JP2021169876A - Refrigeration cycle device - Google Patents

Abstract

To provide a small refrigeration cycle device.SOLUTION: A refrigeration cycle device includes: a compressor 21 compressing a refrigerant; a decompression part 23 decompressing the refrigerant; heat exchangers 22, 24 exchanging heat between the refrigerant and ambient air; and refrigerant piping 70 providing an annular refrigerant flow passage by connecting the compressor, the decompression part and the heat exchanger. The refrigerant piping includes: compressor side piping 71 extending continuously from the compressor; heat exchanger side piping 72 extending continuously from the heat exchanger; and vibration isolating piping 80 provided between the compressor side piping and the heat exchanger side piping and reducing vibration transmitted from the compressor to the heat exchanger. The vibration isolating piping is piping configured by using a softer material than that of the compressor side piping. Length from an axial end part to a central part of the vibration isolating piping is shorter than an outer dimension of the vibration isolating piping. Due to this configuration, the small refrigeration cycle device can be provided.SELECTED DRAWING: Figure 3

Description

The disclosure herein relates to a refrigeration cycle device.

Patent Document 1 discloses an air conditioner hose for a vehicle having excellent vibration absorption performance. The air conditioner hose for a vehicle connects a compressor, a condenser, and an evaporator, and plays a role of transporting a refrigerant. The air conditioner hose for a vehicle plays a role of suppressing the transmission of compressor vibration to a condenser or an evaporator. The vehicle air conditioner hose includes an inner rubber layer, an outer rubber layer, and a reinforcing thread layer. The contents of the prior art document are incorporated by reference as an explanation of the technical elements in this specification.

Japanese Unexamined Patent Publication No. 2013-130283

In the configuration of the prior art document, an air conditioner hose having high withstand voltage strength is used. Therefore, the rigidity of the air conditioner hose is high, and it is necessary to secure a long length of the air conditioner hose in order to secure good vibration absorption performance. Therefore, the physique of the entire refrigeration cycle device including the air conditioner hose portion tends to be large. Further improvements are required in the refrigeration cycle apparatus in the above-mentioned viewpoint or in other viewpoints not mentioned.

One object disclosed is to provide a compact refrigeration cycle device.

The refrigeration cycle apparatus disclosed here includes a compressor (21) that compresses the refrigerant, a decompression unit (23) that depressurizes the refrigerant, and heat exchangers (22, 24) that exchange heat between the refrigerant and the surrounding air. And a compressor pipe (70) that connects the compressor, the decompression unit, and the heat exchanger to provide an annular refrigerant flow path, and the compressor pipe is on the compressor side that extends continuously from the compressor. It is provided between the pipe (71), the heat exchanger side pipe (72) continuously extending from the heat exchanger, and the compressor side pipe and the heat exchanger side pipe, and is provided from the compressor to the heat exchanger. It is equipped with a vibration-proof pipe (80) that reduces transmitted vibration, and the vibration-proof pipe is a pipe constructed using a material softer than the compressor-side pipe, and is the axial end of the vibration-proof pipe. The length from the center to the center is shorter than the outer diameter of the anti-vibration pipe.

According to the disclosed refrigeration cycle apparatus, the anti-vibration pipe is a pipe made of a softer material than the compressor-side pipe, and the length from the axial end to the center of the anti-vibration pipe is prevented. It is shorter than the outer diameter of the vibration pipe. Therefore, the amount of deformation in the central portion, which is easily deformed by the refrigerant flowing through the anti-vibration pipe, can be reduced. Therefore, by maintaining the shape of the anti-vibration pipe in a stable manner, it is easy to exert an appropriate anti-vibration function. Therefore, a small refrigeration cycle device can be provided.

The disclosed aspects herein employ different technical means to achieve their respective objectives. The claims and the reference numerals in parentheses described in this section exemplify the correspondence with the parts of the embodiments described later, and are not intended to limit the technical scope. The objectives, features, and effects disclosed herein will be made clearer by reference to the subsequent detailed description and accompanying drawings.

It is a perspective view which shows the appearance of an air conditioner. It is a perspective view which shows the internal structure of an air conditioner. It is a top view which shows the internal structure of an air conditioner. FIG. 3 is a cross-sectional view showing a cross section taken along line IV-IV of FIG. It is sectional drawing which shows the cross section in the VV line of FIG. It is sectional drawing which shows the connection part between the refrigerant pipes. It is sectional drawing which shows the peripheral structure of the anti-vibration pipe. It is a top view which shows the internal structure of the air conditioner in 2nd Embodiment. It is sectional drawing which shows the peripheral structure of the anti-vibration pipe in 2nd Embodiment.

A plurality of embodiments will be described with reference to the drawings. In a plurality of embodiments, functionally and / or structurally corresponding parts and / or related parts may be designated with the same reference code or reference codes having a hundreds or more different digits. For the corresponding and / or associated part, the description of other embodiments can be referred to.

1st Embodiment As shown in FIGS. 1 and 2, the air conditioner 1 includes a housing 10, a refrigeration cycle device 20, and a blower device 30. The air conditioner 1 is used as a seat air conditioner for enhancing the comfort of a occupant sitting on a seat by using a seat arranged in the vehicle interior of the vehicle as an air conditioning target space. The air conditioner 1 is arranged in a small space between the seat surface of the seat and the floor surface of the passenger compartment. The air conditioner 1 supplies air conditioning air such as cold air and hot air through a duct arranged on the seat. However, the device to which the refrigeration cycle device 20 can be applied is not limited to the seat air conditioner. For example, the refrigeration cycle device 20 may be applied to an air conditioner that blows air conditioning air from an air outlet provided on a dashboard or the like, with the entire interior of the vehicle as an air conditioning target space.

The housing 10 is formed in a rectangular parallelepiped shape that can be arranged between the seat surface portion of the seat and the floor surface of the passenger compartment. The housing 10 includes an upper cover 11 and a main body case 15. However, the shape of the housing 10 is not limited to the rectangular parallelepiped shape.

The upper cover 11 constitutes the upper surface of the housing 10. The upper cover 11 is attached so as to close the opening of the box-shaped main body case 15 having an open upper part. The upper cover 11 is formed with a hot air vent 12 and a cold air vent 13. The hot air vent 12 is formed on the right side portion of the upper cover 11. The hot air vent 12 is a vent for sucking the air outside the housing 10 into the inside of the housing 10 as the blower device 30 operates. The cold air vent 13 is formed on the left side portion of the upper cover 11. The cold air vent 13 is a vent for sucking the air outside the housing 10 into the inside of the housing 10 as the blower device 30 operates.

The upper cover 11 is formed with a supply port 14s and an exhaust port 14e. The supply port 14s and the exhaust port 14e are formed in the central portion of the upper cover 11 in the left-right direction. The supply port 14s is formed behind the exhaust port 14e. The supply port 14s is a vent for supplying the air-conditioned air whose temperature has been adjusted by the refrigeration cycle device 20 in the air-conditioning device 1 to the air-conditioned space. The exhaust port 14e is an opening inside the housing 10 from which a part of the air whose temperature has been adjusted by the refrigeration cycle device 20 is exhausted. The air blown out from the exhaust port 14e is blown to the outside of the air-conditioned space. For example, when the air conditioner 1 performs a cooling operation, cold air is blown out from the supply port 14s and warm air is blown out from the exhaust port 14e. Further, when the air conditioner 1 performs the heating operation, hot air is blown out from the supply port 14s and cold air is blown out from the exhaust port 14e.

The main body case 15 has a box shape with an open upper part. In the main body case 15, each component constituting the refrigerating cycle device 20 and the blower device 30 is arranged. The main body case 15 includes a partition portion for partitioning the inside of the main body case 15.

