JP7146139B1 - heat exchangers and air conditioners - Google Patents

Abstract

The heat exchanger includes a plurality of heat transfer tubes arranged at intervals in the vertical direction, and a distributor for distributing the refrigerant to the plurality of heat transfer tubes, and the distributor is an insertion through which the heat transfer tubes are inserted. a surface portion, a facing surface portion facing the insertion surface portion in the direction in which the plurality of heat transfer tubes extend, and a wall extending between the insertion surface portion and the facing surface portion in an axis-perpendicular cross section of the distributor, and joined to the facing surface portion a side surface portion, wherein the opposing surface portion includes a flat plate portion connected to the side surface portion, and a portion of an inner wall forming an internal space of the distributor protrudes from the flat plate portion toward the insertion surface portion in an axis-perpendicular cross section. and a bulging portion.

Description

TECHNICAL FIELD The present disclosure relates to heat exchangers and air conditioners that exchange heat between a refrigerant passing through heat transfer tubes and air, and more particularly to a distributor that branches and supplies refrigerant to heat transfer tubes.

Generally, a vapor compression refrigeration cycle widely used in heat pump devices such as air conditioners has four elements: a compressor, a heat exchanger functioning as a condenser, a heat exchanger functioning as an evaporator, and an expansion valve. Consists of parts. In the refrigeration cycle, a refrigerant, which is a working fluid, flows through these four elemental parts with changes in state. Conventionally, an evaporator provided in a vapor compression refrigeration cycle 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. be. In order for the evaporator to function with high efficiency, it is necessary to evenly distribute the refrigerant to each of the plurality of heat transfer tubes.

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

Therefore, a cylindrical tube having a plurality of outflow pipe connection ports in the longitudinal direction has a plurality of partitioned spaces inside, and a small diameter flow path that can communicate with each space is provided inside. A distributor has been proposed that is characterized by having a space extending from an inlet via an orifice upstream of the channel (see, for example, Patent Document 1). In the distributor described in Patent Literature 1, the gas-liquid two-phase refrigerant is homogeneously mixed at the orifice, and then the refrigerant is evenly distributed to the small-diameter flow paths. It is

Japanese Patent No. 5376010

However, in the distributor described in Patent Document 1, a small space branched into three is formed in the space to which the refrigerant flows out of the small diameter pipe, and the three branches are supplied to the small space. At the flow rate of the refrigerant, the gas refrigerant and the liquid refrigerant of the gas-liquid two-phase refrigerant tend to separate in the small space, and the liquid refrigerant may be difficult to flow in the small space located in the upper part of the three branches.

An object of the present disclosure is to solve the problems described above, and to provide a heat exchanger and an air conditioner that are excellent in performance for evenly distributing a gas-liquid two-phase refrigerant.

A heat exchanger according to the present disclosure includes a plurality of heat transfer tubes that are spaced apart in the vertical direction, and a distributor that distributes refrigerant to the plurality of heat transfer tubes. An insertion surface portion to be inserted, a facing surface portion facing the insertion surface portion in the direction in which the plurality of heat transfer tubes extend, and a wall extending between the insertion surface portion and the facing surface portion in an axis-perpendicular cross section of the distributor, wherein the facing surface portion The opposing surface portion has a flat plate portion connected to the side portion, and a flat plate portion in which a part of the inner wall forming the internal space of the distributor extends toward the insertion surface portion in an axis-perpendicular cross section. A corner surrounded by the flat plate portion, the bulging portion, and the side portion is formed as an internal space of the distributor .

An air conditioner according to the present disclosure includes the heat exchanger according to the present disclosure and an air blower that supplies air to a plurality of heat transfer tubes.

A heat exchanger according to the present disclosure includes a distributor having an insertion surface portion into which a plurality of heat transfer tubes are inserted and a facing surface portion facing the insertion surface portion. The facing surface portion has a flat plate portion connected to the side surface portion, and a bulging portion in which a part of the inner wall forming the internal space of the distributor bulges from the flat plate portion toward the insertion surface portion in the axis-perpendicular cross section. . The heat exchanger can distribute the gas-liquid two-phase refrigerant with a large flooding constant by having the bulging portion in the distributor. Therefore, the distributor can prevent the separation of the gas-liquid two-phase refrigerant into the gas refrigerant and the liquid refrigerant, and can evenly supply the gas refrigerant and the liquid refrigerant to the plurality of heat transfer tubes located downstream of the distributor.

Since the air conditioner according to the present disclosure includes the heat exchanger having the above configuration, it is possible to prevent the separation of the gas-liquid two-phase refrigerant into the gas refrigerant and the liquid refrigerant, and to a plurality of heat transfer tubes located downstream of the distributor. Gas refrigerant and liquid refrigerant can be evenly supplied.

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 distributor related to Embodiment 1. FIG. 1 is a perspective view of a distributor according to Embodiment 1; FIG. FIG. 4 is a cross-sectional view perpendicular to the extending direction of the main body 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. 11 is a first explanatory diagram for explaining the action of the bulging portion; FIG. 11 is a second explanatory diagram for explaining the action of the bulging portion; FIG. 10 is a diagram showing the relationship between the flooding constant and the height inside the distributor; 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. 10 is a perspective view of a main body of a distributor according to Embodiment 2; FIG. 11 is a schematic diagram of a distributor related to Embodiment 3; FIG. 11 is a conceptual cross-sectional view of an orifice plate used in a distributor according to Embodiment 3; FIG. 11 is a conceptual cross-sectional view of a first alternative form of an orifice plate used in a distributor according to Embodiment 3; FIG. 11 is a conceptual cross-sectional view of a second alternative form of an orifice plate used in a distributor according to Embodiment 3; FIG. 11 is a conceptual cross-sectional view of a third alternative form of an orifice plate used in a distributor according to Embodiment 3; FIG. 10 is a diagram showing a first relationship of liquid distribution deviation to height within the distributor; FIG. 10 is a diagram showing a second relationship of the liquid distribution deviation to the intra-distributor height; FIG. 5 is a relational diagram between the flow rate of gas-liquid two-phase refrigerant and heat exchanger performance when any one of the distributors of Embodiments 1 to 3 is applied. FIG. 3 is a first schematic diagram showing the relationship between a heat exchanger to which the distributor according to Embodiments 1 to 3 is applied and an outdoor fan. FIG. 4 is a second schematic diagram showing the relationship between a heat exchanger to which the distributor according to Embodiments 1 to 3 is applied and an outdoor fan. FIG. 2 is a first schematic diagram showing the relationship between a heat exchanger to which a distributor according to Embodiments 1 to 3 is applied and an indoor fan. FIG. 4 is a second schematic diagram showing the relationship between a heat exchanger to which the distributor according to Embodiments 1 to 3 is applied and an indoor fan. FIG. 4 is a third schematic diagram showing the relationship between a heat exchanger to which the distributor according to Embodiments 1 to 3 is applied and an indoor fan. FIG. 4 is a fourth schematic diagram showing the relationship between another heat exchanger to which the distributor according to Embodiments 1 to 3 is applied and an indoor fan.

