulging portion 27 is in contact with the gas-liquid two-phase refrigerant by forming a plurality of protruding surfaces with a plurality of square convex portions 27d forming the bulging portion 27. Area can be increased. Therefore, the first distributor 20, in which the bulging portion 27 has a plurality of protruding surfaces, is different from the configuration of the single semicircular bulging portion 27 as in the first embodiment. The portion where the surface tension acts increases, and the fall of the liquid refrigerant can be suppressed.

Further, the first distributor 20 of FIG. 17 has a single semicircular shape as in the first embodiment by forming a plurality of protruded surfaces with a plurality of square convex portions 27d forming the bulging portion 27. The wetted edge length _L2 is increased compared to the configuration of the bulging portion 27 . Therefore, first distributor 20 in which bulging portion 27 has a plurality of protruding surfaces has a larger flooding constant _C2 than the configuration of one semicircular bulging portion 27 as in the first embodiment. Separation of gas refrigerant and liquid refrigerant can be suppressed.

As shown in FIG. 17, the first distributor 20 in which the bulging portion 27 has a plurality of protruding surfaces can suppress the liquid refrigerant from falling and can suppress the separation of the gas refrigerant and the liquid refrigerant. The supply of liquid refrigerant to the upper portion of the first distributor 20 is more likely to increase than in the first distributor 20 of 1. Therefore, even if the first distributor 20 has a plurality of heat transfer tubes 12 and the number of refrigerant branches increases, the mass flow rate of the gas-liquid two-phase refrigerant decreases from the bottom to the top of the first distributor 20. , the liquid refrigerant can be easily supplied from the upper portion of the first distributor 20 .

Further, when the second part 24 is manufactured by extrusion molding, the first distributor 20 according to the second embodiment has a bulging portion 27 formed of a plurality of convex portions as shown in FIGS. 14 to 16. Even if it has a shape, it can be manufactured at a low cost as in the first embodiment.

In addition, the bulging portion 27 has, in an axis-perpendicular cross section, one semicircular shape, one quadrangular shape, one triangular shape, a shape in which a plurality of semicircles are continuous, a shape in which a plurality of quadrilaterals are continuous, or a shape in which a plurality of squares are continuous. It is formed in any one cross-sectional shape of a shape in which triangles are continuous. The first distributor 20 can increase the flooding constant _C2 by having the bulging portion 27 having such a configuration as compared with the case where the bulging portion 27 is not provided. As a result, the first distributor 20 can separate the liquid refrigerant and the gas refrigerant in the gas-liquid two-phase refrigerant in the first distributor 20 and maintain a flow velocity at which the liquid refrigerant does not drop. Insufficient supply of liquid refrigerant to the upper part of the can be suppressed.

As described above, in the first distributor 20 according to Embodiment 2, the amount of liquid refrigerant supplied to the upper portion of the first distributor 20 is can be increased. Therefore, the first distributor 20 according to the second embodiment supplies the liquid refrigerant to the upper part of the first distributor 20 even when the refrigerant distribution path has more branches than the first distributor 20 according to the first embodiment. be able to.

Embodiment 3.
FIG. 18 is a conceptual cross-sectional view of another first form of orifice plate 91 used in first distributor 20 according to the third embodiment. FIG. 19 is a conceptual cross-sectional view of a second alternative form of orifice plate 91 used in first distributor 20 according to the third embodiment. FIG. 20 is a conceptual cross-sectional view of a third alternative form of orifice plate 91 used in first distributor 20 according to the third embodiment. 18 to 20 are cross-sectional views taken along line CC of the first distributor 20 shown in FIG. An orifice plate 91 that is different from the first embodiment will be described with reference to FIGS. 18 to 20. FIG. Components having the same functions and actions as those of the first distributor 20 and the like according to Embodiments 1 and 2 are denoted by the same reference numerals, and descriptions thereof are omitted.

The orifice plate 91 may have two orifice holes 92 such as an orifice hole 92a and an orifice hole 92b shown in FIGS. 18 and 19, the orifice plate 91 is formed with two orifice holes 92 such as an orifice hole 92a and an orifice hole 92b, but the orifice plate 91 is formed with at least one orifice hole 92. It is good if there is For example, the orifice plate 91 may be formed with only one of the orifice holes 92a and 92b shown in FIGS.

When viewed in a direction parallel to the longitudinal direction of the body portion 20a, the hole shape of the orifice hole 92 may be circular as shown in the orifice hole 92 in FIG. 18, or as shown in FIG. It may be formed in a rectangular shape. Also, the shape of the orifice hole 92 may be formed in an elliptical shape (not shown) when viewed in a direction parallel to the longitudinal direction of the body portion 20a.

7 and 20, the orifice plate 91 may be formed at the central portion of the orifice plate 91, and as shown in FIGS. may be formed in As shown in FIG. 19, the orifice plate 91 has an orifice hole 92a and an orifice hole 92b, each of which consists of a side surface portion 26, a flat plate portion 28, a bulging portion 27, and an orifice plate 91. It may be formed to be an enclosed space. In other words, the orifice holes 92 may be formed in the

corners

21c and 21d described above.

As shown in FIGS. 18 to 20, the orifice holes 92 are formed in the orifice plate 91 at positions that do not overlap the heat transfer tubes 12 when viewed in a direction parallel to the longitudinal direction of the main body 20a. That is, the first distributor 20 is arranged at a position where the plurality of heat transfer tubes 12 and the orifice holes 92 do not overlap when the first distributor 20 is projected in the axial direction of the first distributor 20 . In the advancing direction (Z-axis direction) of the gas-liquid two-phase refrigerant flowing upward in the internal space 21 of the first distributor 20, the heat transfer tubes 12 and the orifice holes 92 are arranged at positions that do not overlap.

It is considered that the gas-liquid two-phase refrigerant that flows upward in the internal space 21 of the first distributor 20 passes through the XY cross section that does not overlap the heat transfer tubes 12 . In this case, when the formation position of the orifice hole 92 is arranged in a portion overlapping with the heat transfer tube 12, the flow path of the gas-liquid two-phase refrigerant detours from the traveling direction and advances to the orifice hole 92 due to the existence of the heat transfer tube 12. flow.

If the flow of the gas-liquid two-phase refrigerant bypasses the heat transfer tubes 12 in this way, the distributor is likely to cause excessive pressure loss due to passage through the orifice holes 92, which not only reduces the supply of gas refrigerant but also The supply of refrigerant also tends to decrease. Therefore, as shown in FIGS. 18 to 20, the first distributor 20 is arranged at a position where the plurality of heat transfer tubes 12 and the orifice holes 92 do not overlap when projected in the axial direction of the first distributor 20. ing.

