JP2020133923A - Air conditioner - Google Patents

Abstract

To provide an air conditioner in which refrigerant piping can be shortened than conventional ones.SOLUTION: A space S1 for an outdoor unit in which a compressor, an outdoor heat exchanger 120 and an outdoor fan 410 are disposed, and a space S2 for an indoor unit in which an indoor heat exchanger 300 and an indoor fan 420 are disposed, are adjacent to each other through a partitioning wall 510. A first opening 541 for an indoor heat exchange, communicated with an air-conditioned room is formed in a bottom surface 551 opposed to the partitioning wall 510, of a space definition portion 500B for the indoor unit. The indoor fan 420 is disposed in a position facing the first opening 541 for indoor heat exchange, and forms air flow from the air-conditioned room toward the space S2 for the indoor unit through the first opening 541 for indoor heat exchange. The indoor heat exchanger 300 surrounds the indoor fan 420 in a plane view in parallel with a Z-axis direction as a direction where the partitioning wall 510 and the bottom surface 551 are opposed to each other, consequently positions in the Z-axis direction, of the indoor heat exchanger 300 and the indoor fan 420 overlap each other.SELECTED DRAWING: Figure 5

Description

The present invention relates to an air conditioner.

As disclosed in Patent Document 1, there is known an air conditioner having a structure in which each element constituting the refrigeration cycle is housed in one casing. The inside of the casing is divided into an indoor unit room and an outdoor unit room by a partition wall.

In the indoor unit room, an indoor heat exchanger that exchanges heat with the air in the air-conditioned room that is the target of air conditioning and an indoor fan that forms an air flow that hits the indoor heat exchanger are arranged. In the outdoor unit room, a compressor that compresses the refrigerant, an outdoor heat exchanger that exchanges heat between the air outside the air-conditioned room, and an outdoor fan that forms an air flow that hits the outdoor heat exchanger are arranged. .. The compressor, indoor heat exchanger, and outdoor heat exchanger are connected by a refrigerant pipe that penetrates the partition wall.

Japanese Unexamined Patent Publication No. 11-325505

In the air conditioner according to Patent Document 1, each of the outdoor heat exchanger and the indoor heat exchanger faces the partition wall. Then, in the indoor unit room, an indoor fan is interposed between the indoor heat exchanger and the partition wall. Further, the indoor heat exchanger and the indoor fan are separated from each other in the direction in which the indoor heat exchanger and the partition wall face each other.

Therefore, the distance between the outdoor heat exchanger and the indoor heat exchanger is large. Therefore, a refrigerant pipe with a long path length is required. If the path length of the refrigerant pipe is long, there are problems such as a decrease in the coefficient of performance representing the air conditioning capacity per unit power consumption and an increase in the weight of the air conditioner. Therefore, it is desired to shorten the length of the refrigerant pipe.

An object of the present invention is to provide an air conditioner in which a refrigerant pipe can be made shorter than before.

In order to achieve the above object, the air conditioner according to the present invention
A compressor that compresses the refrigerant and
An outdoor heat exchanger and an indoor heat exchanger, one of which functions as a condenser for condensing the refrigerant and the other of which functions as an evaporator for evaporating the refrigerant.
An outdoor fan that forms an air flow that hits the outdoor heat exchanger,
An indoor fan that forms an air flow that hits the indoor heat exchanger,
An outdoor unit space defining portion that defines an outdoor unit space in which the compressor, the outdoor heat exchanger, and the outdoor fan are arranged, and an indoor unit in which the indoor heat exchanger and the indoor fan are arranged. It has an indoor unit space defining portion that defines the space for use, and the outdoor unit space and the indoor unit space are composed of the outdoor unit space defining portion and the indoor unit space defining portion. With the adjacent casings separated by the partition wall,
A refrigerant pipe that penetrates the partition wall and connects the compressor, the outdoor heat exchanger, and the indoor heat exchanger to form a flow path for the refrigerant.
With
The indoor unit space defining portion has a facing surface facing the partition wall, and the facing surface is formed with a first opening for indoor heat exchange leading to an air-conditioned room to be air-conditioned.
The indoor fan is arranged at a position facing the first indoor heat exchange opening, and is directed from one of the air-conditioned room and the indoor unit space to the other through the indoor heat exchange first opening. Form an air flow,
The indoor heat exchanger surrounds the indoor fan in a plan view parallel to the facing direction, which is the direction in which the partition wall and the facing surface face each other. The positions in the opposite direction with the fan overlap.

According to the above configuration, since the positions of the indoor heat exchanger and the indoor fan in the facing direction overlap, the indoor heat exchanger and the indoor fan are separated from each other in the facing direction, as compared with the conventional indoor heat exchanger. Is brought closer to the outdoor heat exchanger. As a result, the length of the refrigerant pipe can be shortened as compared with the conventional case.

Side view showing the mode of installation of the railroad vehicle air conditioner according to the first embodiment. Conceptual diagram showing the configuration of the railroad vehicle air conditioner according to the first embodiment. Perspective view showing the appearance of the upper part of the railroad vehicle air conditioner according to the first embodiment. A perspective view showing the appearance of the bottom of the railroad vehicle air conditioner according to the first embodiment. Partial sectional view showing the air flow inside the air conditioner for a railroad vehicle according to the first embodiment. Top view showing the air flow inside the air conditioner for railroad vehicles according to the first embodiment. A perspective view showing the indoor heat exchanger according to the first embodiment and its surroundings. Top view showing the outdoor heat exchanger according to the first embodiment and its surroundings. A perspective view showing an indoor heat exchanger and an outdoor heat exchanger according to the first embodiment. Partial sectional view of the railroad vehicle air conditioner according to the first embodiment as viewed in the negative direction of the Y axis. Partial sectional view of the railroad vehicle air conditioner according to the first embodiment as viewed in the positive direction of the Y axis. Partial sectional view of the railroad vehicle air conditioner according to the second embodiment as viewed in the negative direction of the Y axis. Partial rupture view showing the connection portion between the outdoor heat exchanger and the refrigerant pipe according to the third embodiment. Partial sectional view which shows the internal structure of the air conditioner which concerns on a comparative form

Hereinafter, the railroad vehicle air conditioner according to the first to third embodiments will be described with reference to the drawings. In the figure, the same or corresponding parts are designated by the same reference numerals.