Hereinafter, embodiments for implementing 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. Moreover, in each embodiment, the same reference numerals are given to the same or equivalent parts as those explained in the preceding embodiments, and the explanation thereof may be omitted. 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. Further, the following embodiments can be partially combined with each other, even if not explicitly stated, as long as there is no particular problem with the combination.

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 pipes to circulate the refrigerant. It constitutes a refrigerant circuit that 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 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 point C where it becomes 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 point C flows through the outdoor heat exchanger 5, causing 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, the operating state of the air conditioner 10 during cooling operation will be described along the flow of the refrigerant with reference to FIG. 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 flow path switching device 2 and reaches the 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 to reach a point B where it becomes 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. 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. 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 distributor 20, and a header 80. As shown in FIG. Note that the distributor 20 may be called a header.

(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 distributor 20 and the header 80 . The heat exchange section 50a includes a plurality of heat transfer tubes 12 extending in the first direction (X-axis direction) so as to connect the distributor 20 and the header 80, and heat transfer promoting members 13 connecting the adjacent heat transfer tubes 12 to each other. and

The heat exchange section 50 a is provided such that each of the plurality of heat transfer tubes 12 extends between the distributor 20 and the header 80 . Each of the plurality of heat transfer tubes 12 is formed in a tubular shape and circulates a refrigerant therein. Each of the heat transfer tubes 12 has one end connected to the distributor 20 and the other end connected to the header 80 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 distributor 20 . The plurality of heat transfer tubes 12 are arranged at intervals in the vertical 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 extension 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 section or an elliptical tube. Alternatively, the heat transfer tube 12 may be a flat tube 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 .

Note that the heat exchange portion 50a is not limited to one 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 50a2 positioned upstream of the circulating refrigerant and a main heat exchange section 50a1 positioned downstream of the circulating refrigerant. A distributor 20 is arranged on one end side of the main heat exchange portion 50a1 in the X-axis direction, and a header 80 is arranged on the other end side thereof.

In the heat exchanger 50, the refrigerant whose flow is branched into two flows through the auxiliary heat exchange section 50a2, which constitutes a part of the heat exchange section 50a. Refrigerants flow through the main heat exchange portions 50a1 that form other portions of the heat exchange portion 50a. Note that the heat exchange section 50a is limited to the above configuration having the auxiliary heat exchange section 50a2 positioned upstream of the circulating refrigerant and the main heat exchange section 50a1 positioned downstream of the circulating refrigerant. is not. For example, the heat exchange section 50a may be composed of only the main heat exchange section 50a1 without the auxiliary heat exchange section 50a2. Also, in the heat exchange section 50a, the number of branches of the refrigerant in the auxiliary heat exchange section 50a2 and the main heat exchange section 50a1 may be different from 2 and 16 described above. That is, the numbers of branches of the auxiliary heat exchange section 50a2 and the main heat exchange section 50a1 may be different from those of this embodiment.

(Header 80)
The header 80 is connected to one end of the plurality of heat transfer tubes 12 in the extending direction (X-axis direction). The header 80 is connected to the heat transfer tubes 12 of the heat exchange section 50a so that the inside of the header 80 and the inside of the heat transfer tubes 12 are communicated with each other. The header 80 is formed 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 heat exchange section 50a.

The header 80 is provided with an outflow pipe 301 . The outflow pipe 301 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.

(Distributor 20)
The distributor 20 is connected to the other ends of the plurality of heat transfer tubes 12 in the extending direction (X-axis direction). The distributor 20 is arranged on the opposite side of the header 80 via the plurality of heat transfer tubes 12 . The distributor 20 is connected to the heat transfer tubes 12 of the heat exchange section 50a so that the inside of the distributor 20 and the pipeline of the heat transfer tubes 12 communicate with each other. The distributor 20 is formed to extend along the arrangement direction (Z-axis direction) of the plurality of heat transfer tubes 12 . The distributor 20 distributes the refrigerant to the multiple heat transfer tubes 12 . In the heat exchanger 50 , the distributor 20 functions as a distribution mechanism that distributes the refrigerant flowing into the heat exchange section 50 a to the plurality of heat transfer tubes 12 .

The distributor 20 is provided with an inflow pipe 31 and an inflow pipe 32 . The inflow pipe 31 and the inflow pipe 32 are pipes for causing the refrigerant distributed to the plurality of heat transfer pipes 12 to flow into the heat exchanger 50 . The inflow pipe 31 and the auxiliary heat exchange section 50 a 2 are connected by a pipe 201 , and the inflow pipe 32 and the auxiliary heat exchange section 50 a 2 are connected by a pipe 202 . A detailed configuration of the distributor 20 will be described later.

[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 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 with reference to FIG. 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 has a dryness X of 0.05 to 0.30. flows into the bifurcated pipe 11 from the pipe 100 in the figure in a gas-liquid two-phase state in the range of . In addition, the pipe 100 is a pipe that constitutes a refrigerant flow path between the heat exchanger 50 and the decompression device 4 .

After that, the gas-liquid two-phase refrigerant is branched by the two-branch pipe 11, flows into the pipes 101 and 102, respectively, and flows into the auxiliary heat exchange section 50a2. At this time, the gas-liquid two-phase refrigerant flowing through the heat transfer tubes 14 of the auxiliary heat exchange section 50a2 and the air flowing by the outdoor fan 6 (see FIG. 1) exchange heat. 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 50a2.

The gas-liquid two-phase refrigerant that has passed through the auxiliary heat exchange section 50a2 flows through the pipes 201 and 202 to the inflow pipes 31 and 32, respectively. At this time, the dryness X of the gas-liquid two-phase refrigerant flowing into the inflow pipe 31 and the inflow pipe 32 can range from about 0.05 to 0.60. The value of dryness X is the ratio of the auxiliary heat exchange section 50a2 to the entire heat exchange section 50a, the air volume passing through the auxiliary heat exchange section 50a2, or the pressure from the bifurcated pipe 11 to the inflow pipe 31 and the inflow pipe 32. Varies depending on the impact of losses, etc.

The gas-liquid two-phase refrigerant that has passed through the inflow pipe 31 and the inflow pipe 32 flows into the spaces 21a and 21b (see FIG. 3) formed inside the distributor 20 . The gas-liquid two-phase refrigerant that has flowed into the spaces 21a and 21b is divided into 8 branches in each of the spaces 21a and 21b, that is, a total of 16 branches, and flows into the heat transfer tubes 12 .

The gas-liquid two-phase refrigerant distributed to the 16 branches flows to the main heat exchange portion 50a1, and heat exchange is performed between the air flowing by the outdoor fan 6 (see FIG. 1) and the gas-liquid two-phase refrigerant. The refrigerant passing through the main heat exchange portion 50a1 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 degree of dryness X is 0.85 or more. It becomes a two-phase refrigerant and flows out to the header 80 . The 16 branched refrigerants join together at the header 80 and flow out of the heat exchanger 50 through the outflow pipe 301 .