[Action and effect of heat exchanger 50]
The first distributor 20 is formed at a position where the orifice holes 92 and the heat transfer tubes 12 do not overlap, so that the flow of the gas-liquid two-phase refrigerant bypassing the heat transfer tubes 12 is less likely to occur. The gas-liquid two-phase refrigerant flowing upward in the internal space 21 easily passes through the orifice hole 92 . Therefore, the first distributor 20 is formed at a position where the orifice hole 92 and the heat transfer tube 12 do not overlap, thereby ensuring a sufficient supply amount of the liquid-rich gas-liquid two-phase refrigerant flowing into the upper space 21b. It is possible to suppress deterioration of the heat exchanger performance of the heat exchanger 50 .

Embodiment 4.
FIG. 21 is a conceptual diagram illustrating the relationship between the orifice holes 92 and the heat transfer tubes 12 in the first distributor 20 according to the fourth embodiment. FIG. 21(a) is a schematic cross-sectional view perpendicular to the direction in which the main body 20a extends along line CC shown in FIG. FIG. 21(b) is a schematic cross-sectional view of the main body 20a taken along line EE in FIG. 21(a). FIG. 21(c) is a diagram showing the "air temperature distribution" with respect to the "air flow direction" in the air flow direction indicated by the white arrow in FIG. 21(b). Components having the same functions and actions as those of the first distributor 20 and the like according to Embodiments 1 to 3 are denoted by the same reference numerals, and descriptions thereof are omitted.

The relationship between the positions where the orifice holes 92 are formed and the heat transfer tubes 12 will be described with reference to FIG. The heat transfer tube 12 shown in FIG. 21 is formed flat with respect to the air flow direction. The heat transfer tube 12 extends along the Y axis, which is perpendicular to the Z axis, which is the axial direction of the main body 20a, and the X axis, which is the direction in which the heat transfer tube 12 extends. It is formed in a flat shape having a long axis in the direction. The air flow is formed by, for example, the outdoor fan 6 or the indoor fan 7 shown in FIG. The outdoor fan 6 or the indoor fan 7 or the like supplies air to the heat exchanger 50 .

Each of the plurality of heat transfer tubes 12 is a flat tube. Each of the plurality of heat transfer tubes 12 has a plurality of coolant channel holes 12a formed therein, and the plurality of coolant channel holes 12a are arranged side by side in the Y-axis direction, which is the air flow direction. The formation position of the orifice hole 92 in the orifice plate 91 is formed at a position deviated to the windward side from the central position of the first distributor 20 . That is, the first distributor 20 is formed such that the orifice hole 92 is located relatively on the windward side with respect to the heat transfer tube 12 in which the plurality of refrigerant flow path holes 12a are arranged side by side in the air flow direction. ing.

As shown in FIG. 21(c), the air gradually exchanges heat in the direction of flow, resulting in a temperature drop. Therefore, the heat transfer tube 12 tends to lack the amount of heat for heat exchange in the refrigerant passage holes 12a located downstream of the air. The liquid refrigerant that has passed through the orifice hole 92 is most likely to concentrate in the refrigerant flow path hole 12 a that is the shortest distance from the orifice hole 92 . The first distributor 20 is orificed with respect to the heat transfer tubes 12 so that the refrigerant passage hole 12a, which is the shortest distance from the orifice hole 92 where the liquid refrigerant that has passed through the orifice hole 92 is most likely to concentrate, is on the windward side of the air. The formation positions of the holes 92 are biased.

[Action and effect of heat exchanger 50]
Each of the plurality of heat transfer tubes 12 has a plurality of refrigerant passage holes 12a formed therein, and the plurality of refrigerant passage holes 12a are formed by a blower such as the outdoor blower 6 or the indoor blower 7. arranged in the same direction. In the first distributor 20 , the orifice hole 92 is formed in the orifice plate 91 at a position that is shifted to the windward side of the center position of the first distributor 20 . Therefore, the first distributor 20 can improve the heat exchanger performance of the heat exchanger 50 by enabling distribution of the liquid refrigerant according to the heat amount of the heat transfer tubes 12 having the plurality of refrigerant flow passage holes 12a. can.

In addition, in the first distributor 20, the formation positions of the orifice holes 92 are biased with respect to the heat transfer tubes 12 so that the refrigerant flow path holes 12a that are the shortest from the orifice holes 92 are on the windward side of the air. Therefore, the first distributor 20 can improve the heat exchanger performance of the heat exchanger 50 by enabling distribution of the liquid refrigerant according to the heat amount of the heat transfer tubes 12 having the plurality of refrigerant flow passage holes 12a. can.

Embodiment 5.
FIG. 22 is a schematic diagram of a heat exchanger 50 according to Embodiment 5. FIG. Components having the same functions and actions as those of the heat exchanger 50 and the like according to Embodiments 1 to 4 are denoted by the same reference numerals, and descriptions thereof are omitted. Solid arrows shown in FIG. 22 indicate the direction in which the coolant flows. 22 indicates the direction of air flow. In the following description, the heat exchanger 50 will be described as a configuration when it is used as the outdoor heat exchanger 5 functioning as an evaporator when the air conditioner 10 is used for heating operation.

As shown in FIG. 22, the heat exchanger 50 has a heat exchange section 50a, a first distributor 20, a second distributor 30, and a header 80. The first distributor 20 and the second distributor 30 may be called headers.

The heat exchange section 50a of Embodiment 5 has two or more rows of heat exchange sections 50a. As shown in FIG. 22, the heat exchange section 50a has a first heat exchange section 51 located upstream and a second heat exchange section 52 located downstream in the direction of air flow. The first heat exchange portion 51 and the second heat exchange portion 52 are each formed to form an XZ plane. The first heat exchange section 51 and the second heat exchange section 52 are arranged so as to face each other in the Y-axis direction, which is the direction in which air flows.

When the heat exchanger 50 is the outdoor heat exchanger 5 (see FIG. 1), the outdoor blower 6 forms an air flow passing through the heat exchanger 50 in the air conditioner 10 . In this case, the heat exchange section 50a has a first heat exchange section 51 located upstream and a second heat exchange section 52 located downstream in the direction in which the air formed by the outdoor fan 6 flows. That is, the first heat exchange section 51 is arranged on the windward side with respect to the second heat exchange section 52 , and the second heat exchange section 52 is arranged on the leeward side with respect to the first heat exchange section 51 .