[Embodiment 1]
As shown in FIG. 1, a plurality of railroad vehicle air conditioners 700 according to the present embodiment are installed on the roof 810 of the railroad vehicle 800. Each railroad vehicle air conditioner 700 air-conditions the guest room 820 as an air-conditioned room defined inside the railroad vehicle 800.

As shown in FIG. 2, each railroad vehicle air conditioner 700 includes a refrigeration cycle device 100 that constitutes a refrigeration cycle using a refrigerant.

The refrigeration cycle device 100 expands the compressor 110 that compresses the refrigerant, the outdoor heat exchanger 120 that functions as a condenser that condenses the refrigerant compressed by the compressor 110, and the refrigerant condensed by the outdoor heat exchanger 120. It includes an expander 130 for inflating, an indoor heat exchanger 300 which functions as an evaporator for evaporating the refrigerant expanded by the inflator 130, and a gas-liquid separator 140 for separating a liquid from the refrigerant which has passed through the indoor heat exchanger 300. ..

The refrigeration cycle device 100 also includes a refrigerant pipe 200 through which a refrigerant flows. The refrigerant pipe 200 constitutes a closed flow path for the refrigerant that connects the compressor 110, the outdoor heat exchanger 120, the expander 130, the indoor heat exchanger 300, and the gas-liquid separator 140 in this order.

Further, the railroad vehicle air conditioner 700 includes an outdoor fan 410 that forms an air flow that hits the outdoor heat exchanger 120, and an indoor fan 420 that forms an air flow that hits the indoor heat exchanger 300. The air flow formed by the outdoor fan 410 promotes heat exchange between the outside air of the railway vehicle 800 shown in FIG. 1 (hereinafter referred to as external air) and the outdoor heat exchanger 120. The air flow formed by the indoor fan 420 promotes heat exchange between the air in the cabin 820 (hereinafter referred to as internal air) shown in FIG. 1 and the indoor heat exchanger 300.

Further, the railroad vehicle air conditioner 700 includes a casing 500 that houses the refrigeration cycle device 100, the outdoor fan 410, and the indoor fan 420 described above. The casing 500 serves as an outdoor unit space defining housing 500A as an outdoor unit space defining portion defining the outdoor unit space S1 and an indoor unit space defining portion defining the indoor unit space S2. It has a space-defining casing 500B for an indoor unit.

A compressor 110, an outdoor heat exchanger 120, an expander 130, a gas-liquid separator 140, and an outdoor fan 410 are arranged in the outdoor unit space S1. An indoor heat exchanger 300 and an indoor fan 420 are arranged in the indoor unit space S2. The space S1 for the outdoor unit and the space S2 for the indoor unit are adjacent to each other with a partition wall 510 composed of the space defining housing 500A for the outdoor unit and the space defining housing 500B for the indoor unit.

As shown in FIG. 5, the space-defining housing 500B for the indoor unit is embedded in the roof 810 of the railway vehicle 800. Specifically, a recess is formed in the roof 810, and the space defining housing 500B for the indoor unit is fitted in the recess. Then, the space defining housing 500A for the outdoor unit is stacked vertically above the space defining housing 500B for the indoor unit.

The height of the upper surface of the space defining housing 500B for the indoor unit is the same as the height of the portion of the roof 810 other than the recess. The space-defining housing 500A for the outdoor unit projects upward from the roof 810.

The outdoor unit space defining housing 500A defines the outdoor unit space S1 independently of the indoor unit space defining housing 500B. Further, the space defining housing 500B for the indoor unit defines the space S2 for the indoor unit independently of the space defining housing 500A for the outdoor unit. The joint portion between the space defining housing 500A for the outdoor unit and the space defining housing 500B for the indoor unit constitutes the partition wall 510.

Specifically, the partition wall 510 is composed of a horizontal upper surface portion of the space defining housing 500B for the indoor unit and a horizontal bottom surface portion of the space defining housing 500A for the outdoor unit. The outdoor unit space S1 and the indoor unit space S2 are adjacent to each other in the vertical direction with a partition wall 510 in between.

The indoor unit space demarcation housing 500B has a heat insulating wall 520 having heat insulating properties at a position facing the indoor unit space S2. The heat insulating wall 520 also forms a part of the partition wall 510. The heat insulating wall 520 suppresses heat transfer from the outside to the inside of the space-defining housing 500B for indoor units, and also suppresses the condensation of moisture in the internal air on the inner surface of the space-defining housing 500B for indoor units. ..

For the following description, a right-handed XYZ Cartesian coordinate system having a Z-axis parallel to the vertical direction, a Y-axis parallel to the length direction of the railcar 800, and an X-axis parallel to the width direction of the railcar 800. Define. The direction vertically upward is the positive direction of the Z axis. An XYZ Cartesian coordinate system is attached to each figure.

As shown in FIG. 3, the casing 500 as a whole is formed in the shape of a rectangular parallelepiped having a height in the Z-axis direction, a width in the X-axis direction, and a depth in the Y-axis direction. Further, each of the outdoor unit space defining housing 500A and the indoor unit space defining housing 500B is a rectangular parallelepiped having a height in the Z-axis direction, a width in the X-axis direction, and a depth in the Y-axis direction. It is formed in the shape of.