(Detailed configuration of distributor 20)
FIG. 3 is a schematic diagram of distributor 20 according to the first embodiment. FIG. 4 is a perspective view of the distributor 20 according to Embodiment 1. FIG. FIG. 4 omits illustration of the lid 41 in order to explain the internal structure of the 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 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 distributor 20 will be described with reference to FIGS. 3 and 4. FIG. The distributor 20, as shown in FIG. 3, has a body portion 20a and an inflow pipe 31 and an inflow pipe 32 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 20a of the distributor 20 is installed in a state in which the central axis in the longitudinal direction (Z-axis direction) is vertical, or in a state in which the central axis in the longitudinal direction is tilted within a range having a vertical vector component. An inlet 34 and an internal space 21 are formed in the body portion 20a.

The inflow port 34 is connected to the inflow pipe 31 or the inflow pipe 32 and is an inflow port through which the refrigerant flows from the inflow pipe 31 or the inflow pipe 32 . The internal space 21 communicates with the tube inner space of the heat transfer tube 12 and with the tube inner spaces of the inflow pipe 31 and the inflow pipe 32. It is a space that flows in a direction.

The body portion 20 a has a first part 23 , a second part 24 , lids 41 and 42 , and a partition plate 61 . 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 main body portion 20a of the 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. 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 distributor 20 including the first component 23 may be referred to as an axis-perpendicular cross section. The first component 23 has an insertion surface portion 25 forming a curved portion and a side surface portion 26 forming a flat portion. 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 straight line shape. The insertion surface portion 25 is curved so as to protrude toward the side where the heat transfer tubes 12 are arranged. 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 component 23 is formed so that two side surface portions 26 face each other, and both end portions of an insertion surface portion 25 formed in an arc shape in a cross section perpendicular to the longitudinal direction (Z-axis direction) of the first component 23 are provided. A side portion 26 is provided on each side. 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 facing surface portion, which 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 connection port 33 into which the heat transfer tube 12 is inserted is formed in the insertion surface portion 25 of the first component 23 . The connection port 33 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 33 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 33 and penetrates the wall of the first component 23 . The heat transfer tube 12 inserted into the connection port 33 is held by the first component 23 .

The second part 24 is a facing surface portion facing the insertion surface portion 25 in the direction in which the plurality of heat transfer tubes 12 extend. 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 part 24, which is the facing surface portion, includes a flat plate portion 28 connected to the side surface portion 26, and a portion of the inner wall forming the internal space 21 of the distributor 20 facing the insertion surface portion 25 in the axis-perpendicular cross section of the distributor 20. and a bulging portion 27 that bulges from the flat plate portion 28 . 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 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 provided between the 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 single 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 34 into which the inflow pipe 31 and the inflow pipe 32 are inserted is formed in the bulging portion 27 of the second component 24, which is the facing surface portion. The inflow port 34 is a through hole. The inlet pipe 31 and the inlet pipe 32 are inserted into the inlet 34 and penetrate the wall of the second part 24 . The inflow pipe 31 and the inflow pipe 32 inserted into the inflow port 34 are held by the second part 24 .

The inlet 34 is formed inside the main body 20a at a position facing the heat transfer tube 12 positioned at the bottom among the plurality of heat transfer tubes 12 . Alternatively, as shown in FIG. 3 , the inlet 34 is formed inside the main body 20a so as to be positioned below the lowermost heat transfer tube 12 among the plurality of heat transfer tubes 12 .

The main body portion 20a is formed such that a bulging portion 27 is positioned between two opposing side surface portions 26. As shown in FIG. 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 . In a cross section perpendicular to the longitudinal direction (Z-axis direction) of the body portion 20a, the internal space 21 is formed in a substantially U shape.

A representative manufacturing method of the body portion 20a is as follows. The first part 23 is formed with a connection port 33 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 33 and bending work for forming the curved surface, and is formed as a semicircular pressed plate component.

The second part 24 has an inflow port 34 that serves as a connection port for the inflow pipe 31 and the inflow pipe 32, and 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 34 and bending for forming the curved surface, and is molded as a pressed plate part having the bulging portion 27 .

The method for manufacturing 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 33 and the inlet port 34, 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 by using another means such as electric resistance welding pipe processing. may

The distributor 20 has a cover 41 and a cover 42 that form 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 . 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.

A partition plate 61 is provided inside the body portion 20a to divide the internal space 21 of the body portion 20a into upper and lower spaces. An upper space 21a and a lower space 21b are formed by a partition plate 61 inside the body portion 20a. In the internal space 21 of the body portion 20 a , an upper space 21 a is a space formed above the partition plate 61 and a lower space 21 b is a space formed below the partition plate 61 . Since the upper space 21a and the lower space 21b are separated by the partition plate 61, the coolant does not move between the upper space 21a and the lower space 21b. The distributor 20 has at least one or more partition plates 61 . Note that the partition plate 61 is not an essential component of the distributor 20, and the distributor 20 may not have the partition plate 61.

As shown in FIG. 3, in the body portion 20a, the portion forming the upper space 21a is the upper body portion 20a1, and the portion forming the lower space 21b is the lower body portion 20a2. A connection port 33 and an inlet 34 are formed in the upper body portion 20a1 and the lower body portion 20a2, respectively. As shown in FIGS. 2 and 3, eight connection ports 33 are formed in each of the upper body portion 20a1 and the lower body portion 20a2, and 16 connection ports 33 are formed in the body portion 20a as a whole.

A plurality of heat transfer tubes 12 pass through the connection port 33 of the upper main body portion 20a1, and a plurality of other heat transfer tubes 12 pass through the connection port 33 of the lower main body portion 20a2. A plurality of heat transfer tubes 12 are attached to the upper body portion 20a1, and a plurality of other heat transfer tubes 12 are attached to the lower body portion 20a2. Note that the number of connection openings 33 formed in the body portion 20a is not limited to 16 pieces. The number of connection ports 33 to be formed is defined by the number of heat transfer tubes 12 included in the heat exchange section 50a.

(Inflow pipe 31 and inflow pipe 32)
An inflow pipe 31 and an inflow pipe 32 are attached to the body portion 20a. The inflow pipe 31 is attached to the upper body portion 20a1, and the inflow pipe 32 is attached to the lower body portion 20a2. The inflow pipe 31 and the inflow pipe 32 communicate with the internal space 21 of the body portion 20a.