For example, when the outdoor fan 6 is positioned on the windward side of the heat exchanger 50 in the direction of air flow formed by the outdoor fan 6 , the first heat exchange section 51 is positioned outside the second heat exchange section 52 . It is arranged on the side close to the blower 6 . Alternatively, when the outdoor fan 6 is located on the leeward side of the heat exchanger 50 in the direction of air flow formed by the outdoor fan 6, the first heat exchange section 51 is compared with the second heat exchange section 52. It is arranged on the far side from the outdoor fan 6. - 特許庁

When the heat exchanger 50 is the indoor heat exchanger 3 (see FIG. 1), the indoor blower 7 forms an air flow passing through the heat exchanger 50 in the air conditioner 10 . In this case, the heat exchange section 50a has a first heat exchange section 51 located on the upstream side and a second heat exchange section 52 located on the downstream side in the direction in which the air formed by the indoor fan 7 flows.

For example, when the indoor fan 7 is located on the windward side of the heat exchanger 50 in the direction in which the air formed by the indoor fan 7 flows, the first heat exchange section 51 is positioned indoors relative to the second heat exchange section 52 . It is arranged on the side close to the blower 7 . Alternatively, when the indoor fan 7 is located on the leeward side of the heat exchanger 50 in the direction of air flow formed by the indoor fan 7, the first heat exchange section 51 is compared with the second heat exchange section 52. It is arranged on the far side from the indoor fan 7. - 特許庁

As shown in FIG. 22, the first heat exchanging portion 51 includes a first auxiliary heat exchanging portion 51a located upstream of the circulating refrigerant, and a first main heat exchanging portion 51b located downstream of the circulating refrigerant. , has Similarly, as shown in FIG. 22, the second heat exchange section 52 includes a second auxiliary heat exchange section 52a positioned upstream of the circulating refrigerant and a second main heat exchange section 52a positioned downstream of the circulating refrigerant. and a portion 52b. In the heat exchange section 50a, refrigerant flows through the first auxiliary heat exchange section 51a, the second auxiliary heat exchange section 52a, the first main heat exchange section 51b, and the second main heat exchange section 52b in this order.

The first auxiliary heat exchange section 51a is connected to the first distributor 20 at one end side in the extending direction (X-axis direction) of the heat transfer tubes 12, and is connected to the second auxiliary heat exchange section 52a via a joint 401 at the same first side. It is connected. Among the plurality of heat transfer tubes 12 , the first auxiliary heat exchange section 51 a is partly connected to the first distributor 20 and partly connected to the joint 401 . The first auxiliary heat exchange portion 51a has a U-shaped hairpin portion 202 on the other end side in the extending direction (X-axis direction) of the heat transfer tube 12 .

The first auxiliary heat exchange section 51 a changes the flow direction of the refrigerant flowing out of the first distributor 20 and flowing through the heat transfer tubes 12 at the hairpin section 202 . The first auxiliary heat exchange portion 51a is formed so that the refrigerant flows from the first distributor 20 toward the hairpin portion 202 and passes through another different heat transfer tube 12 from the hairpin portion 202 toward the arrangement side of the first distributor 20. It is Refrigerant from the hairpin portion 202 toward the arrangement side of the first distributor 20 flows through the joint 401 into the second auxiliary heat exchange portion 52a.

The second auxiliary heat exchange section 52a is connected to the first auxiliary heat exchange section 51a via a joint 401 at one end side in the extending direction (X-axis direction) of the heat transfer tube 12, and is connected to the first auxiliary heat exchange section 51a via a pipe 300 at the same one end side. It is connected to the 2 distributor 30 . Among the plurality of heat transfer tubes 12 , the second auxiliary heat exchange section 52 a is partly connected to the pipe 300 and partly connected to the joint 401 . The second auxiliary heat exchange portion 52a has a U-shaped hairpin portion 202 (not shown) on the other end side of the heat transfer tube 12 in the extending direction (X-axis direction).

In the second auxiliary heat exchange portion 52a, the refrigerant flowing out of the joint 401 and flowing through the heat transfer tube 12 changes its flow direction at the hairpin portion 202, and passes through another heat transfer tube 12 different from the heat transfer tube 12 toward the hairpin portion 202. 300 is formed. The second auxiliary heat exchange section 52 a and the second distributor 30 are connected by a pipe 300 .

The first main heat exchange section 51b includes an upper main heat exchange section 5b1, a middle upper main heat exchange section 5b2, a middle lower main heat exchange section 5b3, and a lower main heat exchange section 5b4. The upper main heat exchange section 5b1 is a portion of the first main heat exchange section 51b where the heat transfer tubes 12 forming the upper main heat exchange section 5b1 are connected to the upper second distributor 31 . The middle upper main heat exchange section 5b2 is a portion of the first main heat exchange section 51b where the heat transfer tubes 12 forming the middle upper main heat exchange section 5b2 are connected to the middle upper second distributor 32 (see FIG. 2).

The middle and lower main heat exchange portion 5b3 is the portion of the first main heat exchange portion 51b where the heat transfer pipes 12 constituting the middle and lower main heat exchange portion 5b3 are connected to the middle and lower second distributor 33 (see FIG. 2). is. The lower main heat exchange section 5b4 is a portion of the first main heat exchange section 51b where the heat transfer tubes 12 forming the lower main heat exchange section 5b4 are connected to the lower second distributor . The first main heat exchange section 51b is also a general term for the upper main heat exchange section 5b1, the intermediate upper main heat exchange section 5b2, the intermediate lower main heat exchange section 5b3, and the lower main heat exchange section 5b4.

The first main heat exchange section 51b is connected to the second distributor 30 on one end side in the extending direction (X-axis direction) of the heat transfer tubes 12, and is connected to the second main heat exchange section 52b via a joint 401 on the same first side. It is connected. Among the plurality of heat transfer tubes 12 , the first main heat exchange section 51 b is partly connected to the second distributor 30 and partly connected to the joint 401 . The first main heat exchange portion 51b has a U-shaped hairpin portion 202 on the other end side in the extending direction (X-axis direction) of the heat transfer tube 12 .

In the first main heat exchange portion 51b, the direction of flow of the refrigerant flowing out of the second distributor 30 and flowing through the heat transfer tubes 12 is changed at the hairpin portion 202. The first main heat exchange portion 51b is formed such that the refrigerant flows from the second distributor 30 toward the hairpin portion 202 and passes through the different heat transfer tubes 12 from the hairpin portion 202 toward the arrangement side of the second distributor 30. It is Refrigerant from the hairpin portion 202 toward the arrangement side of the second distributor 30 flows through the joint 401 into the second main heat exchange portion 52b.