The blower 30 includes a supply blower 30s that sends air to the supply port 14s and an exhaust blower 30e that sends air to the exhaust port 14e. The blower 30 is an axial blower that blows air in a direction along the axial direction of the rotation shaft of the motor that rotates the blades of the blower 30. However, as the blower device 30, a blower other than the axial flow blower may be adopted.

In FIG. 3, the refrigeration cycle device 20 is housed inside the housing 10. The refrigeration cycle apparatus 20 constitutes a vapor compression type refrigeration cycle. The refrigeration cycle device 20 includes a compressor 21, a condenser 22, a decompression unit 23, and an evaporator 24. The refrigeration cycle device 20 includes a refrigerant pipe 70 that provides a refrigerant flow path. The refrigerant discharged from the compressor 21 flows in the order of the condenser 22, the decompression unit 23, and the evaporator 24, and repeats a series of cycles sucked into the compressor 21. The refrigerating cycle device 20 circulates the refrigerant by operating the compressor 21 to cool or heat the air blown to the vicinity of the seat, which is the space to be air-conditioned.

An accumulator may be provided in the refrigerant flow path from the evaporator 24 to the compressor 21. According to this, only the gas-phase refrigerant can be returned to the compressor 21 by performing gas-liquid separation of the refrigerant using an accumulator.

As the refrigerant that circulates in the refrigeration cycle device 20, an HFC-based refrigerant such as R134a can be adopted. However, the refrigerant of the refrigeration cycle device 20 may be any refrigerant whose high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant and can form a steam compression type subcritical refrigeration cycle. As the refrigerant, an HFO-based refrigerant such as R1234yf or a natural refrigerant such as R744 may be adopted. Further, the refrigerant contains refrigerating machine oil for lubricating the drive of the compressor 21.

The compressor 21 is a device that sucks in the vapor phase refrigerant, compresses it, and discharges it. The compressor 21 compresses the gas phase refrigerant to bring the vapor phase refrigerant into a high temperature and high pressure state. The compressor 21 is configured as an electric compressor in which a fixed-capacity compression mechanism having a fixed discharge capacity is driven by an electric motor. The compressor 21 is arranged at the rear inside the main body case 15.

As the compression mechanism of the compressor 21, various compression mechanisms such as a reciprocating type compression mechanism and a vane type compression mechanism can be adopted. When the refrigerant is compressed using a cylinder as in the reciprocating compression mechanism, the axial direction of the cylinder is the compression direction of the refrigerant. However, as the compression mechanism of the compressor 21, a mechanism that does not use a cylinder may be adopted. For example, a scroll-type compression mechanism that moves a pair of spiral bodies relative to each other can be adopted. In this case, the compression direction of the refrigerant is a direction orthogonal to the rotation axis of the spiral body. For example, if the rotation axis of the spiral body is in the direction along the left-right direction, the radial direction having the components in the front-rear direction and the up-down direction is the compression direction of the refrigerant. Since large vibrations are mainly generated by the compression of the compressor 21, the compression direction of the compressor 21 is the vibration direction of the compressor 21. Here, the vibration direction is the direction in which the compressor 21 vibrates most.

The electric motor constituting the compressor 21 can electrically control the rotation speed. Therefore, the refrigerant discharge capacity of the compressor 21 can be controlled by electrically controlling the rotation speed of the electric motor.

The condenser 22 includes a heat exchange unit formed in a flat plate shape by laminating a plurality of tubes and fins. The condenser 22 exchanges heat between the high-temperature and high-pressure gas-phase refrigerant flowing inside and the surrounding air to condense the gas-phase refrigerant into the liquid-phase refrigerant. In other words, heat is applied to the surrounding air to reduce the energy of the refrigerant. Therefore, the air around the condenser 22 is heated. The condenser 22 is arranged on the right side of the main body case 15. The condenser 22 is provided at a position where it overlaps with the hot air vent 12 in the vertical direction. The heat exchange portion in the condenser 22 is formed to be larger than the opening area of the hot air vent 12. Therefore, the air sucked from the hot air vent 12 passes through the heat exchange portion of the condenser 22. The condenser 22 provides an example of a heat exchanger.

The pressure reducing unit 23 is configured so that the refrigerant flow path is narrower than that of the other refrigerant pipes 70. By passing through the decompression unit 23, the pressure of the liquid phase refrigerant is lowered, and the liquid phase refrigerant becomes a low temperature and low pressure liquid phase refrigerant. In other words, the refrigerant easily evaporates when it passes through the decompression unit 23. The decompression unit 23 is arranged on the front side in the main body case 15. As the decompression unit 23, a fixed throttle such as a capillary tube can be adopted. However, as the pressure reducing unit 23, an expansion valve capable of electrically controlling the throttle opening may be adopted.

The evaporator 24 includes a heat exchange unit formed in a flat plate shape by laminating a plurality of tubes and fins. The evaporator 24 exchanges heat between the low-temperature low-pressure liquid-phase refrigerant flowing inside and the surrounding air to evaporate the liquid-phase refrigerant into the gas-phase refrigerant. In other words, the energy of the refrigerant rises by removing heat from the surrounding air. Therefore, the air around the evaporator 24 is cooled. The evaporator 24 is arranged on the left side of the main body case 15. The evaporator 24 is provided at a position where it overlaps with the cold air vent 13 in the vertical direction. The heat exchange portion in the evaporator 24 is formed to be larger than the opening area of the cold air vent 13. Therefore, the air sucked from the cold air vent 13 passes through the heat exchange portion of the evaporator 24. The evaporator 24 provides an example of a heat exchanger.

The air conditioner 1 includes a blower support portion 55 between the condenser 22 and the evaporator 24. The blower support portion 55 is a component for arranging the blower device 30 at an appropriate position. The blower support portion 55 includes a supply opening 47s and an exhaust opening 47e. The supply opening 47s is an opening for mounting the supply blower 30s. The exhaust opening 47e is an opening for attaching the exhaust blower 30e. The supply opening 47s and the exhaust opening 47e are provided adjacent to each other in the front-rear direction.

The air conditioner 1 is between the condenser 22 and the evaporator 24, and includes a blower destination switching unit 40 below the blower device 30. The air destination switching unit 40 is a mechanism for switching the air destination of the hot air heated by the condenser 22 and the cold air cooled by the evaporator 24.

The blow destination switching unit 40 includes a supply slide door 46s, an exhaust slide door 46e, and a drive motor 50. The supply slide door 46s and the exhaust slide door 46e are plate-shaped members that slide in the left-right direction. The temperature of the air-conditioned air supplied from the supply port 14s to the air-conditioned space is controlled by the stop position of the supply sliding door 46s. The temperature of the wind exhausted to the outside from the exhaust port 14e is controlled by the stop position of the exhaust sliding door 46e.

The drive motor 50 is a motor that provides a driving force for sliding the supply slide door 46s and the exhaust slide door 46e. The drive motor 50 is connected to the supply slide door 46s and the exhaust slide door 46e via a shaft and a gear. Therefore, by rotating the drive motor 50, the supply slide door 46s and the exhaust slide door 46e can be slid in the left-right direction.

The air flow in the air conditioner 1 will be described below by taking the case of performing the cooling operation as an example. In FIG. 4, a hot air side ventilation passage 17 is formed between the condenser 22 and the bottom surface of the main body case 15. The warm air heated by the condenser 22 flows through the ventilation passage 17 on the warm air side. On the other hand, a cold air side ventilation passage 18 is formed between the evaporator 24 and the bottom surface of the main body case 15. The cold air cooled by the evaporator 24 flows through the air passage 18 on the cold air side. A hot air supply opening 42s is formed between the hot air side ventilation passage 17 and the supply blower 30s. On the other hand, a cold air supply opening 44s is formed between the cold air side ventilation passage 18 and the supply blower 30s. The supply sliding door 46s is located below the supply blower 30s.