An outdoor heat exchange first opening 531 that communicates the outdoor unit space S1 shown in FIG. 2 with the outside is formed on the upper surface of the outdoor unit space defining housing 500A. Further, on both of the pair of side surfaces orthogonal to the X axis of the outdoor unit space defining housing 500A, a second opening 532 for outdoor heat exchange is formed so as to communicate the outdoor unit space S1 shown in FIG. 2 with the outside. ing. In FIG. 3, only one outdoor heat exchange second opening 532 appears.

As shown in FIG. 5, the outdoor fan 410 sucks the external air into the outdoor unit space S1 through the outdoor heat exchange first opening 531 and exchanges heat with the outdoor heat exchanger 120 into a pair of outdoor air. The heat is discharged to the outside of the outdoor unit space S1 through the second heat exchange opening 532. The outdoor fan 410 is composed of an axial blower having a propeller-type impeller that rotates around the Z axis.

As shown in FIG. 4, on the bottom surface of the indoor unit space defining housing 500B, a first opening 541 for indoor heat exchange and a pair of second indoor heat exchange openings leading to the indoor unit space S2 shown in FIG. 2, respectively. 542 is formed. The indoor heat exchange second opening 542 is formed on both sides of the indoor heat exchange first opening 541 in the X-axis direction.

As shown in FIG. 5, each of the indoor heat exchange first opening 541 and the pair of indoor heat exchange second openings 542 communicate with the duct 830. The duct 830 leads to the guest room 820 shown in FIG. The indoor fan 420 sucks the internal air from the guest room 820 shown in FIG. 1 into the indoor unit space S2 through the indoor heat exchange first opening 541 and the duct 830, and exchanges heat with the indoor heat exchanger 300. Air is discharged to the cabin 820 shown in FIG. 1 through a pair of indoor heat exchange second openings 542 and a duct 830.

Hereinafter, in order to show the problem to be solved in the present embodiment, a comparative embodiment will be described prior to the detailed description of the railroad vehicle air conditioner 700.

As shown in FIG. 14, the air conditioner 900 according to the comparative embodiment has an indoor fan 912 between the indoor heat exchanger 911 and the partition wall 930 in the indoor unit space 910, similarly to the one disclosed in Patent Document 1. Has an intervening configuration. The indoor heat exchanger 911 and the indoor fan 912 are separated from each other in the direction in which the indoor heat exchanger 911 and the partition wall 930 face each other. Therefore, the distance between the indoor heat exchanger 911 and the outdoor heat exchanger 921 is large. Therefore, a refrigerant pipe 940 having a long path length is required.

Further, in the outdoor unit space 920, the outdoor fan 922 is interposed between the outdoor heat exchanger 921 and the partition wall 930. That is, the outdoor fan 922 keeps the outdoor heat exchanger 921 away from the indoor heat exchanger 911. This also leads to an increase in the path length of the refrigerant pipe 940.

Further, each of the indoor heat exchanger 911 and the outdoor heat exchanger 921 has a configuration in which a portion into which the refrigerant is introduced and a portion in which the refrigerant is discharged are arranged on the same end face. As a result, of the refrigerant pipe 940, the connection portion 941 that guides the refrigerant discharged from the outdoor heat exchanger 921 to the indoor heat exchanger 911 is bypassed in order to avoid contact with the compressor 923 and the gas-liquid separator 924. I have to let you. This also leads to an increase in the path length of the refrigerant pipe 940.

If the path length of the refrigerant pipe 940 is long, there are problems such as a decrease in the coefficient of performance representing the air conditioning capacity per unit power consumption and an increase in the weight of the air conditioner 900. Therefore, it is desired to shorten the length of the refrigerant pipe 940.

In particular, in the railroad vehicle 800, the passenger compartment 820 is released every time the railroad vehicle 800 arrives at the station, and passengers get on and off, so that the passenger compartment 820 is difficult to be air-conditioned. Therefore, a device for air-conditioning the guest room 820 is required to have a high coefficient of performance. Further, in order to suppress the energy required to propel the railway vehicle 800, the device for air-conditioning the passenger compartment 820 is required to be lightweight.

Further, the air conditioner 900 according to the comparative embodiment is assumed to be used in a mode in which the direction in which the indoor heat exchanger 911 and the partition wall 930 face each other coincides with the horizontal direction. In the use in which the indoor heat exchanger 911 and the partition wall 930 face each other in the vertical direction (hereinafter referred to as vertical use), the moisture in the air condensed by the indoor heat exchanger 911 (hereinafter referred to as condensed water). ) Drops into the air-conditioned room, which is the target of air conditioning, through the opening 913 facing the indoor heat exchanger 911.

As described above, in the comparative form, there is a problem that the path length of the refrigerant pipe 940 is long, and there is a problem that condensed water leaks from the indoor heat exchanger 911 in the vertical use. Hereinafter, the description of the present embodiment for solving the above-mentioned problems will be returned.

As shown in FIG. 5, in the present embodiment, unlike the comparative embodiment, the outdoor unit space S1 and the indoor unit space S2 of the indoor heat exchanger 300 and the indoor fan 420 are adjacent to each other, that is, Z. Axial positions overlap. As a result, the indoor heat exchanger 300 is brought closer to the outdoor heat exchanger 120. Hereinafter, the configuration in the indoor unit space S2 will be specifically described.

As described above, the bottom surface 551 of the space demarcation section 500B for the indoor unit as the facing surface facing the partition wall 510 has the first opening 541 for indoor heat exchange and the indoor heat exchange leading to the guest room 820 shown in FIG. 1, respectively. A second opening 542 for use is formed. The facing direction, which is the direction in which the partition wall 510 and the bottom surface 551 face each other, coincides with the Z-axis direction. The indoor fan 420 is arranged at a position facing the first opening 541 for indoor heat exchange.