The second main heat exchange portion 52b is connected to the first main heat exchange portion 51b via a joint 401 at one end side in the extending direction (X-axis direction) of the heat transfer tubes 12, and is connected to the header 80 at the same side. there is Among the plurality of heat transfer tubes 12 , the second main heat exchange section 52 b is partly connected to the header 80 and partly connected to the joint 401 . The second main heat exchange portion 52b has a U-shaped hairpin portion 202 (not shown) on the other end side of the heat transfer tube 12 in the extending direction (X-axis direction).

In the second main heat exchange portion 52b, the refrigerant flowing out of the joint 401 and flowing through the heat transfer tube 12 changes its flow direction at the hairpin portion 202, and passes through the other heat transfer tube 12 different from the heat transfer tube 12 heading for the hairpin portion 202 and passes through the header. It is formed to face 80.

(First distributor 20)
The first distributor 20 is provided on the refrigerant inflow side of the first auxiliary heat exchange section 51a when the heat exchanger 50 functions as an evaporator. The first distributor 20 is connected to one end in the extension direction (X-axis direction) of the plurality of heat transfer tubes 12 that constitute the first auxiliary heat exchange section 51a. The first distributor 20 is connected to the heat transfer tubes 12 of the first auxiliary heat exchange section 51a so that the inside of the first distributor 20 and the inside of the heat transfer tubes 12 communicate with each other.

The first distributor 20 is formed to extend along the arrangement direction (Z-axis direction) of the plurality of heat transfer tubes 12 . The first distributor 20 distributes the refrigerant to the multiple heat transfer tubes 12 . In the heat exchanger 50 , the first distributor 20 functions as a distribution mechanism that distributes the refrigerant flowing into the first auxiliary heat exchange section 51 a of the heat exchange section 50 a to the plurality of heat transfer tubes 12 .

(Second distributor 30)
The second distributor 30 is provided on the refrigerant inflow side of the first main heat exchange section 51b when the heat exchanger 50 functions as an evaporator. The second distributor 30 is provided on the refrigerant outflow side of the second auxiliary heat exchange section 52a when the heat exchanger 50 functions as an evaporator.

The second distributor 30 is connected to one end in the extending direction (X-axis direction) of the plurality of heat transfer tubes 12 forming the first main heat exchange section 51b. The second distributor 30 is connected to the heat transfer tubes 12 of the first main heat exchange section 51b so that the inside of the second distributor 30 and the pipeline of the heat transfer tubes 12 communicate with each other. The second distributor 30 is connected via piping 300 to a plurality of heat transfer tubes 12 that constitute the second auxiliary heat exchange section 52a.

The second distributor 30 is formed to extend along the arrangement direction (Z-axis direction) of the plurality of heat transfer tubes 12 . The second distributor 30 distributes the refrigerant to the multiple heat transfer tubes 12 . The second distributor 30 functions as a distribution mechanism that distributes the refrigerant flowing into the first main heat exchange section 51 b of the heat exchange section 50 a to the plurality of heat transfer tubes 12 in the heat exchanger 50 .

The second auxiliary heat exchange section 52a and the second distributor 30 are connected by the pipe 300 as described above. More specifically, the second auxiliary heat exchange section 52 a is connected to the upper pipe 301 , the middle upper pipe 302 , the middle lower pipe 303 , and the lower pipe 304 .

The upper pipe 301 is a pipe that connects the second auxiliary heat exchange section 52 a and the upper second distributor 31 . The upper pipe 301 communicates the lower space 21 a (see FIG. 2 ) of the first distributor 20 with the inside of the second upper distributor 31 via the heat transfer pipes 12 . The middle upper pipe 302 is a pipe that connects the second auxiliary heat exchange section 52 a and the middle upper second distributor 32 . The middle upper pipe 302 communicates the upper space 21 b (see FIG. 2 ) of the first distributor 20 with the inside of the middle upper second distributor 32 via the heat transfer pipes 12 .

The middle and lower pipe 303 is a pipe that connects the second auxiliary heat exchange section 52 a and the middle and lower second distributor 33 . The middle-lower pipe 303 communicates the upper space 21 b (see FIG. 2 ) of the first distributor 20 with the inside of the second middle-lower distributor 33 via the heat transfer pipes 12 . The lower pipe 304 is a pipe that connects the second auxiliary heat exchange section 52 a and the second lower distributor 34 . The lower pipe 304 communicates the lower space 21a (see FIG. 2) of the first distributor 20 with the inside of the second lower distributor 34 via the heat transfer pipes 12 .

(Header 80)
The header 80 is connected to one end in the extending direction (X-axis direction) of the plurality of heat transfer tubes 12 forming the second main heat exchange portion 52b. The header 80 is connected to the heat transfer tubes 12 of the second main heat exchange section 52b so that the inside of the header 80 and the inside of the heat transfer tubes 12 communicate with each other. In the heat exchanger 50, the header 80 functions as a merging mechanism for merging the refrigerants flowing out from the plurality of heat transfer tubes 12 of the second main heat exchange portion 52b. In addition, the header 80 may be called a gas header.

As shown in FIG. 22, the heat exchanger 50 shown in Embodiment 5 has the second distributor 30 arranged on the upstream side and the header 80 arranged on the downstream side in the direction of air flow. Moreover, as shown in FIG. 22, the heat exchanger 50 shown in Embodiment 5 has the first distributor 20 arranged on the upstream side and the header 80 arranged on the downstream side in the direction of air flow.

22, the heat exchanger 50 shown in Embodiment 5 has the second distributor 30 arranged above the first distributor 20, and the first distributor 30 below the second distributor 30. A distributor 20 is arranged. In the heat exchanger 50 shown in Embodiment 5, the first distributor 20, the lower second distributor 34, the middle-lower second distributor 33, the middle-upper second distributor 32, and the upper-second distributor 31 are , are arranged vertically. In the heat exchanger 50 shown in Embodiment 5, the first distributor 20, the lower second distributor 34, the middle-lower second distributor 33, the middle-upper second distributor 32, and the upper-second distributor 31 are , are arranged in this order from bottom to top.