The supply sliding door 46s is located on the far right side. In this state, the hot air supply opening 42s is closed by the supply slide door 46s. Therefore, warm air does not flow through the supply blower 30s. On the other hand, the cold air supply opening 44s is not closed by the supply sliding door 46s. Therefore, as shown by the arrow CA, cold air flows through the supply blower 30s.

In FIG. 5, a warm air exhaust opening 42e is formed between the hot air side ventilation passage 17 and the exhaust blower 30e. On the other hand, a cold air exhaust opening 44e is formed between the cold air side ventilation passage 18 and the exhaust blower 30e. The exhaust sliding door 46e is located on the leftmost side. In this state, the hot air exhaust opening 42e is not closed by the exhaust sliding door 46e. Therefore, as shown by the arrow WA, warm air flows through the exhaust blower 30e. On the other hand, the cold air exhaust opening 44e is closed by the exhaust sliding door 46e. Therefore, cold air does not flow through the exhaust blower 30e.

In summary, the cooling operation can be performed by configuring the supply blower 30s to flow cold air and the exhaust blower 30e to flow warm air. Here, a part of the warm air may be configured to flow through the supply blower 30s during the cooling operation. In this case, a part of the cold air is mixed with the exhausted air. According to this, the temperature of the air conditioning air supplied to the air conditioning target space can be raised as compared with the case where only the cold air is supplied. In other words, the temperature of the supplied air-conditioning air can be controlled by controlling the mixing ratio of the cold air and the hot air. When the heating operation is performed, the temperature of the conditioned air is raised by increasing the ratio of the hot air to that of the cold air, and the air is supplied to the air-conditioned space.

The detailed structure of the refrigerant pipe 70 constituting the refrigeration cycle device 20 will be described below. In FIG. 3, the refrigerant pipe 70 includes a compressor side pipe 71, a heat exchanger side pipe 72, and a heat exchanger inter-heat exchanger pipe 73. The compressor side pipe 71 is a pipe that extends continuously and integrally from the compressor 21. The compressor side pipe 71 includes a discharge pipe 71u provided on the discharge side of the compressor 21 and a suction pipe 71d provided on the suction side of the compressor 21. The axial direction of the discharge pipe 71u is a direction along the left-right direction. The axial direction of the suction pipe 71d is a direction along the left-right direction. The compressor 21 sucks the refrigerant from the suction pipe 71d, compresses the refrigerant, and then discharges the refrigerant from the discharge pipe 71u. Hereinafter, a case where a scroll type compression mechanism is adopted as the compressor 21 will be described as an example.

The discharge pipe 71u is provided on the right side surface of the compressor 21. The suction pipe 71d is provided on the left side surface of the compressor 21. In other words, in the compressor 21, the surface provided with the suction pipe 71d is the surface opposite to the surface provided with the discharge pipe 71u.

Two pipes extend from the condenser 22 or the evaporator 24, which is a heat exchanger. Of the two pipes that extend continuously and integrally from the heat exchanger, the pipe that is closer to the compressor 21 in the flow of the refrigerant is the heat exchanger side pipe 72. Of the two pipes that extend continuously and integrally from the heat exchanger, the pipe that is farther from the compressor 21 in the flow of the refrigerant is the heat exchanger inter-heat exchanger pipe 73.

The heat exchanger side pipe 72 includes a condenser side pipe 72u that is continuously and integrally extending from the condenser 22, and an evaporator side pipe 72d that is continuously and integrally extending from the evaporator 24. The axial direction of the condenser side pipe 72u is a direction along the front-rear direction. The axial direction of the evaporator side pipe 72d is a direction along the front-rear direction. The heat exchanger inter-heater piping 73 connects the condenser 22 and the evaporator 24. A part of the heat exchanger inter-heater piping 73 has a narrower refrigerant flow path than the other piping, and functions as a decompression unit 23 for reducing the pressure of the refrigerant.

The refrigerant pipe 70 includes a connection pipe 79 and a vibration-proof pipe 80. The connection pipe 79 is a pipe that connects the pipes to each other. The connection pipe 79 includes a discharge side connection pipe 79u and a suction side connection pipe 79d. The connecting pipe 79 includes a portion extending along the left-right direction, which is the axial direction of the compressor-side pipe 71. Further, the connection pipe 79 includes a portion extending along the front-rear direction, which is the axial direction of the heat exchanger side pipe 72. The connecting pipe 79 includes a bent portion that smoothly connects a portion extending along the left-right direction and a portion extending along the front-rear direction. In other words, the connecting pipe 79 includes a bent portion for changing the axial direction of the pipe.

The anti-vibration pipe 80 is a pipe for reducing vibration transmitted through the refrigerant pipe 70. The anti-vibration pipe 80 is made of a soft material having higher elasticity than pipes such as the compressor side pipe 71 and the heat exchanger side pipe 72 constituting the refrigerant pipe 70. The anti-vibration pipe 80 flexibly displaces with respect to vibration and suppresses the transmission of vibration. The amount of displacement of the anti-vibration pipe 80 can be secured more by the displacement caused by expanding and contracting in the direction intersecting the axial direction than by the displacement caused by being compressed in the axial direction. Therefore, it is possible to effectively reduce the vibration of the component in the direction intersecting the axial direction of the vibration-proof pipe 80 rather than the component in the axial direction of the vibration-proof pipe 80.

The material constituting the compressor side pipe 71, the heat exchanger side pipe 72, the heat exchanger inter-heat exchanger pipe 73, and the connection pipe 79 is a metal material. On the other hand, the material constituting the anti-vibration pipe 80 is a material softer than the metal material constituting the compressor side pipe 71 and the like, and is a material in which the refrigerant is as difficult to permeate as possible. As a result, the vibration-proof piping 80 can exhibit two functions, a vibration-proof function for reducing vibration and a piping function for providing a stable refrigerant flow path. As the material constituting the anti-vibration pipe 80, a rubber material such as hydrogenated nitrile rubber (HNBR), which is a material used for a sealing member such as an O-ring, can be adopted.

The material constituting the anti-vibration pipe 80 is not limited to the rubber material. A low elasticity resin material may be adopted as the material constituting the anti-vibration pipe 80. Resin materials generally have lower refrigerant permeability than rubber materials. Therefore, the amount of the refrigerant that permeates from the inside to the outside of the vibration isolation pipe 80 and leaks can be reduced. Resin materials generally have higher heat resistance than rubber materials. Therefore, even when heated by a high-temperature refrigerant, it is easy to stably maintain an appropriate shape and performance. Resin materials generally have higher strength than rubber materials. Therefore, even when a large external force such as vibration is applied, it is easy to stably maintain an appropriate shape.

The vibration-proof pipe 80 includes a discharge-side first vibration-proof pipe 81u, a discharge-side second vibration-proof pipe 82u, a suction-side first vibration-proof pipe 81d, and a suction-side second vibration-proof pipe 82d. The discharge-side first vibration-proof pipe 81u is provided between the discharge-side pipe 71u and the discharge-side connection pipe 79u. The discharge side second vibration isolation pipe 82u is provided between the discharge side connection pipe 79u and the condenser side pipe 72u. In other words, the discharge-side second vibration-proof pipe 82u is provided at a position farther from the compressor 21 in the refrigerant flow path than the discharge-side first vibration-proof pipe 81u. The discharge-side first vibration-proof pipe 81u provides an example of the first vibration-proof pipe. The discharge-side first vibration-proof pipe 81u provides an example of the discharge-side vibration-proof pipe. The discharge side second anti-vibration pipe 82u provides an example of the second anti-vibration pipe. The discharge-side second vibration-proof pipe 82u provides an example of the discharge-side vibration-proof pipe.