The inflow pipe 31 communicates with the upper space 21a, and the inflow pipe 32 communicates with the lower space 21b. The gas-liquid two-phase refrigerant flowing through the internal space 21 of the main body 20 a flows into the inflow pipe 31 and the inflow pipe 32 when the heat exchanger 50 functions as an evaporator. As shown in FIG. 2 , the inflow pipe 31 is connected to the pipe 201 and the inflow pipe 32 is connected to the pipe 202 . In addition, when the heat exchange section 50a does not have the auxiliary heat exchange section 50a2, the inflow pipe 31 and the inflow pipe 32 may be connected to the bifurcated pipe 11 via the pipe 101 and the pipe 102, respectively.

Next, attachment positions of the inflow pipe 31 and the inflow pipe 32 will be described with reference to FIG. The inflow pipe 31 is located at a position facing the heat transfer tube 12 located at the bottom of the 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. 12 is preferably attached along the direction of extension (the X-axis direction). Similarly, the inflow pipe 32 is located at a position facing the heat transfer tube 12 located at the bottom of the space 21b, 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. , preferably along the direction in which the heat transfer tubes 12 extend (the X-axis direction).

If the installation position of the inflow pipe 31 and the inflow pipe 32 is set at the midpoint between the heat transfer tubes 12 in the space 21a or the space 21b, 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 inflow pipe 31 and the inflow pipe 32 are desirably attached at the positions described above.

Next, the characteristics of the working fluid when using the distributor 20 of this embodiment will be described. When the gas-liquid two-phase refrigerant flowing from the inflow pipe 31 and the inflow pipe 32 respectively flows vertically upward through the spaces 21a and 21b in the distributor 20, the plurality of heat transfer tubes 12 connected to the first part 23 , the upward flow velocity decreases step by step.

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. Here, the cross-sectional area of the internal space 21 of the distributor 20 in the cross-sectional view taken along the line AA shown in FIG. 5 is defined as the cross-sectional area S1 [m ² ]. Also, the cross-sectional area of the internal space 21 of the distributor 20 in the cross-sectional view along the line BB shown in FIG. 6 is defined as S2 [m ² ].

Also, the peripheral length of the cross section of the distributor 20 forming the cross-sectional area S1 is defined as the wetting edge length L1 [m]. Also, the peripheral length of the cross section of the distributor 20 forming the cross-sectional area S2 is defined as the wetting edge length L2 [m]. Also, let D1 [m] be the hydraulic equivalent diameter in the cross section of the distributor 20 forming the cross-sectional area S1. Also, let D2 [m] be the hydraulic equivalent diameter in the cross section of the distributor 20 forming the cross-sectional area S2. 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[-] are calculated from 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 C2[-] in the cross-sectional area S2 is less than 0.5, 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 C2[-] has a flow velocity of 0.5 or more.

As shown in FIGS. 5 and 6, the body portion 20a of the distributor 20 is formed with a corner portion 21c and a corner portion 21d. Distributor 20 may have only one of corner 21c and corner 21d, or may have both corner 21c and corner 21d. The corners 21 c and 21 d are spaces surrounded by the flat plate portion 28 , the bulging portion 27 and the side surface 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 distributor 20 can suppress the fall of the liquid refrigerant by the surface tension acting on the corners 21c and 21d.

In addition, by providing the corners 21c and 21d of the distributor 20, the distance between the heat transfer tubes 12 and the joints 28a between the side surface 26 and the flat plate 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. 7 is a first explanatory diagram for explaining the action of the bulging portion 27. As shown in FIG. FIG. 8 is a second explanatory diagram for explaining the action of the bulging portion 27. As shown in FIG. A first tangent line J 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 body portion 20a. When viewed in a direction parallel to the longitudinal direction of the distributor 20 and the main body portion 20a, the first tangent line J is perpendicular to the direction in which the plurality of heat transfer tubes 12 extend (the X-axis direction). The top portion 27 b 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 . A second tangent line K is defined as a line that is parallel to the first tangent line J and that is in contact with the flat plate portion 28 that is the farthest from the insertion surface portion 25 and that forms the inner wall of the internal space 21 .

As shown in FIG. 7, a cross-sectional area surrounded by the first tangent line J, the second tangent line K, and the side surface portion 26 is defined as a specific cross-sectional area SA. Then, as shown in FIG. 8, the cross-sectional area of the portion corresponding to the internal space 21 in the specific cross-sectional area SA is defined as a first cross-sectional area SA1, and the cross-sectional area of the portion other than the internal space 21 in the specific cross-sectional area SA is defined as a second cross-sectional area SA2. The distributor 20 is formed such that the second cross-sectional area SA2 is greater than or equal to the first cross-sectional area SA1 (second cross-sectional area SA2≧first cross-sectional area SA1). With this relationship between the first cross-sectional area SA1 and the second cross-sectional area SA2, the distributor 20 can minimize the second cross-sectional area SA2 and increase the wet edge length L2. can do. Therefore, the 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 and the intra-distributor height. "Conventional" shown in FIG. 9 indicates a distributor that does not have the distributor 20 of the present disclosure, and "Embodiment" indicates the distributor 20 of this embodiment. As shown in FIG. 9, as the height position in the distributor 20 increases, the gas-liquid two-phase refrigerant is sequentially discharged to the heat transfer tubes 12, so the flooding constant decreases. In the conventional distributor, the hydraulic equivalent diameter D2 of the internal space 21 becomes large, so the flooding constant C2 becomes small and the flooding constant falls below 0.5, thereby causing separation between the gas refrigerant and the liquid refrigerant. It therefore happens that conventional distributors are only supplied with gaseous refrigerant at the top of the height within the distributor. Therefore, in the conventional distributor, the distribution of the gas-liquid two-phase refrigerant becomes uneven, and the heat exchanger performance tends to deteriorate.

On the other hand, in the distributor 20 of the present disclosure, by having the bulging portion 27, the flooding constant C2 can be increased as described above. Distributable.

[Action and effect of heat exchanger 50]
The distributor 20 of the present disclosure can increase the flooding constant C2 as described above by having the bulging portion 27 as described above. Phase refrigerant can be distributed. Therefore, the distributor 20 can prevent the separation of the gas refrigerant and the liquid refrigerant, and the gas refrigerant and the liquid refrigerant are evenly distributed to the heat exchange section 50a composed of the plurality of heat transfer tubes 12 located downstream of the distributor 20. and can be supplied. Therefore, the heat exchanger 50 having the distributor 20 can suppress deterioration in heat exchanger performance.

In addition, since the inner space 21 of the distributor 20 is narrow due to the bulging portion 27, excessive refrigerant is not supplied to the upper portion due to pressure loss, compared to the conventional distributor.

Further, the distributor 20 is formed so that the second cross-sectional area SA2 is greater than or equal to the first cross-sectional area SA1. With this relationship between the first cross-sectional area SA1 and the second cross-sectional area SA2, the distributor 20 can minimize the second cross-sectional area SA2 and increase the wet edge length L2. can do. Therefore, the distributor 20 can reduce the hydraulic equivalent diameter D2, and as a result, can also increase the flooding constant C2. Therefore, the distributor 20 can prevent the separation of the gas refrigerant and the liquid refrigerant, and the gas refrigerant and the liquid refrigerant are evenly distributed to the heat exchange section 50a composed of the plurality of heat transfer tubes 12 located downstream of the distributor 20. and can be supplied. Therefore, the heat exchanger 50 having the distributor 20 can suppress deterioration in heat exchanger performance.