As shown in FIG. 6, the indoor heat exchanger 300 surrounds the indoor fan 420 in a plan view parallel to the Z-axis direction. The indoor heat exchange second opening 542 is arranged on the bottom surface 551 in a region other than between the indoor heat exchanger 300 and the indoor fan 420 in a plan view parallel to the Z-axis direction. Specifically, the second opening 542 for indoor heat exchange is formed on both sides of the indoor heat exchanger 300 in the X-axis direction.

The indoor heat exchanger 300 has a first main body portion 310 and a second main body portion 320 facing each other in the X-axis direction with the indoor fan 420 interposed therebetween. The first main body 310 is arranged between the second opening 542 for indoor heat exchange and the indoor fan 420. The second main body 320 is arranged between the other second opening 542 for indoor heat exchange and the indoor fan 420.

Each of the first main body 310 and the second main body 320 is a plan view parallel to the Z-axis direction, and the indoor fan 420 is also in a direction orthogonal to the direction in which the first main body 310 and the second main body 320 face each other. Face to face. That is, each of the first main body 310 and the second main body 320 has a shape facing the indoor fan 420 not only in the X-axis direction but also in the Y-axis direction, specifically, in a plan view parallel to the Z-axis direction. It is formed in a character shape.

As described above, the indoor heat exchanger 300 surrounds the indoor fan 420 in a plan view parallel to the Z axis. As a result, as shown in FIG. 5, the positions of the indoor heat exchanger 300 and the indoor fan 420 are overlapped in the Z-axis direction. As a result, the indoor heat exchanger 300 is brought closer to the outdoor heat exchanger 120 than the configuration of the comparative form shown in FIG. Therefore, the length of the refrigerant pipe 200 shown in FIG. 2 can be shortened.

As shown in FIG. 6, a filter 600 for capturing dust contained in the internal air is arranged between the indoor fan 420 and the indoor heat exchanger 300. The filter 600 includes a first filter 610 interposed between the first main body 310 and the indoor fan 420, and a second filter 620 interposed between the second main body 320 and the indoor fan 420.

Each of the first filter 610 and the second filter 620 has a shape facing the indoor fan 420 not only in the X-axis direction but also in the Y-axis direction, specifically, in a plan view parallel to the Z-axis direction, and has a C shape. It is formed.

The indoor fan 420 blows out the internal air sucked up from the guest room 820 shown in FIG. 1 radially into the indoor unit space S2 in a plan view parallel to the Z-axis direction. The indoor fan 420 is composed of a turbo-type centrifugal blower having an impeller that rotates around the Z axis.

Of the internal air blown out from the indoor fan 420, the air that has passed through the first filter 610 and the first main body 310 in this order is mainly passed through one of the indoor heat exchange second openings 542 to the guest room 820 shown in FIG. Be returned.

On the other hand, of the internal air blown out from the indoor fan 420, the internal air that has passed through the second filter 620 and the second main body 320 in this order is shown in FIG. 1 mainly through the other indoor heat exchange second opening 542. Returned to guest room 820.

As shown in FIG. 5, the filter 600 is in contact with the partition wall 510 and the bottom surface 551. Further, the indoor heat exchanger 300 is in contact with the partition wall 510. As a result, it is possible to reduce the proportion of the internal air flowing from the indoor heat exchange first opening 541 to the indoor heat exchange second opening 542 that does not pass through the filter 600 and the indoor heat exchanger 300.

Further, a drain pan 560 for receiving the condensed water condensed by the indoor heat exchanger 300 is interposed between the indoor heat exchanger 300 and the bottom surface 551. The condensed water collected in the drain pan 560 is discharged to the outside of the railway vehicle 800 through a discharge structure (not shown).

Therefore, the railroad vehicle air conditioner 700 according to the present embodiment has a mode in which the facing direction in which the partition wall 510 and the bottom surface 550 face each other coincides with the vertical direction, unlike the configuration of the comparative mode shown in FIG. Despite being used in the above, condensed water does not leak into the first opening 541 for indoor heat exchange and the second opening 542 for indoor heat exchange.

Next, the configuration in the outdoor unit space S1 will be specifically described. In the present embodiment, the outdoor heat exchanger 120 is attached to the top surface 552 of the outdoor unit space defining portion 500A, which is a surface facing the partition wall 510. Specifically, the outdoor heat exchanger 120 is suspended from the top surface 552 by a hanging tool 570.

As a result, the outdoor heat exchanger 120 is arranged at a position closer to the partition wall 510 than the outdoor fan 410 in the Z-axis direction. This also contributes to shortening the distance between the outdoor heat exchanger 120 and the indoor heat exchanger 300 in the Z-axis direction and shortening the length of the refrigerant pipe 200 shown in FIG.

The outdoor heat exchanger 120 is formed in a flat plate shape and faces the partition wall 510. The periphery of the outdoor heat exchanger 120 extends parallel to the outdoor heat exchanger 120 and is covered with an air passage defining plate 553 facing the partition wall 510.

The external air taken in from the first opening 531 for outdoor heat exchange by the outdoor fan 410 and passed through the outdoor heat exchanger 120 is between the outdoor heat exchanger 120 and the air passage defining plate 553 and the partition wall 510. It is discharged from the outdoor heat exchange second opening 532 through the gap. The air passage defining plate 553 suppresses a shortcut in which the outside air is discharged from the outdoor heat exchange second opening 532 without passing through the outdoor heat exchanger 120.

Next, the detailed configuration of the indoor heat exchanger 300 and the flow of the refrigerant in the indoor heat exchanger 300 will be described.

As shown in FIG. 7, the indoor heat exchanger 300 has an indoor heat exchange refrigerant introduction unit 300A into which the refrigerant is introduced and an indoor heat exchange refrigerant discharge unit 300B into which the refrigerant is discharged. The indoor heat exchange refrigerant introduction unit 300A and the indoor heat exchange refrigerant discharge unit 300B face each other with the indoor fan 420 in a plan view parallel to the Z-axis direction.