The suction side first vibration isolation pipe 81d is provided between the suction pipe 71d and the suction side connection pipe 79d. The suction side second vibration isolation pipe 82d is provided between the suction side connection pipe 79d and the evaporator side pipe 72d. In other words, the suction-side second vibration-proof pipe 82d is provided at a position farther from the compressor 21 in the refrigerant flow path than the suction-side first vibration-proof pipe 81d. The suction-side first vibration-proof pipe 81d provides an example of the first vibration-proof pipe. The suction side first vibration isolation pipe 81d provides an example of the suction side vibration isolation pipe. The suction side second anti-vibration pipe 82d provides an example of the second anti-vibration pipe. The suction side second vibration isolation pipe 82d provides an example of the suction side vibration isolation pipe.

The length Lu1 of the discharge-side first vibration-proof pipe 81u along the axial direction is shorter than the length Lc of the refrigerant pipe 70 from the compressor 21 to the discharge-side first vibration-proof pipe 81u. In other words, the length Lu1 of the first anti-vibration pipe 81u on the discharge side is shorter than the length Lc along the axial direction of the discharge pipe 71u. The length Lu2 of the discharge-side second vibration-proof pipe 82u along the axial direction is shorter than the length from the compressor 21 in the refrigerant pipe 70 to the discharge-side second vibration-proof pipe 82u. The length Ld1 of the suction-side first vibration-proof pipe 81d along the axial direction is shorter than the length from the compressor 21 in the refrigerant pipe 70 to the suction-side first vibration-proof pipe 81d. The length Ld2 of the suction-side second vibration-proof pipe 82d along the axial direction is shorter than the length from the compressor 21 in the refrigerant pipe 70 to the suction-side second vibration-proof pipe 82d.

In summary, the length of the anti-vibration pipe 80 is shorter than the length from the compressor 21 to the anti-vibration pipe 80 in the refrigerant pipe 70. Further, the length of the anti-vibration pipe 80 is shorter than the length of the compressor side pipe 71. Here, when the length of the discharge pipe 71u and the length of the suction pipe 71d are different, the shortest length is regarded as the length of the compressor side pipe 71. Further, the length of the anti-vibration pipe 80 is shorter than the length of the compressor 21 in the lateral direction. The length of the anti-vibration pipe 80 is less than half the length from the compressor 21 to the heat exchanger in the refrigerant pipe 70. As a result, the length of the vibration-proof pipe 80, in which the refrigerant easily leaks, is shortened as compared with the pipe made of a metal material, and the leakage of the refrigerant in the entire refrigerant pipe 70 is suppressed.

The length Lu2 of the discharge-side second vibration-proof pipe 82u is shorter than the length Lu1 of the discharge-side first vibration-proof pipe 81u. Therefore, the amount of the refrigerant leaking from the discharge-side second vibration-proof pipe 82u is smaller than the amount of the refrigerant leaking from the discharge-side first vibration-proof pipe 81u. The length Ld2 of the suction-side second vibration-proof pipe 82d is shorter than the length Ld1 of the suction-side first vibration-proof pipe 81d. Therefore, the amount of the refrigerant leaking from the suction side second vibration isolation pipe 82d is smaller than the amount of the refrigerant leaking from the suction side first vibration isolation pipe 81d.

The refrigerant pipe 70 from the compressor 21 to the condenser 22 includes a bent portion, and includes a portion extending in the left-right direction and a portion extending in the front-rear direction. In other words, the length component of the refrigerant pipe 70 from the compressor 21 to the condenser 22 can be divided into a left-right direction component and a front-rear direction component. The left-right component indicates the total length of the pipes in the left-right direction. The anteroposterior component indicates the total length of the pipes in the anteroposterior direction. In the length component of the refrigerant pipe 70 from the compressor 21 to the condenser 22, the left-right component is larger than the front-rear component. In the length component of the refrigerant pipe 70 from the compressor 21 to the evaporator 24, the left-right component is larger than the front-rear component. However, the magnitude relationship between the left-right component and the front-rear component in each portion of the refrigerant pipe 70 is not limited to the above example.

The discharge-side second anti-vibration pipe 82u is provided at a position closer to the condenser 22 than the compressor 21 which is a vibration source in the refrigerant pipe 70 from the compressor 21 to the condenser 22. More specifically, the discharge-side second anti-vibration pipe 82u is provided at a position closer to the condenser 22 than the compressor 21 with respect to the front-rear direction component in the length of the refrigerant pipe 70 from the compressor 21 to the condenser 22. ing. Here, the close position with respect to the anteroposterior component indicates a close position when only the anteroposterior component is compared. For example, the front-rear direction component of the pipe from the discharge-side second vibration-proof pipe 82u to the condenser 22 is smaller than the front-rear direction component of the pipe from the discharge-side second vibration-proof pipe 82u to the compressor 21. In this case, the discharge-side second anti-vibration pipe 82u is located closer to the condenser 22 than the compressor 21 in terms of components in the front-rear direction.

Further, the discharge-side first vibration-proof pipe 81u is provided at a position closer to the condenser 22 than the compressor 21 with respect to the left-right component in the length of the refrigerant pipe 70 from the compressor 21 to the condenser 22. Here, the close position with respect to the left-right component indicates a close position when only the left-right component is compared. For example, the left-right component of the pipe from the discharge-side first vibration-proof pipe 81u to the condenser 22 is smaller than the left-right component of the pipe from the discharge-side first vibration-proof pipe 81u to the compressor 21. In this case, the discharge-side first anti-vibration pipe 81u is located closer to the condenser 22 than the compressor 21 in terms of the front-rear direction component. The discharge-side first vibration-proof pipe 81u is provided at a position closer to the condenser 22 than the compressor 21 in the left-right direction in which the left-right direction, which is the traveling direction of vibration, is the axial direction. Further, the discharge-side second anti-vibration pipe 82u is provided at a position closer to the condenser 22 than the compressor 21 in the front-rear direction, which is the traveling direction of vibration.

The suction side second vibration isolation pipe 82d is provided at a position closer to the evaporator 24 than the compressor 21 which is a vibration source in the refrigerant pipe 70 from the compressor 21 to the evaporator 24. More specifically, the suction-side second anti-vibration pipe 82d is provided at a position closer to the evaporator 24 than the compressor 21 with respect to the front-rear direction component in the length of the refrigerant pipe 70 from the compressor 21 to the evaporator 24. ing. Further, the suction-side first anti-vibration pipe 81d is provided at a position closer to the evaporator 24 than the compressor 21 with respect to the left-right component in the length of the refrigerant pipe 70 from the compressor 21 to the evaporator 24. In other words, the suction-side first vibration-proof pipe 81d is provided at a position closer to the evaporator 24 than the compressor 21 in the left-right direction, which is the traveling direction of vibration, in the left-right direction. Further, the suction side second vibration isolation pipe 82d is provided at a position closer to the evaporator 24 than the compressor 21 in the front-rear direction, which is the traveling direction of vibration.

In summary, the vibration isolation pipe 80 is provided at a position closer to the heat exchanger than the compressor 21 which is the vibration source in the refrigerant pipe 70 from the compressor 21 to the heat exchanger. As a result, the vibration generated in the compressor 21 is transmitted to the vibration isolation pipe 80 at a position closer to the heat exchanger than the compressor 21. In other words, it is easy to secure a long length from the compressor 21 which is the vibration source to the vibration isolation pipe 80.