Further, the inlet 34 is formed inside the main body portion 20a at a position facing the heat transfer tube 12 positioned at the bottom among the plurality of heat transfer tubes 12 . Alternatively, as shown in FIG. 3 , the inlet 34 is formed inside the main body 20a so as to be positioned below the lowermost heat transfer tube 12 among the plurality of heat transfer tubes 12 . If the installation position of the inflow pipe 31 and the inflow pipe 32 connected to the inflow port 34 is at the middle point between the heat transfer tubes 12 in the internal space 21, the upward flow and the downward flow of the refrigerant will be different. As a result, the flow velocity for upward flow of the gas-liquid two-phase refrigerant 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, it is desirable that the formation position of the inflow port 34 to which the inflow pipe 31 and the inflow pipe 32 are connected is formed at the position described above.

At least a part of the insertion surface portion 25 is formed so as to be convex on the side opposite to the facing surface portion. As the body portion 20a of the distributor 20 is closer to a circular shape, the pressure resistance in the distributor 20 increases.

Further, the distributor 20 has lids 41 and 42 that close both ends of the distributor 20 in the longitudinal direction and form an internal space 21 together with an insertion surface portion 25 , a facing surface portion, and a side surface portion 26 . Without the lids 41 and 42 above and below the distributor 20 , the refrigerant would leak out and the space would not be closed, so the distributor 20 has the lids 41 and 42 . The distributor 20 can easily form a closed space by closing the upper and lower ends with the lids 41 and 42 rather than forming the closed space by bending the upper and lower ends of the distributor 20 at right angles and crushing the ends. .

In addition, the distributor 20 has at least one partition plate 61 that separates the inner space 21 into an upper space and a lower space in the longitudinal direction of the distributor 20 . When it is desired to divide the heat exchanger 50 and the distributor 20 so that there are a plurality of inflow points by the inlet 34, the division can be achieved by making one long distributor 20 and separating the internal space 21 with a partition plate 61. The manufacturing cost and material cost can be reduced compared to individually manufacturing a plurality of distributors 20 in the required number.

Moreover, the distributor 20 is formed in a tubular shape by combining the first part 23 and the second part 24 . Although it is possible to manufacture a cylinder in which the insertion surface portion 25, the side surface portion 26, and the opposing surface portion are all integrated by extrusion molding, the connection port 33 and the inlet port 34 must be cut after extrusion molding, which increases the manufacturing cost. It takes Since the distributor 20 is composed of two halves of 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 kept low. be able to.

As described above, the distributor 20 according to the present embodiment improves the uneven distribution of the gas-liquid two-phase refrigerant to equal distribution by using only the simple structural element of the bulging portion 27, and the size of the distributor 20 main body is improved. can be minimized. In addition, since the size of the main body 20a of the distributor 20 can be minimized, the material cost can be reduced and the mounting space can be reduced.

Embodiment 2.
FIG. 10 is a conceptual cross-sectional view of bulging portion 27 according to the second embodiment. Components having the same functions and actions as those of the distributor 20 and the like according to the first embodiment are denoted by the same reference numerals, and descriptions thereof are omitted. FIG. 10 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.

FIG. 11 is a conceptual cross-sectional view of a first alternative form of the bulging portion 27 according to the second embodiment. FIG. 12 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. 11, or may be formed in a triangular shape as shown in FIG. good too.

FIG. 13 is a conceptual cross-sectional view of a third alternative form of the bulging portion 27 according to the second embodiment. FIG. 14 is a conceptual cross-sectional view of a fourth alternative form of the bulging portion 27 according to the second embodiment. FIG. 15 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. 13, 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. 14, the shape of the vertical cross section of the bulging portion 27 may be formed such that a plurality of small square rectangular convex portions 27d are continuous. Moreover, as shown in FIG. 15, 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 continuously formed.

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.

FIG. 16 is a perspective view of main body 20a of distributor 20 according to the second embodiment. As an example of the distributor 20, the distributor 20 having the fourth variant bulging portion 27 shown in FIG. 14 will be described with reference to FIG. Distributor 20 shown in FIG. 16 has bulging portion 27 in which a plurality of small rectangular convex portions 27d are continuously formed, unlike semicircular bulging portion 27 described in the first embodiment. is doing. Therefore, the distributor 20 shown in FIG. 16 forms a plurality of projecting surfaces by a plurality of rectangular projections 27d projecting into the internal space 21. As shown in FIG.

[Action and effect of heat exchanger 50]
Generally, in the gas-liquid two-phase refrigerant that flows upward in the distributor, the liquid refrigerant tends to concentrate on the wall surface in the distributor, and the gas refrigerant tends to concentrate in the center of the cavity in the distributor. In the distributor 20 of FIG. 16, a plurality of protruding surfaces are formed by a plurality of rectangular protrusions 27d forming the bulging portion 27, thereby increasing the contact area between the wall surface of the bulging portion 27 and the gas-liquid two-phase refrigerant. can be made Therefore, in the distributor 20, the surface tension of the gas-liquid two-phase refrigerant is increased, compared to the configuration of the single semicircular bulging portion 27 as in the first embodiment, and the liquid refrigerant falls. can be suppressed.

16 has a plurality of protruding surfaces formed by a plurality of rectangular convex portions 27d forming the protruding portion 27, thereby forming a single semicircular protruding portion as in the first embodiment. 27, the wet edge length L2 is increased. Therefore, the distributor 20 has a larger flooding constant C2 than the configuration of the single semicircular swelling portion 27 as in the first embodiment, and can suppress the separation of the gas refrigerant and the liquid refrigerant. Therefore, in the distributor 20 shown in FIG. 16, the supply of liquid refrigerant to the upper portion of the distributor 20 is more likely to increase than in the distributor 20 of the first embodiment. Further, when the second part 24 is manufactured by extrusion molding, the distributor 20 according to the second embodiment has the shape of the bulging portion 27 formed by a plurality of convex portions as shown in FIGS. Even if there is, it can be manufactured at a low cost as in the case of the first embodiment.

As described above, the distributor 20 according to the second embodiment increases the amount of liquid refrigerant supplied to the upper portion of the distributor 20 by increasing the peripheral length of the bulging portion 27 provided in the second component 24. can. Therefore, the distributor 20 according to the second embodiment can exhibit the effect of improving uniform distribution of the gas-liquid two-phase refrigerant more than the distributor 20 according to the first embodiment.