The indoor heat exchange refrigerant introduction unit 300A and the indoor heat exchange refrigerant discharge unit 300B intersect the X-axis direction, which is the direction in which the pair of indoor heat exchange second openings 542 shown in FIGS. 5 and 6 are arranged. They face each other in the direction, specifically the Y-axis direction.

The indoor heat exchange refrigerant introduction unit 300A covers the inside of the refrigerant introduction first header pipe 330 and the second main body 320, which are connected to the branch pipe group 311 that covers the inside of the first main body 310. It has a second header pipe 340 for introducing a refrigerant connected to the branch pipe group 321.

Each of the refrigerant introduction first header pipe 330 and the refrigerant introduction second header pipe 340 extends in the Z-axis direction. The first header pipe 330 for introducing the refrigerant and the second header pipe 340 for introducing the refrigerant are arranged at intervals in the Z-axis direction.

The indoor heat exchange refrigerant discharge unit 300B has a refrigerant discharge header pipe 350 connected to the branch pipe groups 311 and 321. The refrigerant discharge header pipe 350 extends in the Z-axis direction.

The refrigerant introduced into the first header pipe 330 for introducing the refrigerant flows through the inside of the first main body 310 toward the header pipe 350 for discharging the refrigerant along the branch pipe group 311. The refrigerant introduced into the second header pipe 340 for introducing the refrigerant flows inside the second main body 320 along the branch pipe group 321 toward the header pipe 350 for discharging the refrigerant. The branch pipe groups 311 and 321 merge at the refrigerant discharge header pipe 350, and the refrigerant is discharged from the refrigerant discharge header pipe 350.

Next, the detailed configuration of the outdoor heat exchanger 120 and the flow of the refrigerant in the outdoor heat exchanger 120 will be described.

As shown in FIG. 8, the outdoor heat exchanger 120 has an outdoor heat exchange refrigerant introduction unit 120A into which the refrigerant is introduced and an outdoor heat exchange refrigerant discharge unit 120B into which the refrigerant is discharged. The outdoor heat exchange refrigerant introduction unit 120A is arranged at one end of the outdoor heat exchanger 120 in the Y-axis direction, and the outdoor heat exchange refrigerant discharge unit 120B is located at the other end of the outdoor heat exchanger 120 in the Y-axis direction. Have been placed.

That is, in the outdoor heat exchanger 120, the direction from one of the outdoor heat exchange refrigerant introduction unit 120A and the outdoor heat exchange refrigerant discharge unit 120B toward the other is the indoor heat exchange refrigerant introduction in the indoor heat exchanger 300 shown in FIG. It coincides with the Y-axis direction, which is the direction in which the unit 300A and the indoor heat exchange refrigerant discharge unit 300B face each other.

The outdoor heat exchange refrigerant introduction unit 120A has a refrigerant introduction header pipe 121 connected to a branch pipe group 123 covering the inside of the outdoor heat exchanger 120. The outdoor heat exchange refrigerant discharge unit 120B has a refrigerant discharge header pipe 122 connected to the branch pipe group 123. Since the branch pipe group 123 joins inside the outdoor heat exchanger 120, the number of branch pipes constituting the branch pipe group 123 connected to the refrigerant discharge header pipe 122 is the refrigerant introduction header pipe 121. It is less than the number of branch pipes connected to.

Each of the refrigerant introduction header pipe 121 and the refrigerant discharge header pipe 122 extends in a direction parallel to the horizontal XY plane, specifically, in the X-axis direction. The refrigerant introduced into the refrigerant introduction header pipe 121 travels in the Y-axis minus direction inside the outdoor heat exchanger 120 along the branch pipe group 123, and joins the refrigerant discharge header pipe 122. Refrigerant is discharged from the refrigerant discharge header pipe 122.

Next, the configuration of the flow path of the refrigerant from the indoor heat exchanger 300 to the outdoor heat exchanger 120 will be specifically described.

As shown in FIG. 9, the flow path of the refrigerant between the indoor heat exchange refrigerant discharge unit 300B of the indoor heat exchanger 300 and the outdoor heat exchange refrigerant introduction unit 120A of the outdoor heat exchanger 120 is shown in FIG. The gas-liquid separator 140 and the compressor 110 also shown in the above are arranged.

The gas-liquid separator 140 and the compressor 110 are arranged in the outdoor unit space S1 shown in FIG. The compressor 110 includes a motor that constitutes a compression mechanism that compresses the refrigerant. The rotation shaft of the motor of the compressor 110 is arranged parallel to the in-plane direction in which the outdoor heat exchanger 120 extends. Specifically, the rotation shaft of the motor of the compressor 110 is arranged in the X-axis direction in parallel with the refrigerant introduction header pipe 121.

The compressor 110 is arranged on the side of the outdoor heat exchanger 120 in the positive direction of the Y axis. The gas-liquid separator 140 is arranged beside the compressor 110 in the X-axis direction. The positions of the compressor 110, the gas-liquid separator 140, and the outdoor heat exchanger 120 in the Z-axis direction overlap.

The indoor heat exchange refrigerant discharge unit 300B, the gas-liquid separator 140, the compressor 110, and the outdoor heat exchange refrigerant introduction unit 120A are connected by the refrigerant pipe 200 also shown in FIG. The refrigerant discharged from the indoor heat exchange refrigerant discharge unit 300B is introduced into the outdoor heat exchange refrigerant introduction unit 120A via the gas-liquid separator 140 and the compressor 110 in this order.

The refrigerant pipe 200 has a flow path from the indoor heat exchange refrigerant discharge unit 300B to the gas-liquid separator 140 among the refrigerant flow paths from the indoor heat exchange refrigerant discharge unit 300B to the outdoor heat exchange refrigerant introduction unit 120A. It has a first penetrating portion 210 that constitutes it.