FIG. 23 is an explanatory diagram of the refrigerant flow paths of the heat exchanger 50 according to Embodiment 5. FIG. "Distributor side" in FIG. 23 represents the end of the heat exchanger 50 on the side where the first distributor 20 is arranged, and "hairpin side" means the end of the heat exchanger 50 on the side where the hairpin portion 202 is arranged. represent. Dotted line arrows and solid line arrows in FIG. 23 indicate the flow of the coolant. The flow of the refrigerant passage passing through the first heat exchange portion 51 and the second heat exchange portion 52 will be described with reference to FIG. 23 . Note that the inlet A1, the opening A2, the opening A3, the outlet A4, the inlet B1, the opening B2, the opening B3, and the outlet B4 conceptually represent openings at the ends of the heat transfer tubes 12. It is.

The inlet A1, the opening A2, the opening A3, the outlet A4, the inlet B1, the opening B2, the opening B3, and the outlet B4 are connected to the lower body portion 20a1 of the first distributor 20, and the lower space 21a. (see FIG. 3). In addition, the inlet A1, the opening A2, the opening A3, the outlet A4, the inlet B1, the opening B2, the opening B3, and the outlet B4 are connected to the upper body portion 20a2 of the first distributor 20, It communicates with the space 21b (see FIG. 3).

For example, the refrigerant flow when the first heat exchange section 51 shown in FIG. 23 is the first auxiliary heat exchange section 51a and the second heat exchange section 52 is the second auxiliary heat exchange section 52a will be described. When the refrigerant RA distributed by the first distributor 20 flows into the first heat exchange portion 51 from the inlet A1 of the first heat exchange portion 51, the refrigerant RA flows from the inlet A1 to the hairpin portion 202 (see FIG. 22). reference).

In the first heat exchange section 51, the refrigerant RA that has reached the hairpin portion 202 makes a U-turn at the hairpin portion 202, flows through the heat transfer tube 12 one stage above the heat transfer tube 12 that has flowed from the inlet A1 to the hairpin portion 202, It goes from the hairpin part 202 to the opening A2. The opening A2 is located one step above the inlet A1.

The opening A2 of the first heat exchange section 51 and the opening A3 of the second heat exchange section 52 are connected by a U vent 402, which is a U-shaped pipe. More specifically, the opening A2 and the opening A3 are provided with a joint 401 (see FIG. 22), and a U-bent is formed to connect the joint 401 of the opening A2 and the joint 401 of the opening A3. 402 is provided.

Refrigerant RA moves along the line from the first heat exchange section 51 to the second heat exchange section 52 by means of the U vent 402 . The refrigerant RA that has flowed out from the opening A2 of the first heat exchange section 51 passes through the U vent 402 and flows into the opening A3 of the second heat exchange section 52 . The refrigerant RA that has flowed into the second heat exchange portion 52 from the opening A3 flows from the opening A3 to the hairpin portion 202 (see FIG. 22).

In the second heat exchange section 52, the refrigerant RA that has reached the hairpin section 202 makes a U-turn at the hairpin section 202, flows through the heat transfer tube 12 one stage below the heat transfer tube 12 that has flowed from the opening A3 to the hairpin section 202, It goes from the hairpin part 202 to the outflow port A4. The outflow port A4 is located one step below the opening A3. Refrigerant RA flowing out of second heat exchange section 52 from outlet A4 flows into second distributor 30 through pipe 300 (see FIG. 22).

Further, when the refrigerant RB distributed by the first distributor 20 flows into the first heat exchanging portion 51 from the inflow port B1 of the first heat exchanging portion 51, the refrigerant RB flows from the inflow port B1 to the hairpin portion 202 ( 22). The inflow port B1 is located one step below the inflow port A1.

In the first heat exchange section 51, the refrigerant RB that has reached the hairpin portion 202 makes a U-turn at the hairpin portion 202, flows through the heat transfer tube 12 that is one step below the heat transfer tube 12 that has flowed from the inlet B1 to the hairpin portion 202, It goes from the hairpin part 202 to the opening B2. The opening B2 is located one step below the inlet B1.

The opening B2 of the first heat exchange section 51 and the opening B3 of the second heat exchange section 52 are connected by a U vent 402, which is a U-shaped tube. More specifically, a joint 401 (see FIG. 22) is provided at the openings B2 and B3, and a U-bent is formed to connect the joint 401 of the opening B2 and the joint 401 of the opening B3. 402 is provided.

Refrigerant RB moves along the line from the first heat exchange section 51 to the second heat exchange section 52 by means of the U vent 402 . Refrigerant RB that has flowed out from the opening B2 of the first heat exchange section 51 passes through the U vent 402 and flows into the opening B3 of the second heat exchange section 52 . The refrigerant RB that has flowed into the second heat exchange portion 52 from the opening B3 flows from the opening B3 to the hairpin portion 202 (see FIG. 22).

In the second heat exchange portion 52, the refrigerant RB that has reached the hairpin portion 202 makes a U-turn at the hairpin portion 202, flows through the heat transfer tube 12 one stage above the heat transfer tube 12 that has flowed from the opening B3 to the hairpin portion 202, It goes from the hairpin part 202 to the outflow port B4. The outflow port B4 is located one step above the opening B3. Refrigerant RB flowing out of second heat exchange section 52 from outlet B4 flows into second distributor 30 through pipe 300 (see FIG. 22). Note that the outflow port B4 is formed one step below the outflow port A4.

The above description of the flow of the refrigerant RA and the refrigerant RB is for the case where the first heat exchange section 51 is the first auxiliary heat exchange section 51a and the second heat exchange section 52 is the second auxiliary heat exchange section 52a. It explains the flow of When the first heat exchange section 51 is the first main heat exchange section 51b and the second heat exchange section 52 is the second main heat exchange section 52b, the refrigerant RA flows from the second distributor 30 to the inlet A1. Refrigerant RB flows from the second distributor 30 into the inlet B1.

Further, when the first heat exchange portion 51 is the first main heat exchange portion 51b and the second heat exchange portion 52 is the second main heat exchange portion 52b, the refrigerant RA flows through the second heat exchange portion 52. The refrigerant RB flows into the header 80 from the outlet A4, and the refrigerant RB flows into the header 80 from the outlet B4 of the second heat exchange section 52. As shown in FIG. The flow of the refrigerant RA from the inflow port A1 to the outflow port A4 and the flow of the refrigerant RB from the inflow port B1 to the outflow port B4 are caused by the first auxiliary heat exchange portion 51a. , is the same as the case where the second heat exchange section 52 is the second auxiliary heat exchange section 52a.