The longer the distance from the compressor 21 which is the vibration source to the anti-vibration pipe 80, the smaller the spring constant with respect to the displacement of the anti-vibration pipe 80. The spring constant with respect to displacement will be described below. For example, it is assumed that the vibration of a vibration source such as the compressor 21 causes the piping such as the refrigerant pipe 70 to be displaced so as to be tilted by 1 ° as compared with the normal state. In this case, the closer the position is to the vibration source, the smaller the displacement amount in the radial direction of the pipe, and the farther away from the vibration source, the larger the displacement amount in the radial direction of the pipe. Therefore, when the elastic body such as the vibration isolation pipe 80 is arranged at a position close to the vibration source and when it is arranged at a position far from the vibration source, the displacement amount with respect to the vibration is larger when the elastic body is arranged at a position far from the vibration source. Become. That is, by arranging the elastic body at a position far from the vibration source, the spring constant becomes smaller than when it is arranged at a position close to the vibration source. As described above, even if the elastic bodies are made of the same material and have the same shape, the apparent spring constant that changes depending on the distance from the vibration source is the spring constant with respect to the displacement.

The anti-vibration pipe 80 is a cylindrical pipe made of a material softer than metal. The anti-vibration pipe 80 is deformed in the axial direction by being pulled or compressed by an external force applied in the direction along the axial direction. The anti-vibration pipe 80 is deformed in the radial direction by an external force applied in the radial direction, which is a direction orthogonal to the axial direction. In other words, the anti-vibration pipe 80 is deformed in the radial direction by a shearing force. When an external force of the same magnitude is applied to each of the axial direction and the radial direction of the anti-vibration pipe 80, the amount of deformation in the radial direction is larger than the amount of deformation in the axial direction. Further, the anti-vibration pipe 80 has a larger amount of deformation in the axial direction and a larger amount of deformation in the radial direction than the pipe made of metal. That is, the vibration-proof pipe 80 tends to reduce vibration in the axial direction and the radial direction as compared with a pipe made of at least metal.

The axial direction of the first anti-vibration pipe 81u on the discharge side is a direction along the left-right direction. The discharge-side first anti-vibration pipe 81u can effectively reduce the vibration of the components in the front-rear direction and the up-down direction, which are the directions intersecting in the axial direction. In particular, by arranging the piping at a position away from the compressor 21 in the left-right direction, which is the axial direction, it is easy to enhance the vibration reducing effect in the front-rear direction and the up-down direction in the first vibration-proof pipe 81u on the discharge side. The axial direction of the second anti-vibration pipe 82u on the discharge side is a direction along the front-rear direction. The discharge-side second anti-vibration pipe 82u can effectively reduce the vibration of the components in the left-right direction and the up-down direction, which are the directions intersecting in the axial direction. In particular, by arranging the second vibration isolation pipe 82u on the discharge side at a position away from the compressor 21 in the front-rear direction, which is the axial direction, it is easy to enhance the effect of reducing vibration in the left-right direction and the up-down direction.

The axial direction of the suction-side first anti-vibration pipe 81d is a direction along the left-right direction. The suction-side first anti-vibration pipe 81d can effectively reduce the vibration of the components in the front-rear direction and the up-down direction, which are the directions intersecting in the axial direction. In particular, by arranging the piping at a position away from the compressor 21 in the left-right direction, which is the axial direction, it is easy to enhance the effect of reducing vibration in the front-rear direction and the up-down direction in the first vibration isolation pipe 81d on the suction side. The axial direction of the second vibration isolation pipe 82d on the suction side is a direction along the front-rear direction. The suction-side second anti-vibration pipe 82d can effectively reduce the vibration of the components in the left-right direction and the up-down direction, which are the directions intersecting in the axial direction. In particular, by arranging the position away from the compressor 21 in the front-rear direction, which is the axial direction, it is easy to enhance the effect of reducing vibration in the left-right direction and the up-down direction in the second vibration isolation pipe 82d on the suction side.

In summary, the vibration-proof pipe 80 includes a discharge-side first vibration-proof pipe 81u and a suction-side first vibration-proof pipe 81d as pipes capable of effectively reducing vibrations of components in the front-rear direction and the vertical direction. .. Further, the vibration-proof pipe 80 includes a discharge-side second vibration-proof pipe 82u and a suction-side second vibration-proof pipe 82d as pipes capable of effectively reducing vibrations of components in the left-right direction and the up-down direction. In other words, the anti-vibration pipe 80 can effectively reduce the vibration of the components in all directions of the front-rear direction, the left-right direction, and the up-down direction.

The detailed structure of the anti-vibration pipe 80 will be described below. The suction-side first vibration-proof pipe 81d has the same shape as the discharge-side first vibration-proof pipe 81u. Further, the suction side second vibration isolation pipe 82d has the same shape as the discharge side second vibration isolation pipe 82u. Further, the discharge-side second vibration-proof pipe 82u and the suction-side second vibration-proof pipe 82d have a shape in which the axial length of the discharge-side first vibration-proof pipe 81u is shortened, and are the same except for the length. .. Therefore, the structure of the vibration-proof pipe 80 other than the discharge-side first vibration-proof pipe 81u is basically the same as the structure of the discharge-side first vibration-proof pipe 81u. Hereinafter, the detailed structure of the vibration-proof pipe 80 will be described by taking the discharge-side first vibration-proof pipe 81u as an example.

In FIG. 6, cylindrical connecting portions 77 are provided at both ends of the discharge-side first anti-vibration pipe 81u in the axial direction. The tubular connecting portion 77 is made of a metal material. The first vibration-proof pipe 81u on the discharge side and the cylindrical connection portion 77 are firmly adhered and fixed. A bolt portion is formed on the outer side of the tubular connecting portion 77 in the radial direction. A nut portion is formed on the outer side of the discharge pipe 71u and the discharge side connection pipe 79u in the radial direction. The bolt portion and the nut portion are used to fasten and fix the pipes to each other.

The end of the discharge pipe 71u is inserted into the cylindrical connecting portion 77 in a state where the pipes are fastened and fixed to each other. An O-ring is provided at a portion where the discharge pipe 71u and the cylindrical connection portion 77 overlap in the radial direction. As a result, the leakage of the refrigerant from the gap between the pipes is suppressed. In a state where the pipes are fastened and fixed to each other, the end portion of the discharge side connecting pipe 79u is in a state of being inserted into the cylindrical connecting portion 77. An O-ring is provided at a portion where the discharge pipe 71u and the cylindrical connection portion 77 overlap in the radial direction. As a result, the leakage of the refrigerant from the gap between the pipes is suppressed.

In a state where the pipes are fastened and fixed to each other, the vibration of the discharge pipe 71u is transmitted to the tubular connecting portion 77 in contact with the discharge pipe 71u without being significantly reduced. Therefore, up to the cylindrical connection portion 77 in contact with the discharge pipe 71u may be regarded as the discharge pipe 71u.

In FIG. 7, the center line CL in the discharge-side first anti-vibration pipe 81u is shown by a alternate long and short dash line. The inner diameter dimension of the tubular connecting portion 77 is the same as the inner diameter dimension Da of the first vibration isolation pipe 81u on the discharge side. Further, the inner diameter dimension Da of the first anti-vibration pipe 81u on the discharge side is equal to the inner diameter dimension of the discharge pipe 71u and the inner diameter dimension of the discharge side connecting pipe 79u. In other words, the inner diameter of the refrigerant pipe 70 is the same for the anti-vibration pipe 80 and the other pipes. On the other hand, the outer diameter dimension Db of the first anti-vibration pipe 81u on the discharge side is larger than the outer diameter dimension of the cylindrical connecting portion 77.