As shown in FIG. 10, the first penetrating portion 210 extends continuously in the Z-axis direction with the refrigerant discharge header pipe 350. The first penetrating portion 210 penetrates the partition wall 510 in the Z-axis direction and is connected to the gas-liquid separator 140. The portion of the first penetrating portion 210 penetrating the partition wall 510 is airtightly sealed with a sealing material.

The outdoor heat exchanger 120 is arranged directly above the indoor heat exchanger 300. Specifically, the region where the outdoor heat exchanger 120 is projected onto the bottom surface 551 parallel to the Z-axis direction and the region where the indoor heat exchanger 300 is projected onto the bottom surface 551 parallel to the Z-axis direction have an overlap. ..

Further, as described above, the direction in which the indoor heat exchange refrigerant introduction unit 300A shown in FIG. 7 and the indoor heat exchange refrigerant discharge unit 300B face each other is also the direction in which the outdoor heat exchange refrigerant introduction unit 120A shown in FIG. 8 faces. And the direction from one side of the outdoor heat exchange refrigerant discharge unit 120B toward the other are also Y-axis directions and coincide with each other.

Therefore, as shown in FIG. 10, by raising the first penetrating portion 210 from the refrigerant discharge header pipe 350 toward the outdoor unit space S1 in the Z-axis plus direction, the refrigerant is discharged from the refrigerant discharge header pipe 350. A rational routing of the refrigerant pipe 200 is realized without being unnecessarily lengthened over the introduction header pipe 121. This also contributes to shortening the length of the refrigerant pipe 200.

Next, the configuration of the flow path of the refrigerant from the outdoor heat exchanger 120 to the indoor heat exchanger 300 will be specifically described.

As shown in FIG. 7, the expander 130 also shown in FIG. 2 is arranged in the flow path of the refrigerant between the outdoor heat exchange refrigerant discharge unit 120B and the indoor heat exchange refrigerant introduction unit 300A. .. The refrigerant discharged from the outdoor heat exchange refrigerant discharge unit 120B is introduced into the indoor heat exchange refrigerant introduction unit 300A via the expander 130.

The expander 130 is arranged beside the refrigerant discharge header pipe 122 constituting the outdoor heat exchange refrigerant discharge unit 120B in the negative direction of the Y-axis. The positions of the expander 130 and the refrigerant discharge header pipe 122 in the Z-axis direction overlap.

The inflator 130 is composed of a capillary tube. The capillary pipe has a meandering shape in the XY plane, and extends in the X-axis direction in parallel with the refrigerant discharge header pipe 122. The end of the capillary pipe constituting the inflator 130 in the negative direction of the X-axis is connected to the refrigerant discharge header pipe 122.

The refrigerant pipe 200 has a second through portion 220 that constitutes a flow path for the refrigerant from the expander 130 to the indoor heat exchange refrigerant introduction portion 300A. The second penetrating portion 220 includes the end of the capillary pipe constituting the expander 130 in the plus direction of the X axis, the first header pipe 330 for introducing the refrigerant and the second refrigerant introducing the refrigerant, which constitute the refrigerant introducing portion 300A for indoor heat exchange. It is connected to the end of the header tube 340 in the plus direction of the Z axis.

As shown in FIG. 11, the second penetrating portion 220 extends from the expander 130 toward the refrigerant introduction first header pipe 330 and the refrigerant introduction second header pipe 340 in the Z-axis direction. The second penetrating portion 220 penetrates the partition wall 510 in the Z-axis direction. The portion where the second penetrating portion 220 penetrates the partition wall 510 is hermetically sealed with a sealing material.

As described above, the outdoor heat exchanger 120 is arranged directly above the indoor heat exchanger 300. The direction in which the indoor heat exchange refrigerant introduction unit 300A and the indoor heat exchange refrigerant discharge unit 300B shown in FIG. 7 face each other is also the direction in which the outdoor heat exchange refrigerant introduction unit 120A and the outdoor heat exchange refrigerant shown in FIG. 8 face each other. The directions from one of the discharge units 120B to the other are also Y-axis directions and coincide with each other.

Therefore, as shown in FIG. 11, the second through portion 220 is hung from the expander 130 toward the indoor unit space S2 in the negative direction of the Z axis, so that the first header pipe for introducing the refrigerant from the expander 130 is inserted. A rational routing of the refrigerant pipe 200 without being unnecessarily lengthened is realized over the 330 and the second header pipe 340 for introducing the refrigerant. This also contributes to shortening the length of the refrigerant pipe 200.

Further, as shown in FIG. 8, in a plan view parallel to the Z axis, the first penetrating portion 210 and the second penetrating portion 220 are separated from each other in the Y-axis direction with the outdoor heat exchanger 120 interposed therebetween. In a plan view parallel to the Z-axis direction, the first penetration portion 210, the compressor 110, and the gas-liquid separator 140 are arranged beside the Y-axis plus direction of the outdoor heat exchanger 120, and the outdoor heat exchanger 140 is arranged. A second penetrating portion 220 is arranged beside the 120 in the minus direction of the Y axis.

Therefore, unlike the configuration according to the comparative form shown in FIG. 14, the second penetrating portion 220 does not need to bypass the compressor 110 and the gas-liquid separator 140. Therefore, as shown in FIG. 11, the second penetration portion 220 is formed in a straight tube that connects the expander 130, the first header pipe 330 for introducing the refrigerant, and the second header pipe 340 for introducing the refrigerant in the shortest distance. can do. This also contributes to shortening the length of the refrigerant pipe 200 shown in FIG.

[Embodiment 2]
In the first embodiment, as shown in FIG. 10, the compressor 110 is arranged in a state of being tilted in a direction in which the rotation axis of the compressor 110 penetrates a vertical virtual plane (hereinafter, referred to as sideways). .. The compressor 110 does not necessarily have to be tilted sideways. Hereinafter, a specific description will be given.