FIG. 24 is a schematic diagram of a modification of the heat exchanger 50 according to the fifth embodiment. A modification of heat exchanger 50 according to Embodiment 5 has distributor 120 . The distributor 120 is formed by integrally forming the first distributor 20 and the second distributor 30 . More specifically, the distributor 120 includes a first distributor 20, an upper second distributor 31, a middle upper second distributor 32, a middle lower second distributor 33, and a lower second distributor. 34 are integrally formed. In a modification of heat exchanger 50 according to Embodiment 5, second distributor 30 is formed in the same shape as first distributor 20 . That is, the second distributor 30 is formed of the first part 23 and the second part 24 together with the first distributor 20 .

In the distributor 120, the parts constituting the first distributor 20, the lower second distributor 34, the middle lower second distributor 33, the middle upper second distributor 32, and the upper second distributor 31 are arranged vertically. They are arranged side by side (in the Z-axis direction). In the distributor 120, the parts constituting the first distributor 20, the lower second distributor 34, the middle lower second distributor 33, the middle upper second distributor 32, and the upper second distributor 31 are arranged from below. They are arranged in this order toward the top, and these parts are integrally formed.

The first distributor 20 and the second distributor 30 are integrally formed so as to extend in the vertical direction (Z-axis direction). It has a partition plate 94 separating it from the space.

A partition plate 94 partitions between the first distributor 20 and the second distributor 30 , that is, between the first distributor 20 and the lower second distributor 34 . The space of the first distributor 20 and the space of the lower second distributor 34 are separated by a partition plate 94 . Similarly, between the lower second distributor 34 and the middle-lower second distributor 33, between the middle-lower second distributor 33 and the middle-upper second distributor 32, and between the middle-upper second distributor 32 and the upper second distributor 31 are also partitioned by the partition plate 94 .

A partition plate 94 separates the space of the lower second distributor 34 from the space of the middle lower second distributor 33 . A partition plate 94 separates the space of the middle-lower second distributor 33 and the space of the middle-upper second distributor 32 . A partition plate 94 separates the space of the middle upper second distributor 32 and the space of the upper second distributor 31 .

[Action and effect of heat exchanger 50]
In a modification of heat exchanger 50 according to Embodiment 5, first distributor 20 and second distributor 30 are integrally formed so as to extend in the vertical direction (Z-axis direction). 20 and a partition plate 94 separating the internal space of the second distributor 30 . In a modification of the heat exchanger 50 according to Embodiment 5, if the parts that constitute the first part 23 (see FIG. 4) and the parts that constitute the second part 24 are made of long objects, they can be divided into partition plates 94 or the like. By using small parts, the first distributor 20 and the second distributor 30 can be configured.

In addition, the distributor 120 includes the first distributor 20, the lower second distributor 34, the middle lower second distributor 33, the middle upper second distributor 32, and the upper second distributor 31, respectively. are separated by a partition plate 94. In the distributor 120, if the parts constituting the first part 23 and the parts constituting the second part 24 are made of long pieces, a small part such as the partition plate 94 is used to form the first distributor 20 and the lower part. A second distributor 34, a middle-lower second distributor 33, a middle-upper second distributor 32, and an upper-second distributor 31 can be configured.

A modification of the heat exchanger 50 according to Embodiment 5 has a distributor 120, and by using a partition plate 94, the distributor 120 includes the first distributor 20, the lower second distributor 34, and the middle and lower distributors. The side second distributor 33, the middle upper side second distributor 32, and the upper side second distributor 31 can be configured. The heat exchanger 50 configures the first distributor 20, the lower second distributor 34, the middle lower second distributor 33, the middle upper second distributor 32, and the upper second distributor 31 with simple components. and reduce material and manufacturing costs compared to making these parts separately.

In addition, the heat exchanger 50 includes a first distributor 20, a lower second distributor 34, a middle lower second distributor 33, a middle upper second distributor 32, and an upper second distributor 31 with simple components. can be configured, and compactness can be achieved as compared with the case where these parts are made separately.

In addition, the heat exchanger 50 includes a first distributor 20, a lower second distributor 34, a middle lower second distributor 33, a middle upper second distributor 32, and an upper second distributor 31 with simple components. can be configured. Therefore, the heat exchanger 50 can contribute to improvement in assembling efficiency by reducing the number of parts compared to the case where these parts are made separately.

[Usage example of heat exchanger 50]
FIG. 25 is a first schematic diagram showing the relationship between the heat exchanger 50 and the outdoor fan 6 according to Embodiments 1-5. Arrows shown in FIG. 25 indicate the flow of air. An outdoor fan 6 shown in FIG. 25 is a fan that supplies air to the plurality of heat transfer tubes 12 of the heat exchanger 50 that constitutes the outdoor heat exchanger 5 .

As shown in FIG. 25, the outdoor unit 111 has an outdoor heat exchanger 5 and an outdoor fan 6. The outdoor unit 111 is used for the air conditioner 10 . The outdoor unit 111 is, for example, a domestic or commercial outdoor unit, and has a side-flow type outdoor fan 6 . As the outdoor heat exchanger 5 used in the outdoor unit 111, the heat exchanger 50 described above is used. The outdoor unit 111 may be an indoor unit. In this case, the outdoor heat exchanger 5 is the indoor heat exchanger 3 (see FIG. 1), and the outdoor fan 6 is the indoor fan 7 .

FIG. 26 is a second schematic diagram showing the relationship between the heat exchanger 50 and the outdoor fan 6 according to Embodiments 1-5. Arrows shown in FIG. 26 indicate the flow of air. An outdoor fan 6 shown in FIG. 26 is a fan that supplies air to the plurality of heat transfer tubes 12 of the heat exchanger 50 that constitutes the outdoor heat exchanger 5 .

As shown in FIG. 26, the outdoor unit 112 has an outdoor heat exchanger 5 and an outdoor fan 6. The outdoor unit 112 is used for the air conditioner 10 . The outdoor unit 112 is, for example, an outdoor unit for a building, and is equipped with a top-flow type outdoor fan 6 . As the outdoor heat exchanger 5 used in the outdoor unit 112, the heat exchanger 50 described above is used. The outdoor unit 112 may be an indoor unit. In this case, the outdoor heat exchanger 5 is the indoor heat exchanger 3 (see FIG. 1), and the outdoor fan 6 is the indoor fan 7 .