Embodiment 3.
FIG. 17 is a schematic diagram of distributor 20 according to the third embodiment. Components having the same functions and actions as those of the distributor 20 and the like according to Embodiments 1 and 2 are assigned the same reference numerals, and descriptions thereof are omitted. The distributor 20 of the third embodiment has a plate-like orifice plate 91 that separates the internal space 21 of the body portion 20a of the distributor 20 of the first or second embodiment in the vertical direction (Z-axis direction). ing. Distributor 20 of Embodiment 3 has orifice plate 91 in each of upper body portion 20a1 and lower body portion 20a2.

An orifice plate 91 is provided in an internal space 21a of the upper main body portion 20a1 of the main body portion 20a, and the orifice plate 91 separates the space 21a into an upper space 21a1 and a lower space 21a2. In the internal space 21 of the upper body portion 20 a 1 , an upper space 21 a 1 is a space formed above the orifice plate 91 and a lower space 21 a 2 is a space formed below the orifice plate 91 .

An orifice plate 91 is provided in an internal space 21b of the lower body portion 20a2 of the body portion 20a, and the space 21b is separated by the orifice plate 91 into an upper space 21b1 and a lower space 21b2. In the internal space 21 of the lower body portion 20 a 2 , an upper space 21 b 1 is a space formed above the orifice plate 91 and a lower space 21 b 2 is a space formed below the orifice plate 91 .

As shown in FIG. 17, an orifice hole 92 is formed in an 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 upper space 21a1 and the lower space 21a2 communicate with each other through the orifice hole 92 of the orifice plate 91 in the space 21a inside the upper body portion 20a1. In the upper body portion 20a1, the coolant flows through the orifice holes 92 of the orifice plate 91, and moves from the lower space 21a2 to the upper space 21a1 through the orifice holes 92. As shown in FIG.

Similarly, an upper space 21b1 and a lower space 21b2 communicate with each other through the orifice hole 92 of the orifice plate 91 in the space 21b inside the lower body portion 20a2. In the lower body portion 20a2, the coolant flows through the orifice holes 92 of the orifice plate 91, and moves from the lower space 21b2 to the upper space 21b1 through the orifice holes 92.

[Action and effect of heat exchanger 50]
In general, when the gas-liquid two-phase refrigerant flowing from the inflow pipe has a low flow rate, the pressure loss of the refrigerant in the heat transfer tubes located downstream of the distributor becomes very small. The refrigerant distribution performance deteriorates due to the influence of the head difference. In the distributor, the low-density gas refrigerant, which is not easily affected by the head difference, is excessively supplied to the heat transfer tubes located in the upper part of the internal space of the distributor, and is undersupplied to the heat transfer tubes located in the lower part of the internal space. It is necessary to suppress the unequal distribution of In the distributor 20 of the third embodiment, by providing an orifice plate 91 having an orifice hole 92 in the internal space 21, the inflow of gas refrigerant having a low density going upward is suppressed, The gas refrigerant supplied to the located heat transfer tubes 12 can be increased.

More specifically, the liquid density is about 45 to 50 times greater than the gas density, and in general, the head difference (potential energy) is greater to lift the liquid refrigerant to the upper part of the distributor than to lift the gas refrigerant. It needs to be configured to Therefore, in general, when the gas-liquid two-phase refrigerant has a low flow rate, the low-density gas refrigerant is biased toward the upper portion of the distributor. When the flow rate of the gas-liquid two-phase refrigerant is high, the liquid refrigerant is also likely to be supplied to the upper portion of the distributor due to the force of inertia.

On the other hand, the distributor 20 of Embodiment 3 has an orifice plate 91 having orifice holes 92 . Since the pressure loss generated when the refrigerant passes through the orifice holes 92 increases as the density decreases, the liquid refrigerant can reduce the pressure loss when passing through the orifice holes 92 more than the gas refrigerant. The gas refrigerant is not easily affected by the head difference, but avoids pressure loss passing through the orifice hole 92 and easily flows to the lower portion of the distributor 20 . In the distributor 20, since the gas refrigerant flows to the lower part of the distributor 20, part of the liquid refrigerant that tends to flow to the lower part of the distributor 20 is pushed away to the upper part of the distributor 20, causing the gas to flow to the upper part of the distributor 20. A portion of refrigerant and a portion of liquid refrigerant can be supplied. Therefore, the distributor 20 can prevent the separation of the gas refrigerant and the liquid refrigerant, and the gas refrigerant and the liquid refrigerant are evenly distributed to the heat exchange section 50a composed of the plurality of heat transfer tubes 12 located downstream of the distributor 20. and can be supplied.

The orifice plate 91 is provided to suppress excessive supply of gas refrigerant to the upper portion of the main body portion 20a, as described above. Here, among the branches of the refrigerant distributed by the distributor 20, the lowermost branch is defined as the first branch, and the uppermost branch is defined as the Nth branch. The position of the "branch" is also the position where the heat transfer tubes 12 are arranged.

The orifice plate 91 is preferably arranged at a position between the (N/2)th branch and the (N/2+1)th branch and below that position. For example, consider the case where the refrigerant is split into eight by the distributor 20 . A position between the first (lowest) heat transfer tube 12 to the fourth heat transfer tube 12 and the fifth heat transfer tube 12 is defined as the first position. A position between the first (lowest) heat transfer tube 12 and the second heat transfer tube 12 is defined as a second position. The orifice plate 91 is desirably positioned anywhere in the space between the first position and the second position.

FIG. 18 is a conceptual cross-sectional view of orifice plate 91 used in distributor 20 according to the third embodiment. 18 is a cross-sectional view taken along line CC of distributor 20 shown in FIG. The orifice plate 91 shown in FIG. 18 has one circular orifice hole 92 formed near the center of the orifice plate 91 . By using the orifice plate 91 having such a configuration, the distributor 20 can suppress non-uniformity of the gas refrigerant at the time of low flow rate.

FIG. 19 is a conceptual cross-sectional view of a first alternative form of orifice plate 91 used in distributor 20 according to the third embodiment. FIG. 20 is a conceptual cross-sectional view of a second alternative form of orifice plate 91 used in distributor 20 according to the third embodiment. FIG. 21 is a conceptual cross-sectional view of a third alternative form of orifice plate 91 used in distributor 20 according to the third embodiment. 19 to 21 are cross-sectional views of the distributor 20 shown in FIG. 17 taken along line CC.

Also, as shown in FIG. 19, the orifice plate 91 may be formed with two orifice holes 92 . The orifice plate 91 has an orifice hole 92 formed in a circular shape as shown in FIGS. 18 and 19 when viewed in a direction parallel to the longitudinal direction of the main body 20a. It may also be formed in a rectangular shape, as shown in FIG. Further, the orifice plate 91 may be formed so that the orifice hole 92 has an oval shape (not shown).

18 and 20, the orifice plate 91 may be formed at the central portion of the orifice plate 91. As shown in FIGS. may be formed in The orifice plate 91 shown in FIG. 21 may be formed such that each of the two orifice holes 92 is a space surrounded by the side surface portion 26, the flat plate portion 28, the protruding portion 27, and the orifice plate 91. good. In other words, the orifice holes 92 may be formed in the corners 21c and 21d described above.