As shown in FIG. 12, in the present embodiment, the compressor 110 is arranged in a state in which the rotation axis of the compressor 110 is erected in a direction parallel to the Z axis (hereinafter, referred to as a vertical direction). The compressor 110 is arranged so as to penetrate the partition wall 510 and straddle the outdoor unit space S1 and the indoor unit space S2.

The portion of the partition wall 510 through which the compressor 110 penetrates is hermetically sealed with a sealing material. Further, the outer surface of the portion of the compressor 110 that has entered the indoor unit space S2 is covered with a heat insulating wall 520.

According to the present embodiment, since the compressor 110 also enters the indoor unit space S2, the height of the outdoor unit space defining housing 500A in the Z-axis direction is reduced as compared with the configuration of the first embodiment. Can be done. Further, since the compressor 110 is arranged vertically in the present embodiment, the contact area between the lubricating oil and the refrigerant is smaller inside the compressor 110 than in the configuration of the first embodiment in which the compressor 110 is arranged horizontally. It can be suppressed, and the refrigerant is less likely to dissolve in the lubricating oil and the compressor 110 is less likely to seize.

[Embodiment 3]
In the first embodiment, the components of the refrigeration cycle device 100 and the refrigerant pipe 200 may be connected by a joint member, but from the viewpoint of reducing the weight by reducing the joint member, they are connected by burring and brazing. Is preferable. A specific example will be described below.

As shown in FIG. 13, in the present embodiment, the refrigerant introduction header pipe 121 has a tubular protrusion 121a formed by burring. The tubular protrusion 121a is formed in the middle portion of the refrigerant introduction header pipe 121 in the length direction.

A connecting portion 230 of the refrigerant pipe 200 that connects the compressor 110 shown in FIG. 9 and the refrigerant introduction header pipe 121 is inserted into the tubular protruding portion 121a. As a result, the connection portion 230 and the refrigerant introduction header pipe 121 are communicated with each other.

The tip of the tubular protrusion 121a and the connecting portion 230 are welded by the alloy AL to be tried. The tip of the tubular protrusion 121a is formed in a wavy or zigzag shape. As a result, the tubular protrusion 121a and the connection 230 are fixed by the alloy AL as compared with the case where the tip of the tubular protrusion 121a is formed in a flat shape orthogonal to the length direction of the connection portion 230. The area of the area is increased. Therefore, the strength of the joint between the tubular protrusion 121a and the connection portion 230 is improved.

Further, a stepped portion 121b is formed inside the tubular protruding portion 121a so that the tip of the connecting portion 230 hits. The presence of the stepped portion 121b limits the amount of insertion of the connecting portion 230 into the tubular protruding portion 121a to a specified amount. Therefore, the work of joining the tubular protrusion 121a and the connecting portion 230 can be facilitated.

Note that FIG. 13 illustrates a connection portion between the refrigerant introduction header pipe 121 and the refrigerant pipe 200. Refrigerant introduction first header pipe 330, refrigerant introduction second header pipe 340, refrigerant as a header pipe connected to the branch pipe group 311, 312, or 123 provided in the indoor heat exchanger 300 or the outdoor heat exchanger 120. Similarly, the connection portion between the discharge header pipe 350 or the refrigerant discharge header pipe 122 and the refrigerant pipe 200 can be connected by burring and brazing.

The embodiment of the present invention has been described above. The present invention is not limited to this, and the modifications described below are also possible.

FIG. 5 illustrates the airflow from the indoor heat exchange first opening 541 to the indoor heat exchange second opening 542, but the airflow from the indoor heat exchange second opening 542 to the indoor heat exchange first opening 541 May be formed. That is, the indoor fan 420 sucks the air of the guest room 820 into the indoor unit space S2 through one of the indoor heat exchange first opening 541 and the indoor heat exchange second opening 542, and the indoor heat exchanger 300 The air that has exchanged heat with and may be discharged to the guest room 820 through the other opening.

FIG. 5 illustrates the airflow from the outdoor heat exchange first opening 531 to the outdoor heat exchange second opening 532, but the airflow from the outdoor heat exchange second opening 532 to the outdoor heat exchange first opening 531. May be formed. That is, the outdoor fan 410 sucks the outside air into the outdoor unit space S1 through one of the outdoor heat exchange first opening 531 and the outdoor heat exchange second opening 532, and connects with the outdoor heat exchanger 120. The external air that has exchanged heat between them may be discharged to the outside of the outdoor unit space S1 through the other opening.

FIG. 5 illustrates a configuration in which the indoor unit space S2 does not communicate with the outside of the railroad vehicle 800, but the indoor unit space demarcation housing 500B includes the indoor unit space S2 from the outside of the railcar 800. An opening for introducing external air may be formed to take in external air. The external air taken in from the external air introduction opening may be mixed with the internal air and sent to the guest room 820 through the indoor heat exchange second opening 542.

FIG. 2 shows a configuration in which the outdoor heat exchanger 120 functions exclusively as a condenser and the indoor heat exchanger 300 functions as an evaporator. However, in the refrigeration cycle device 100, the outdoor heat exchanger 120 functions as an evaporator. A four-way valve or other valve that functions and can be switched to a state in which the indoor heat exchanger 300 functions as a condenser may be provided.

In the present specification, a railroad vehicle is not limited to a train, but includes a Shinkansen, a monorail, and other vehicles traveling along a track. Further, the vehicle in which the casing 500 is installed is not limited to a railway vehicle, but may be a bus or other automobile. Further, the place where the casing 500 is installed is not limited to the vehicle. The casing 500 may be installed on the roof of the building.