The wall thickness of the first anti-vibration pipe 81u on the discharge side is larger than the wall thickness of the cylindrical connection portion 77. The wall thickness of the cylindrical connection portion 77 is equal to the wall thickness of the discharge pipe 71u and the discharge side connection pipe 79u. In other words, the wall thickness of the refrigerant pipe 70 is different between the anti-vibration pipe 80 and the other pipes. The length Lu1 of the discharge-side first vibration-proof pipe 81u is not more than twice the inner diameter dimension Da of the discharge-side first vibration-proof pipe 81u. The length Mu1 from the end to the center of the discharge-side first vibration-proof pipe 81u is smaller than the outer diameter dimension Db of the discharge-side first vibration-proof pipe 81u. For example, the outer diameter dimension Db of the first anti-vibration pipe 81u on the discharge side is 12 mm, and the inner diameter dimension Da is 6 mm. For example, the length Lu1 of the discharge-side first vibration-proof pipe 81u is 6 mm, and the length Mu1 from the end to the center of the discharge-side first vibration-proof pipe 81u is 3 mm. For example, the wall thickness of the refrigerant pipe 70 is 1 mm, and the wall thickness of the discharge side first vibration isolation pipe 81u is 3 mm.

The tubular connecting portion 77 includes a flange portion 78 at an end portion in the axial direction. The flange portion 78 is provided in an annular shape that is continuous along the circumferential direction. The outer diameter dimension of the flange portion 78 is slightly larger than the outer diameter dimension of the first vibration isolation pipe 81u on the discharge side. In other words, the flange portion 78 slightly protrudes outward in the radial direction from the discharge-side first vibration-proof pipe 81u.

The discharge-side first vibration-proof pipe 81u includes a contact surface 88 in contact with the flange portion 78. The contact surface 88 of the first anti-vibration pipe 81u on the discharge side is in continuous annular contact with the flange portion 78. As a result, the leakage of the refrigerant from between the first vibration-proof pipe 81u on the discharge side and the cylindrical connection portion 77 is suppressed.

The discharge-side first vibration-proof pipe 81u is fixed to the cylindrical connecting portion 77 by adhering the flange portion 78 and the contact surface 88. The first anti-vibration pipe 81u on the discharge side and the cylindrical connection portion 77 are adhered to each other without a gap, and the leakage of the refrigerant is suppressed.

In a state where a high-pressure refrigerant is flowing through the refrigerant pipe 70, a force that tries to expand from the inside to the outside of the refrigerant pipe 70 acts due to the pressure of the refrigerant. The first vibration-proof pipe 81u on the discharge side is softer than the metal material and easily deforms so as to bulge outward. If the deformation that bulges outward is too large, the refrigerant tends to leak due to the deformation of the first vibration-proof pipe 81u on the discharge side, and the pipe function cannot be properly exerted. In particular, the smaller the wall thickness of the discharge-side first vibration-proof pipe 81u and the longer the length Lu1 of the discharge-side first vibration-proof pipe 81u, the greater the deformation that bulges outward. Therefore, it is necessary to maintain a state in which the discharge-side first vibration-proof pipe 81u can stably exert its piping function by increasing the wall thickness and shortening the length of the discharge-side first vibration-proof pipe 81u. be.

The first anti-vibration pipe 81u on the discharge side and the discharge pipe 71u may be directly bonded and fixed without passing through the tubular connecting portion 77. In this case, a flange portion 78 similar to the cylindrical connection portion 77 is formed in the discharge pipe 71u, and the discharge side first vibration isolation pipe 81u and the discharge pipe 71u are directly bonded and fixed.

The vibration transmission when the air conditioner 1 is driven will be described below. In FIG. 3, in the compressor 21 which is a vibration source, vibration including components in all directions of the left-right direction, the front-back direction, and the up-down direction can be generated. However, when the compressor 21 is provided with a scroll type compression mechanism, large vibrations are generated in the front-rear direction and the up-down direction, and the vibrations generated in the left-right direction are relatively small. The vibration generated in the compressor 21 is transmitted to the first vibration isolation pipe 81u on the discharge side via the discharge pipe 71u. In the first vibration-proof pipe 81u on the discharge side, among the transmitted vibrations, mainly the components in the front-rear direction and the components in the vertical direction are reduced.

The vibration that cannot be completely reduced by the discharge-side first vibration-proof pipe 81u is transmitted to the discharge-side second vibration-proof pipe 82u via the discharge-side connection pipe 79u. In the second vibration-proof pipe 82u on the discharge side, among the transmitted vibrations, mainly the left-right component and the vertical component are reduced. As a result, the vibration transmitted to the condenser side pipe 72u is in a state in which the components in all directions of the left-right direction, the front-rear direction, and the up-down direction are reduced. Therefore, even when the condenser 22 vibrates, the vibration can be reduced. Therefore, the vibration transmitted from the condenser 22 to the air-conditioned space via the air-conditioned air can be reduced. In other words, it is possible to reduce the abnormal noise generated in the air-conditioned space when the air-conditioning device 1 is driven.

Vibration is reduced on the evaporator 24 side as well as on the condenser 22. More specifically, the vibration generated in the compressor 21 is transmitted to the suction side first vibration isolation pipe 81d via the suction pipe 71d. In the suction side first vibration isolation pipe 81d, among the transmitted vibrations, mainly the front-rear direction component and the vertical direction component are reduced.

The vibration that cannot be completely reduced by the suction side first vibration isolation pipe 81d is transmitted to the suction side second vibration isolation pipe 82d via the suction side connection pipe 79d. In the second vibration isolation pipe 82d on the suction side, among the transmitted vibrations, mainly the left-right component and the vertical component are reduced. As a result, the vibration transmitted to the evaporator side pipe 72d is in a state in which the components in all directions of the left-right direction, the front-rear direction, and the up-down direction are reduced. Therefore, even when the evaporator 24 vibrates, the vibration can be reduced. Therefore, the vibration transmitted from the evaporator 24 to the air-conditioned space via the air-conditioned air can be reduced. In other words, it is possible to reduce the abnormal noise generated in the air-conditioned space when the air-conditioning device 1 is driven.

According to the above-described embodiment, the length Mu1 from the axial end portion to the central portion of the anti-vibration pipe 80 is shorter than the outer diameter dimension Db of the anti-vibration pipe 80. Here, the anti-vibration pipe 80 tends to be deformed easily because the local stress due to the refrigerant pressure tends to be concentrated in the central portion of the anti-vibration pipe 80. Therefore, the amount of deformation in the central portion is reduced as compared with the case where the length Mu1 from the axial end portion to the central portion of the anti-vibration pipe 80 is longer than the outer diameter dimension Db of the anti-vibration pipe 80. It is easy to maintain the shape of the anti-vibration pipe 80 in a stable manner. Therefore, it is easy to stably exert the anti-vibration function of the anti-vibration pipe 80. Therefore, a small refrigeration cycle device can be provided.

The discharge-side first anti-vibration pipe 81u is provided at a position closer to the condenser 22 than the compressor 21 in the left-right direction component of the refrigerant pipe 70 from the compressor 21 to the condenser 22. Here, the left-right component is a directional component orthogonal to the vibration direction, which is the direction in which the compressor 21 vibrates most. Therefore, the discharge-side first vibration-proof pipe 81u can be arranged at a position away from the compressor 21 in the left-right direction. Therefore, it is easy to improve the vibration isolation function by reducing the spring constant with respect to the vibration in the front-rear direction and the up-down direction. Similar to the discharge-side first vibration-proof pipe 81u, the suction-side first vibration-proof pipe 81d can easily enhance the vibration-proof function against vibrations in the front-rear direction and the vertical direction.

The axial direction of the first anti-vibration pipe 81u on the discharge side is the left-right direction. Here, the left-right direction is a direction orthogonal to the vibration direction, which is the direction in which the compressor 21 vibrates most. Therefore, the discharge-side first anti-vibration pipe 81u can function as the anti-vibration pipe 80 capable of greatly reducing vibration in the front-rear direction and the up-down direction. The discharge-side first anti-vibration pipe 81u has a high anti-vibration function against vibrations in the front-rear direction and the up-down direction from the two viewpoints of the axial direction and the distance from the compressor 21. Similar to the discharge-side first vibration-proof pipe 81u, the suction-side first vibration-proof pipe 81d also has a high vibration-proof function against vibrations in the front-rear direction and the vertical direction.