The orifice hole 92 is desirably formed so as to be positioned near the inner wall surface of the main body portion 20a in order to allow liquid refrigerant, which tends to concentrate near the wall surface, to pass therethrough. When the orifice holes 92 are formed near the inner wall surface of the main body 20a, the distributor 20 suppresses the upper supply of the gas refrigerant due to the presence of the orifice holes 92, and the orifice holes 92 are formed. Depending on the position, the top supply of liquid refrigerant can be encouraged.

In the distributor 20 according to Embodiment 3, when the gas-liquid two-phase refrigerant flowing into the body portion 20a has a low flow rate, the orifice plate 91 having the orifice hole 92 of a simple element is formed in the body portion 20a. By being provided inside, it is possible to suppress uneven distribution of the gas refrigerant. Distributor 20 of the third embodiment has orifice plate 91 formed with orifice hole 92 which is a simple element, provided in main body 20a. , the uniform distribution of the refrigerant can be achieved even under a wide range of refrigerant inflow conditions.

FIG. 22 is a diagram showing a first relationship of the liquid distribution deviation to the height inside the distributor. "Conventional" shown in FIG. 22 indicates a distributor that does not have the distributor 20 of the present disclosure, and "Embodiment" indicates the distributor 20 according to the third embodiment. FIG. 22 shows the relationship between the internal height of the distributor 20 and the liquid distribution deviation when the amount of refrigerant flowing into the distributor 20 is small.

In the case of a general conventional distributor having a perfect circular cross section perpendicular to the axial direction, the liquid refrigerant is separated from the gas refrigerant, so as shown in FIG. The supply amount is greatly reduced compared to the supply amount at other locations. On the other hand, in the case of the distributors 20 according to Embodiments 1 to 3, since the separation of the liquid refrigerant and the gas refrigerant can be suppressed, as shown in FIG. A supply of liquid refrigerant can be distributed nearly evenly at the location.

Note that the distributor 20 according to Embodiment 2 can more evenly distribute the liquid refrigerant than the distributor 20 according to Embodiment 1, and the distributor 20 according to Embodiment 2 can distribute the liquid refrigerant more evenly. The distributor 20 according to Mode 3 can more evenly distribute the liquid refrigerant. "Embodiment" in FIG. 22 shows the distributor 20 according to Embodiment 3 as an example. In the distributor 20 according to the first embodiment and the distributor 20 according to the second embodiment, as in the "embodiment" of FIG. Indicates a nearly even supply.

FIG. 23 is a diagram showing a second relationship of the liquid distribution deviation to the height inside the distributor. "Conventional" shown in FIG. 23 indicates a distributor that does not have the distributor 20 of the present disclosure, and "Embodiment" indicates the distributor 20 according to the third embodiment. FIG. 23 shows the relationship between the height inside the distributor 20 and the liquid distribution deviation when the refrigerant flowing into the distributor 20 has a large circulation amount.

In the case of a general conventional distributor having a perfect circular cross section perpendicular to the axial direction, the flow velocity of the refrigerant in the distributor 20 is excessively high, so the liquid refrigerant is excessive in the upper part of the distributor 20, as shown in FIG. As shown, the amount of liquid refrigerant supplied to the upper portion of the distributor 20 is greatly increased compared to the amount supplied to other portions. On the other hand, in the case of the distributor 20 according to Embodiments 1 to 3, the internal space 21 is narrowed by the bulging portion 27, or the orifice hole 92 suppresses the inflow of the gas refrigerant directed upward. is no longer supplied to the top compared to the conventional distributor due to pressure loss. Therefore, in the distributors 20 according to Embodiments 1 to 3, as shown in FIG. The supply of liquid refrigerant can be distributed in a near even manner.

As described above, the distributor 20 according to the second embodiment can more evenly distribute the liquid refrigerant than the distributor 20 according to the first embodiment. The distributor 20 according to the third embodiment can more evenly distribute the liquid refrigerant than the distributor 20 can. "Embodiment" in FIG. 23 shows the distributor 20 according to Embodiment 3 as an example. In the distributor 20 according to the first embodiment and the distributor 20 according to the second embodiment, the liquid refrigerant is distributed at all positions of the distributor 20 in the height direction of the distributor 20 in the same manner as the "embodiment" of FIG. Indicates a nearly even supply.

FIG. 24 is a diagram showing the relationship between the flow rate of gas-liquid two-phase refrigerant and heat exchanger performance when the distributor 20 of any one of Embodiments 1 to 3 is applied. "Conventional" shown in FIG. 24 indicates a conventional heat exchanger that does not have the distributor 20 of Embodiments 1 to 3, and "Embodiment" indicates that the distributor 20 of Embodiments 1 to 3 is used. A heat exchanger 50 is shown. As shown in FIGS. 22 and 23, the distributor 20 using any one of the first to third embodiments supplies the liquid refrigerant almost evenly at all locations in the longitudinal direction of the distributor 20. It is possible to distribute with Therefore, as shown in FIG. 24, the heat exchanger 50 is not affected by changes in the flow rate of the gas-liquid two-phase refrigerant compared to conventional heat exchangers, and the performance of the heat exchanger 50 is kept constant. It is possible to maintain a higher performance than conventional heat exchangers.

FIG. 25 is a first schematic diagram showing the relationship between the heat exchanger 50 to which the distributor 20 according to Embodiments 1 to 3 is applied and the outdoor fan 6. As shown in FIG. Arrows shown in FIGS. 25 to 30 indicate the air flow. Further, the outdoor fan 6 and the indoor fan 7 shown in FIGS. 25 to 30 are fans that supply air to the plurality of heat transfer tubes 12 of the heat exchanger 50 that constitutes the outdoor heat exchanger 5 and the indoor heat exchanger 3. .

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. That is, the distributor 20 according to Embodiments 1 to 3 is used for the outdoor heat exchanger 5. FIG.

FIG. 26 is a second schematic diagram showing the relationship between the heat exchanger 50 to which the distributor 20 according to Embodiments 1 to 3 is applied and the outdoor fan 6. As shown in FIG. 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. That is, the distributor 20 according to Embodiments 1 to 3 is used for the outdoor heat exchanger 5. FIG.

FIG. 27 is a first schematic diagram showing the relationship between the heat exchanger 50 to which the distributor 20 according to Embodiments 1 to 3 is applied and the indoor fan 7. As shown in FIG. 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 may be used as the indoor heat exchanger 3 used in the indoor unit 113 . That is, the distributor 20 according to Embodiments 1 to 3 may be used in the indoor heat exchanger 3.