FIG. 27 is a first schematic diagram showing the relationship between the heat exchanger 50 and the indoor fan 7 according to Embodiments 1-5. Arrows shown in FIG. 27 indicate the flow of air. An indoor fan 7 shown in FIG. 27 is a fan that supplies air to the plurality of heat transfer tubes 12 of the heat exchanger 50 that constitutes the indoor heat exchanger 3 .

As shown in FIG. 27, the indoor unit 113 has an indoor heat exchanger 3 and an indoor fan 7. The indoor unit 113 is used for the air conditioner 10 . The indoor unit 113 is, for example, a cassette type indoor unit for commercial use, and is equipped with a turbo fan as the indoor air blower 7 . The heat exchanger 50 described above is used as the indoor heat exchanger 3 used in the indoor unit 113 . The indoor unit 113 may be an outdoor unit. In this case, the indoor heat exchanger 3 is the outdoor heat exchanger 5 (see FIG. 1), and the indoor fan 7 is the outdoor fan 6.

FIG. 28 is a second schematic diagram showing the relationship between the heat exchanger 50 and the indoor fan 7 according to Embodiments 1-5. Arrows shown in FIG. 28 indicate the flow of air. An indoor fan 7 shown in FIG. 28 is a fan that supplies air to the plurality of heat transfer tubes 12 of the heat exchanger 50 that constitutes the indoor heat exchanger 3 .

As shown in FIG. 28, the indoor unit 114 has an indoor heat exchanger 3 and an indoor fan 7. The indoor unit 114 is used for the air conditioner 10 . The indoor unit 114 is, for example, a domestic indoor unit, and is equipped with a cross-flow fan as the indoor blower 7 . The heat exchanger 50 described above is used as the indoor heat exchanger 3 used in the indoor unit 114 . The indoor unit 114 may be an outdoor unit, in which case the indoor heat exchanger 3 is the outdoor heat exchanger 5 (see FIG. 1), and the indoor fan 7 is the outdoor fan 6 .

FIG. 29 is a third schematic diagram showing the relationship between the heat exchanger 50 and the indoor fan 7 according to Embodiments 1-5. FIG. 30 is a fourth schematic diagram showing the relationship between the heat exchanger 50 and the indoor fan 7 according to Embodiments 1-5. Arrows shown in FIGS. 29 and 30 indicate the flow of air. The indoor fan 7 shown in FIGS. 29 and 30 is a fan that supplies air to the plurality of heat transfer tubes 12 of the heat exchanger 50 that constitutes the indoor heat exchanger 3 . As shown in FIGS. 29 and 30, the indoor unit 115 and the indoor unit 116 have an indoor heat exchanger 3 and an indoor fan 7. As shown in FIGS.

In the indoor unit 115, the indoor fan 7 is arranged on the upstream side with respect to the indoor heat exchanger 3, and the indoor heat exchanger 3 is arranged on the downstream side with respect to the indoor fan 7 in the direction of air flow formed by the indoor fan 7. are placed in In the indoor unit 116, the indoor fan 7 is arranged downstream with respect to the indoor heat exchanger 3, and the indoor heat exchanger 3 is arranged upstream with respect to the indoor fan 7 in the direction of air flow formed by the indoor fan 7. are placed in

The indoor unit 115 and the indoor unit 116 are used in the air conditioner 10. The indoor unit 115 and the indoor unit 116 are, for example, ceiling-embedded indoor units, and are equipped with a sirocco fan as the indoor air blower 7 . The heat exchanger 50 described above is used as the indoor heat exchanger 3 used in the

indoor units

115 and 116 . The indoor unit 115 and the indoor unit 116 may be outdoor units. In this case, the indoor heat exchanger 3 is the outdoor heat exchanger 5 (see FIG. 1), and the indoor fan 7 is the outdoor fan 6.

In addition, when the indoor heat exchanger 3 is installed inclined with respect to the direction of gravity as shown in FIGS. 29 and 30, the liquid refrigerant is less likely to fall due to the separation of the liquid refrigerant and the gas refrigerant, which is a problem. However, the heat exchanger 50 having the distributor of Embodiments 1 to 5 may be used in order to suppress the shortage of the liquid refrigerant to the upper part of the distributor when the flow rate of the refrigerant is small.

[Action and effect of the air conditioner 10]
The air conditioner 10 includes the heat exchanger 50 according to any one of the first to fifth embodiments described above. Therefore, the air conditioner 10 can obtain the same effect as any of the heat exchangers 50 according to Embodiments 1-5.

Each of the above-described Embodiments 1 to 5 can be implemented in combination with each other. In addition, the configuration shown in the above embodiment shows an example of the content of the present disclosure, and can be combined with another known technique, and the configuration can be configured without departing from the gist of the present disclosure. It is also possible to omit or change part of The heat exchanger 50 according to the present disclosure can be applied to, for example, a heat pump device, a hot water supply device, a refrigeration device, etc., in addition to the air conditioner 10 described above. Further, the heat exchanger 50 may be used as an upstream distributor that does not require the auxiliary heat exchange section 5a. Also, the second distributor 30 may have the orifice plate 91 .

1 compressor, 2 channel switching device, 3 indoor heat exchanger, 4 decompression device, 5 outdoor heat exchanger, 5a auxiliary heat exchange section, 5b main heat exchange section, 5b1 upper main heat exchange section, 5b2 middle upper main heat exchange part, 5b3 middle and lower main heat exchange part, 5b4 lower main heat exchange part, 6 outdoor fan, 7 indoor fan, 10 air conditioner, 12 heat transfer tube, 12a refrigerant flow path hole, 12b tip, 13 heat transfer Promotion member, 20 first distributor, 20a main body, 20a1 lower main body, 20a2 upper main body, 21 internal space, 21a lower space, 21b upper space, 21c corner, 21d corner, 23 first part, 24 second 2 parts, 25 insertion surface portion, 26 side surface portion, 27 bulging portion, 27a facing surface, 27b top portion, 27c circular convex portion, 27d square convex portion, 27e mountain convex portion, 28 flat plate portion, 28a joint portion, 30 Second distributor, 31 Upper second distributor, 32 Middle upper second distributor, 33 Middle lower second distributor, 34 Lower second distributor, 35 Gas-liquid two-phase refrigerant, 41 Lid, 42 Lid, 43 connection port, 44 inlet, 50 heat exchanger, 50a heat exchange section, 51 first heat exchange section, 51a first auxiliary heat exchange section, 51b first main heat exchange section, 52 second heat exchange section, 52a second 2 auxiliary heat exchange section, 52b second main heat exchange section, 80 header, 91 orifice plate, 92 orifice hole, 92a orifice hole, 92b orifice hole, 94 partition plate, 111 outdoor unit, 112 outdoor unit, 113 indoor unit, 114 Indoor unit, 115 Indoor unit, 116 Indoor unit, 120 Distributor, 201 Inflow pipe, 202 Hairpin part, 300 Pipe, 301 Upper pipe, 302 Middle upper pipe, 303 Middle lower pipe, 304 Lower pipe, 401 Joint, 402 U vent, 801 outflow pipe, A1 inflow port, A2 opening, A3 opening, A4 outflow port, B1 inflow port, B2 opening, B3 opening, B4 outflow port.