The discharge-side second anti-vibration pipe 82u is provided at a position closer to the condenser 22 than the compressor 21 in the front-rear direction component of the refrigerant pipe 70 from the compressor 21 to the condenser 22. Here, the front-rear direction component is a direction component along the vibration direction, which is the direction in which the compressor 21 vibrates most. Therefore, the second vibration isolation pipe 82u on the discharge side can be arranged at a position away from the compressor 21 in the front-rear direction. Therefore, it is easy to improve the vibration isolation function by reducing the spring constant with respect to the vibration in the left-right direction and the up-down direction. Similar to the discharge side second vibration isolation pipe 82d, the suction side second vibration isolation pipe 82d can easily enhance the vibration isolation function against vibrations in the left-right direction and the vertical direction.

The axial direction of the second anti-vibration pipe 82u on the discharge side is the front-rear direction. Here, the front-rear direction is a direction along the vibration direction, which is the direction in which the compressor 21 vibrates most. Therefore, the discharge-side second anti-vibration pipe 82u can function as the anti-vibration pipe 80 capable of greatly reducing vibration in the left-right direction and the up-down direction. The second anti-vibration pipe 82u on the discharge side has a high anti-vibration function against vibrations in the left-right direction and the up-down direction from the two viewpoints of the axial direction and the distance from the compressor 21. The second vibration-proof pipe 82d on the suction side also has a high vibration-proof function against vibrations in the left-right direction and the vertical direction, similarly to the second vibration-proof pipe 82u on the discharge side.

The length of the anti-vibration pipe 80 is shorter than the length from the compressor 21 to the anti-vibration pipe 80 in the refrigerant pipe 70. In other words, the anti-vibration pipe 80 is provided at a position farther from the compressor 21 than the distance corresponding to the length of the anti-vibration pipe 80. Therefore, the displacement in the vibration-proof pipe 80 is compared with the case where the vibration-proof pipe 80 is arranged at a position where the length from the compressor 21 to the vibration-proof pipe 80 in the refrigerant pipe 70 is shorter than the length of the vibration-proof pipe 80. The spring constant for can be reduced. Therefore, it is easy to enhance the anti-vibration function of the anti-vibration pipe 80. Further, the refrigerant leakage caused by the vibration-proof pipe 80 can be suppressed as compared with the case where the length of the vibration-proof pipe 80 is longer than the length from the compressor 21 to the vibration-proof pipe 80 in the refrigerant pipe 70. Therefore, it is easy to stabilize the piping function of the anti-vibration piping 80. As described above, the anti-vibration function and the piping function of the anti-vibration pipe 80 can be enhanced. Therefore, it is possible to provide a small refrigeration cycle device 20.

When applying the refrigeration cycle device 20 to an air conditioner 1 such as a seat air conditioner, it is necessary to store the refrigeration cycle device 20 in the limited storage space of the housing 10. Therefore, downsizing the refrigeration cycle device 20 is particularly important when the refrigeration cycle device 20 is applied to a seat air conditioner.

The anti-vibration pipe 80 is a material softer than the metal material used for the compressor side pipe 71 and the like. Therefore, the vibration-proof pipe 80 is likely to be expanded or contracted or deformed by vibration, and is more likely to permeate the vibration-proof pipe 80 and leak refrigerant than a metal material. Therefore, it is very important to shorten the length of the anti-vibration pipe 80 made of a material that leaks refrigerant more easily than the metal material in order to maintain the stable piping function of the entire refrigerant pipe 70.

The anti-vibration pipe 80 is a material softer than the metal material used for the compressor side pipe 71 and the like. Therefore, the vibration-proof pipe 80 is more likely to be deformed by vibration, and the vibration-proof pipe 80 itself is more likely to be damaged due to deformation than the metal pipe. In particular, the longer the anti-vibration pipe 80 is, the more the local stress due to the refrigerant pressure is likely to be concentrated in the central portion of the anti-vibration pipe 80, and the larger the deformation is likely to be. Therefore, shortening the length of the anti-vibration pipe 80 is very important for maintaining the stable piping function of the entire refrigerant pipe 70. Further, since the length of the vibration-proof pipe 80 is short, excessive deformation of the vibration-proof pipe 80 is suppressed, and the piping function of the vibration-proof pipe 80 is stabilized. Therefore, the reinforcing thread used for the purpose of increasing the rigidity of the vibration isolation pipe 80 can be omitted.

The length Lu1 of the discharge-side first vibration-proof pipe 81u is not more than twice the inner diameter dimension Da of the discharge-side first vibration-proof pipe 81u. In other words, the length of the anti-vibration pipe 80 is not more than twice the inner diameter Da of the anti-vibration pipe 80. Therefore, it is easier to suppress the leakage of the refrigerant caused by the vibration-proof pipe 80 as compared with the case where the length of the vibration-proof pipe 80 is longer than twice the inner diameter dimension Da of the vibration-proof pipe 80. Further, as compared with the case where the length of the vibration-proof pipe 80 is made longer than twice the inner diameter dimension Da of the vibration-proof pipe 80, it is easy to prevent the vibration-proof pipe 80 from being excessively deformed.

The discharge-side second anti-vibration pipe 82u is provided at a position closer to the condenser 22 than the compressor 21 in the traveling direction of the vibration generated by the compressor 21. Further, the suction side second vibration isolation pipe 82d is provided at a position closer to the evaporator 24 than the compressor 21 in the traveling direction of the vibration generated by the compressor 21. In other words, the anti-vibration pipe 80 is provided at a position closer to the heat exchanger than the compressor 21 in the traveling direction of the vibration generated by the compressor 21. Therefore, the spring constant with respect to the displacement of the vibration-proof pipe 80 can be made smaller than that in the case where the vibration-proof pipe 80 is provided at a position close to the compressor 21 which is the vibration source. In other words, even when a material having a relatively hard property is used for the anti-vibration pipe 80, the apparent spring constant can be reduced. Alternatively, the apparent spring constant can be reduced even in the case of a short pipe shape having a small displacement amount with respect to an external force. Therefore, it is easy to secure a high degree of freedom in the material and shape of the anti-vibration pipe 80.

The axial direction of the first anti-vibration pipe 81u on the discharge side is the left-right direction, and the compressor 21 is a scroll compressor whose rotation axis is the left-right direction. In other words, the axial direction of the vibration isolation pipe 80 is the direction along the rotation axis of the compressor 21. Therefore, the vibration-proof piping 80 can effectively reduce the vibration in the radial direction of the rotating shaft of the compressor 21, which tends to generate large vibrations.

The anti-vibration pipe 80 includes a first anti-vibration pipe 81u on the discharge side and a second anti-vibration pipe 82u on the discharge side. Further, the vibration-proof pipe 80 includes a suction-side first vibration-proof pipe 81d and a suction-side second vibration-proof pipe 82d. In other words, the anti-vibration pipe 80 includes a first anti-vibration pipe and a second anti-vibration pipe provided between the first anti-vibration pipe and the heat exchanger. Therefore, vibration transmission from the compressor 21 to the heat exchanger can be suppressed by using the plurality of vibration isolation pipes 80. Here, the shorter the length of the anti-vibration pipe 80, the easier it is to suppress the leakage of the refrigerant due to excessive deformation, and the longer the length, the easier it is to reduce the spring constant. In other words, the shorter the anti-vibration pipe 80, the more stable the piping function is, and the longer the one, the easier it is to exert the anti-vibration function. Therefore, by providing a plurality of anti-vibration pipes 80 having a short length, it is possible to obtain the necessary anti-vibration function as a whole of the anti-vibration pipe 80 while suppressing the leakage of the refrigerant due to the excessive deformation of each of the anti-vibration pipe 80. be able to.