100 ... Refrigeration cycle device, 110 ... Compressor, 120 ... Outdoor heat exchanger (condenser), 120A ... Outdoor heat exchange refrigerant introduction unit, 120B ... Outdoor heat exchange refrigerant discharge unit, 123 ... Branch pipe group, 121 ... Refrigerant introduction header pipe, 121a ... Tubular protrusion, 121b ... Stepped portion, 122 ... Refrigerator discharge header pipe, 130 ... Expander, 140 ... Gas-liquid separator, 200 ... Refrigerator pipe, 210 ... First penetration, 220 ... 2nd penetration part, 230 ... Connection part, 300 ... Indoor heat exchanger (evaporator), 300A ... Indoor heat exchange refrigerant introduction part, 300B ... Indoor heat exchange refrigerant discharge part, 310 ... 1st main body part, 311 ... Branch pipe group, 320 ... Second main body, 321 ... Branch pipe group, 330 ... First header pipe for introducing refrigerant, 340 ... Second header pipe for introducing refrigerant, 350 ... Header pipe for discharging refrigerant, 410 ... Outdoor fan , 420 ... Indoor fan, 500 ... Casing, 500A ... Outdoor unit space demarcation housing (outdoor unit space demarcation part), 500B ... Indoor unit space demarcation housing (indoor unit space demarcation part) 510 ... Partition wall 520 ... Insulation wall, 513 ... Outdoor heat exchange first opening, 532 ... Outdoor heat exchange second opening, 541 ... Indoor heat exchange first opening, 542 ... Indoor heat exchange second opening, 551 ... Bottom surface ( Opposing surface), 552 ... Top surface, 535 ... Air passage defining plate, 560 ... Drain pan, 570 ... Hanging tool, 600 ... Filter, 610 ... First filter, 620 ... Second filter, 700 ... Rail vehicle air conditioner (air conditioning) Equipment), 800 ... Railway vehicle, 810 ... Roof, 820 ... Guest room (air-conditioned room), 830 ... Duct, 900 ... Air conditioner, 910 ... Indoor unit space, 911 ... Indoor heat exchanger, 912 ... Indoor fan, 913 ... opening, 920 ... space for outdoor unit, 921 ... outdoor heat exchanger, 922 ... outdoor fan, 923 ... compressor, 924 ... gas-liquid separator, 930 ... partition wall, 940 ... refrigerant pipe, 941 ... connection, AL ... Alloy, S1 ... Outdoor unit space, S2 ... Indoor unit space.

Claims (5)

A compressor that compresses the refrigerant and
An outdoor heat exchanger and an indoor heat exchanger, one of which functions as a condenser for condensing the refrigerant and the other of which functions as an evaporator for evaporating the refrigerant.
An outdoor fan that forms an air flow that hits the outdoor heat exchanger,
An indoor fan that forms an air flow that hits the indoor heat exchanger,
An outdoor unit space defining portion that defines an outdoor unit space in which the compressor, the outdoor heat exchanger, and the outdoor fan are arranged, and an indoor unit in which the indoor heat exchanger and the indoor fan are arranged. It has an indoor unit space defining portion that defines the space for use, and the outdoor unit space and the indoor unit space are composed of the outdoor unit space defining portion and the indoor unit space defining portion. With the adjacent casings separated by the partition wall,
A refrigerant pipe that penetrates the partition wall and connects the compressor, the outdoor heat exchanger, and the indoor heat exchanger to form a flow path for the refrigerant.
With
The indoor unit space defining portion has a facing surface facing the partition wall, and the facing surface is formed with a first opening for indoor heat exchange leading to an air-conditioned room to be air-conditioned.
The indoor fan is arranged at a position facing the first indoor heat exchange opening, and is directed from one of the air-conditioned room and the indoor unit space to the other through the indoor heat exchange first opening. Form an air flow,
The indoor heat exchanger surrounds the indoor fan in a plan view parallel to the facing direction, which is the direction in which the partition wall and the facing surface face each other. The positions of the fans in the opposite direction overlap with each other.
Air conditioner. The region in which the outdoor heat exchanger is projected onto the facing surface in parallel with the facing direction and the region in which the indoor heat exchanger is projected on the facing surface in parallel with the facing direction have an overlap.
The indoor heat exchanger has an indoor heat exchange refrigerant introduction unit into which the refrigerant is introduced and an indoor heat exchange refrigerant discharge unit into which the refrigerant is discharged.
The indoor heat exchange refrigerant introduction section and the indoor heat exchange refrigerant discharge section face each other with the indoor fan in between in a plan view parallel to the facing direction.
The outdoor heat exchanger has an outdoor heat exchange refrigerant introduction unit into which the refrigerant is introduced and an outdoor heat exchange refrigerant discharge unit into which the refrigerant is discharged.
The outdoor heat exchange refrigerant introduction section is arranged at one end of the outdoor heat exchanger in the direction in which the indoor heat exchange refrigerant introduction section and the indoor heat exchange refrigerant discharge section face each other. The outdoor heat exchange refrigerant discharge portion is arranged at the other end.
The air conditioner according to claim 1. The refrigerant pipe
A first penetrating portion that penetrates the partition wall in the opposite direction and forms a part of the flow path from the indoor heat exchange refrigerant discharge portion to the outdoor heat exchange refrigerant introduction portion.
A second penetrating portion that penetrates the partition wall in the opposite direction and forms a part of the flow path from the outdoor heat exchange refrigerant discharge portion to the indoor heat exchange refrigerant introduction portion.
The air conditioner according to claim 2. The outdoor heat exchanger is arranged at a position closer to the partition wall than the outdoor fan in the facing direction.
The air conditioner according to any one of claims 1 to 3. The casing is fixed to the roof of the vehicle
The indoor heat exchanger exchanges heat with the air in the guest room as the air-conditioned room, which is defined inside the vehicle.
The air conditioner according to any one of claims 1 to 4.