Claims

a plurality of heat transfer tubes arranged at intervals in the vertical direction;
a first distributor formed to extend in the vertical direction for distributing a refrigerant to the plurality of heat transfer tubes;
with
The first distributor is
an insertion surface portion into which the plurality of heat transfer tubes are inserted;
a facing surface portion facing the insertion surface portion in the extending direction of the plurality of heat transfer tubes;
a wall extending between the insertion surface portion and the facing surface portion in an axis-perpendicular cross section that is a cross section perpendicular to the longitudinal direction of the first distributor, the side portion being joined to the facing surface portion;
has
The facing surface portion is
A flat plate portion connected to the side surface portion, and a bulging portion in which a part of an inner wall forming an internal space of the first distributor bulges from the flat plate portion toward the insertion surface portion in the axis-perpendicular cross section. have
The first distributor is
In the axis-perpendicular cross-section, the shortest distance from the tip of each of the plurality of heat transfer tubes to the bulging portion is defined as a first distance M1, and the tip of each of the plurality of heat transfer tubes in the direction in which the plurality of heat transfer tubes extend A heat exchanger that satisfies the relationship of second distance M2≧1.5×first distance M1, where the distance from the portion to the position of the flat plate portion is a second distance M2.
The insertion surface portion is
2. The heat exchanger according to claim 1, wherein at least a portion of the cross section perpendicular to the axis is curved so as to be convex toward the arrangement side of the plurality of heat transfer tubes.
The first distributor is
3. The heat exchanger according to claim 1, further comprising a lid that closes both ends of the first distributor in the longitudinal direction and forms the internal space together with the insertion surface portion, the facing surface portion, and the side surface portion.
The first distributor is
At least one orifice plate separating the internal space into an upper space located above and a lower space located below in the longitudinal direction of the first distributor,
The heat exchanger according to any one of claims 1 to 3, wherein the orifice plate is formed with an orifice hole that is a through hole and communicates the upper space and the lower space.
The first distributor is
5. The heat exchanger according to claim 4, wherein the plurality of heat transfer tubes and the orifice holes are arranged so as not to overlap each other when projected in the axial direction of the first distributor.
At least one inflow port through which a coolant flows into the internal space is formed in the facing surface portion,
The inlet is
In the internal space, it is formed at a position facing the lowermost heat transfer tube among the plurality of heat transfer tubes, or the heat transfer tube positioned at the lowermost among the plurality of heat transfer tubes The heat exchanger according to any one of claims 1 to 5, which is formed so as to be positioned downward.
The first distributor is
a first component having the insertion surface portion and the side surface portion;
a second component that is the facing surface portion;
with
The heat exchanger according to any one of claims 1 to 6, wherein the first part and the second part are combined to form a tubular shape.
The bulging portion is
In the axis-perpendicular cross section, any of one semicircular shape, one quadrangular shape, one triangular shape, a shape in which a plurality of semicircles are continuous, a shape in which a plurality of quadrilaterals are continuous, or a shape in which a plurality of triangles are continuous. The heat exchanger according to any one of claims 1 to 7, wherein the heat exchanger is formed in one cross-sectional shape.
a main heat exchange section having at least half of the plurality of heat transfer tubes;
an auxiliary heat exchange section having remaining heat transfer tubes that do not constitute the main heat exchange section among the plurality of heat transfer tubes;
the first distributor connected to the auxiliary heat exchange unit;
a second distributor connected to the main heat exchange section for distributing the refrigerant flowing out of the auxiliary heat exchange section to the plurality of heat transfer tubes constituting the main heat exchange section;
with
The first distributor and the second distributor are integrally formed so as to extend in the vertical direction, and separate the space inside the first distributor from the space inside the second distributor. The heat exchanger according to any one of claims 1 to 8, which has a partition plate.
a main heat exchange section having at least half of the plurality of heat transfer tubes;
an auxiliary heat exchange section having remaining heat transfer tubes that do not constitute the main heat exchange section among the plurality of heat transfer tubes;
the first distributor connected to the auxiliary heat exchange unit;
a plurality of second distributors connected to the main heat exchange section for distributing the refrigerant flowing out of the auxiliary heat exchange section to the plurality of heat transfer tubes constituting the main heat exchange section;
with
The main heat exchange part is
an upper main heat exchange section positioned above the main heat exchange section in the vertical direction;
a lower main heat exchange section located below the main heat exchange section in the vertical direction;
a center side main heat exchange section disposed between the upper main heat exchange section and the lower main heat exchange section in the vertical direction of the main heat exchange section;
has
In the first distributor,
The upper space forming a space above the orifice plate and the lower space forming a space below the orifice plate are formed,
The upper space is
communicates with the plurality of heat transfer tubes constituting the center-side main heat exchange section via the auxiliary heat exchange section and one or more of the plurality of second distributors;
The lower space is
The upper main heat exchange section and the lower main heat exchange section are configured via the auxiliary heat exchange section and one or more of the plurality of other second distributors that do not communicate with the central main heat exchange section. 6. The heat exchanger according to claim 4 or 5, which communicates with said plurality of heat transfer tubes.
The first distributor is
2. The first distributor is installed in a state in which the central axis of the longitudinal direction of the first distributor is oriented vertically, or in a state in which the central axis of the longitudinal direction of the first distributor is inclined within a range having a vector component in the vertical direction. 11. The heat exchanger according to any one of items 1 to 10.
A heat exchanger according to claim 4 or 5;
a blower that supplies air to the heat exchanger;
has
Each of the plurality of heat transfer tubes has a plurality of coolant channel holes formed therein,
The plurality of coolant channel holes are arranged side by side in a direction in which the air formed by the blower flows,
The air conditioner according to claim 1, wherein the orifice hole is formed in the orifice plate at a position that is inclined toward the windward side of the central position of the first distributor.
A heat exchanger according to any one of claims 1 to 11;
and a blower that supplies air to the heat exchanger.