FIG. 28 is a second schematic diagram showing the relationship between the heat exchanger 50 to which the distributor 20 according to Embodiments 1 to 3 is applied and the indoor fan 7. As shown in FIG. 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 household indoor unit, and is equipped with a line flow fan (registered trademark) as the indoor blower 7 . The heat exchanger 50 described above may be used as the indoor heat exchanger 3 used in the indoor unit 114 . That is, the distributor 20 according to Embodiments 1 to 3 may be used in the indoor heat exchanger 3.

FIG. 29 is a third schematic diagram showing the relationship between the heat exchanger 50 to which the distributor 20 according to Embodiments 1 to 3 is applied and the indoor fan 7. As shown in FIG. FIG. 30 is a fourth schematic diagram showing the relationship between another heat exchanger 50 to which the distributor 20 according to Embodiments 1 to 3 is applied and the indoor fan 7. As shown in FIG. 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 units 115 and 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 may be used as the indoor heat exchanger 3 used in the indoor units 115 and 116 . That is, the distributor 20 according to Embodiments 1 to 3 may be used in the indoor heat exchanger 3.

29 and 30, when the indoor heat exchanger 3 is installed inclined with respect to the direction of gravity, the problem of liquid refrigerant falling due to separation of the liquid refrigerant and the gas refrigerant is less likely to occur. However, when the flow rate of the gas-liquid two-phase refrigerant is excessive, the use of the distributor 20 allows the indoor heat exchanger 3 to suppress excessive liquid refrigerant supply to the upper portion of the distributor 20 . Therefore, the distributor 20 according to Embodiments 1 to 3 may be used for the heat exchanger 50 that is installed inclined with respect to the direction of gravity.

The air conditioner 10 includes the heat exchanger 50 according to any one of the first to third embodiments described above. Therefore, the air conditioner 10 can obtain the same effect as any of the heat exchangers 50 according to Embodiments 1-3. Since the air conditioner is provided with the heat exchanger 50, separation of the gas-liquid two-phase refrigerant into gas refrigerant and liquid refrigerant can be prevented, and the gas refrigerant is evenly distributed to the plurality of heat transfer tubes 12 located downstream of the distributor 20. and liquid refrigerant can be supplied.

Each of the first to third embodiments described above 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 a part of For example, the distributor 20 according to Embodiments 1 to 3 may be of a vertical type in which the body portion 20a extends vertically, or may be of a horizontal type in which the body portion 20a extends in the horizontal direction. Further, the distributor 20 according to Embodiments 1 to 3 may be configured such that the main body portion 20a is inclined with respect to the vertical direction.

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.

1 compressor, 2 channel switching device, 3 indoor heat exchanger, 4 decompression device, 5 outdoor heat exchanger, 6 outdoor fan, 7 indoor fan, 10 air conditioner, 11 bifurcated pipe, 12 heat transfer tube, 13 transmission Heat acceleration member 14 Heat transfer tube 20 Distributor 20a Main body 20a1 Upper main body 20a2 Lower main body 21 Internal space 21a Space 21a1 Upper space 21a2 Lower space 21b Space 21b1 Upper space 21b2 Lower Space 21c corner 21d corner 23 first component 24 second component 25 insertion surface portion 26 side surface portion 27 swelling portion 27a facing surface 27b top portion 27c circular convex portion 27d rectangular convex portion , 27e mountain-shaped convex portion, 28 flat plate portion, 28a joint portion, 31 inflow pipe, 32 inflow pipe, 33 connection port, 34 inflow port, 41 lid, 42 lid, 50 heat exchanger, 50a heat exchange portion, 50a1 main heat exchange part 50a2 auxiliary heat exchange part 61 partition plate 80 header 91 orifice plate 92 orifice hole 100 pipe 101 pipe 102 pipe 111 outdoor unit 112 outdoor unit 113 indoor unit 114 indoor unit 115 Indoor unit, 116 indoor unit, 201 pipe, 202 pipe, 301 outflow pipe.

Claims (12)

a plurality of heat transfer tubes arranged at intervals in the vertical direction;
a distributor that distributes the refrigerant to the plurality of heat transfer tubes;
with
The 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 direction in which the plurality of heat transfer tubes extend;
a side wall portion that extends between the insertion surface portion and the facing surface portion in an axis-perpendicular cross section of the distributor and is 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 distributor bulges from the flat plate portion toward the insertion surface portion in the axis-perpendicular cross section. ,
A heat exchanger , wherein a corner surrounded by the flat plate portion, the bulging portion, and the side surface portion is formed as an internal space of the distributor . 2. The heat exchanger according to claim 1, wherein said bulging portion is arcuate or semicircular. The insertion surface portion is
3. The heat exchanger according to claim 1 or 2, wherein at least a portion of the heat exchanger is curved so as to protrude on the side opposite to the facing surface portion. In the axis-perpendicular cross section,
A first tangent line is defined as a tangent line that is in contact with the topmost portion of the bulging portion that is the portion protruding from the flat plate portion to the insertion surface portion side ,
A second tangent line is defined as a line that is in contact with the portion that constitutes the inner wall and is parallel to the first tangent line, which is the flat plate portion that is the farthest from the insertion surface portion, and
A cross-sectional area of a portion surrounded by the first tangent line, the second tangent line, and the side portion is defined as a specific cross-sectional area,
A first cross-sectional area is defined as a cross-sectional area of a portion of the specific cross-sectional area corresponding to the internal space,
When the cross-sectional area of the specific cross-sectional area other than the internal space is defined as a second cross-sectional area,
4. The heat exchanger according to any one of claims 1 to 3, wherein said second cross-sectional area is formed to be larger than said first cross-sectional area. The distributor is
5. The heat exchanger according to any one of claims 1 to 4, further comprising a lid that closes both ends in the longitudinal direction of the distributor and forms the internal space together with the insertion surface portion, the facing surface portion, and the side surface portion. vessel. The distributor is
The heat exchanger according to any one of claims 1 to 5, comprising at least one or more partition plates separating the internal space into an upper space and a lower space in the longitudinal direction of the 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, the heat transfer tube is formed at a position facing the lowermost heat transfer tube among the plurality of heat transfer tubes, or at a position higher than the lowermost heat transfer tube among the plurality of heat transfer tubes The heat exchanger according to any one of claims 1 to 6, which is formed so as to be positioned downward. The 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 7, 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. 3. A heat exchanger according to claim 2, wherein the heat exchanger is formed with one cross-sectional shape. The distributor is
at least one orifice plate separating the inner space into an upper space and a lower space in the longitudinal direction of the distributor;
The heat exchanger according to any one of claims 1 to 9, wherein the orifice plate is formed with an orifice hole that is a through hole and communicates an upper space and a lower space. The distributor is
11. The device according to any one of claims 1 to 10, wherein the distributor is installed in a state in which the central axis of the distributor in the longitudinal direction is oriented vertically, or in a state in which the central axis in the longitudinal direction of the distributor is inclined in a range having a vector component in the vertical direction. or the heat exchanger according to item 1. A heat exchanger according to any one of claims 1 to 11;
a blower that supplies air to the heat exchanger;
An air conditioner with

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