The axial direction of the first anti-vibration pipe 81u on the discharge side is the left-right direction, and the axial direction of the second anti-vibration pipe 82u on the discharge side is the front-rear direction. The axial direction of the suction-side first vibration-proof pipe 81d is the left-right direction, and the axial direction of the suction-side second vibration-proof pipe 82d is the front-rear direction. In other words, the axial direction of the second anti-vibration pipe is a direction that intersects the axial direction of the first anti-vibration pipe. Therefore, it is possible to effectively reduce the vibration of components in different directions between the first anti-vibration pipe and the second anti-vibration pipe. For example, the discharge-side first anti-vibration pipe 81u effectively reduces the vibration of the components in the front-rear direction and the up-down direction, and the discharge-side second anti-vibration pipe 82u effectively reduces the vibration of the components in the left-right direction and the up-down direction. To reduce. Therefore, even when vibrations having components in different directions are generated in the compressor 21, the components in each direction of the vibration can be effectively reduced.

The vibration-proof pipe 80 includes a discharge-side first vibration-proof pipe 81u and a suction-side first vibration-proof pipe 81d. Further, the anti-vibration pipe 80 includes a second anti-vibration pipe 82u on the discharge side and a second anti-vibration pipe 82d on the suction side. In other words, the vibration isolation pipe 80 includes a discharge side vibration isolation pipe that reduces the vibration transmitted from the compressor 21 to the condenser 22, and a suction side vibration isolation pipe that reduces the vibration transmitted from the compressor 21 to the evaporator 24. It is equipped with piping. Therefore, both the abnormal noise generated when the vibration of the condenser 22 is transmitted to the air-conditioned space via the air-conditioning wind and the abnormal noise generated when the vibration of the evaporator 24 is transmitted to the air-conditioned space via the air-conditioned air. Can be suppressed.

The anti-vibration pipe 80 is made of a rubber material. Therefore, the material can be selected from a large number of candidates as compared with the case where the material used for the vibration isolation pipe 80 is selected from the materials other than the rubber material. Therefore, it is easy to select a soft material with a small spring constant.

The anti-vibration pipe 80 is made of a resin material. Therefore, it is easy to select a material that satisfies the performance required for the vibration isolation pipe 80 in addition to the softness, such as a material having low refrigerant permeability, a material having high heat resistance, and a material having high strength.

The material of the refrigerant pipe 70 is different between the vibration-proof pipe 80 and the portion other than the vibration-proof pipe 80. Therefore, the portion of the refrigerant pipe 70 that is the vibration-proof pipe 80 and the portion other than the vibration-proof pipe 80 can be easily distinguished. Therefore, when a problem such as damage to the vibration-proof pipe 80 occurs, it is easy to check the state of the vibration-proof pipe 80, which is the damaged part.

Although the case where the refrigerant pipe 70 includes a plurality of vibration-proof pipes 80 has been described as an example, the configuration may include only one vibration-proof pipe 80. Further, instead of providing the connection pipe 79, a vibration-proof pipe 80 having a bent portion may be provided, and the compressor side pipe 71 and the heat exchanger side pipe 72 may be connected only by the vibration-proof pipe 80. According to this, since the axial direction of the anti-vibration pipe 80 changes, it is easy to absorb the vibration of each direction component.

Second Embodiment This embodiment is a modification based on the preceding embodiment. In this embodiment, a connecting member 290 for connecting the second vibration-proof pipe 282u on the discharge side and the first vibration-proof pipe 281d on the suction side is provided. Further, an inclined surface 288b is provided on the contact surface 288 of the vibration isolation pipe 280.

In FIG. 8, both the discharge pipe 71u and the suction pipe 71d are provided on the right side surface of the compressor 21. The refrigerant pipe 70 includes a compressor side pipe 71, a heat exchanger side pipe 72, a connection pipe 79, and a vibration isolation pipe 280.

The vibration-proof pipe 280 includes a discharge-side first vibration-proof pipe 281u, a discharge-side second vibration-proof pipe 282u, a suction-side first vibration-proof pipe 281d, and a suction-side second vibration-proof pipe 282d. The discharge-side first vibration-proof pipe 281u is provided between the discharge-side pipe 71u and the discharge-side connection pipe 79u. The discharge side second vibration isolation pipe 282u is provided between the discharge side connection pipe 79u and the condenser side pipe 72u. In other words, the discharge-side second vibration-proof pipe 282u is provided at a position farther from the compressor 21 in the refrigerant flow path than the discharge-side first vibration-proof pipe 281u. The discharge-side first vibration-proof pipe 281u provides an example of the first vibration-proof pipe. The discharge-side first vibration-proof pipe 281u provides an example of the discharge-side vibration-proof pipe. The discharge side second anti-vibration pipe 282u provides an example of the second anti-vibration pipe. The discharge-side second vibration-proof pipe 282u provides an example of the discharge-side vibration-proof pipe.

The suction side first vibration isolation pipe 281d is provided between the suction pipe 71d and the suction side connection pipe 79d. The suction side second vibration isolation pipe 282d is provided between the suction side connection pipe 79d and the evaporator side pipe 72d. In other words, the suction-side second vibration-proof pipe 282d is provided at a position farther from the compressor 21 in the refrigerant flow path than the suction-side first vibration-proof pipe 281d. The suction side first anti-vibration pipe 281d provides an example of the first anti-vibration pipe. The suction side first vibration isolation pipe 281d provides an example of the suction side vibration isolation pipe. The suction side second anti-vibration pipe 282d provides an example of the second anti-vibration pipe. The suction side second vibration isolation pipe 282d provides an example of the suction side vibration isolation pipe.

The length Lu1 of the discharge-side first vibration-proof pipe 281u along the axial direction is shorter than the length Lc of the refrigerant pipe 70 from the compressor 21 to the discharge-side first vibration-proof pipe 281u. In other words, the length Lu1 of the first anti-vibration pipe 281u on the discharge side is shorter than the length Lc along the axial direction of the discharge pipe 71u. The length Lu2 of the discharge-side second vibration-proof pipe 282u along the axial direction is shorter than the length of the refrigerant pipe 70 from the compressor 21 to the discharge-side second vibration-proof pipe 282u. The length Ld1 of the suction-side first vibration-proof pipe 281d along the axial direction is shorter than the length from the compressor 21 in the refrigerant pipe 70 to the suction-side first vibration-proof pipe 281d. The length Ld2 of the suction-side second vibration-proof pipe 282d along the axial direction is shorter than the length from the compressor 21 in the refrigerant pipe 70 to the suction-side second vibration-proof pipe 282d.

In summary, the length of the anti-vibration pipe 280 is shorter than the length of the refrigerant pipe 70 from the compressor 21 to the anti-vibration pipe 280. Further, the length of the anti-vibration pipe 280 is shorter than the length of the compressor side pipe 71. Here, since the length of the discharge pipe 71u is shorter than the length of the suction pipe 71d, the length of the discharge pipe 71u is regarded as the length of the compressor side pipe 71. Further, the length of the anti-vibration pipe 280 is shorter than the length of the compressor 21 in the lateral direction. The length of the anti-vibration pipe 280 is less than half the length from the compressor 21 to the heat exchanger in the refrigerant pipe 70. As a result, the length of the vibration-proof pipe 280, in which the refrigerant easily leaks, is shortened as compared with the pipe made of a metal material, and the refrigerant leakage of the entire refrigerant pipe 70 is suppressed.

The length Lu2 of the discharge-side second vibration-proof pipe 282u is equal to the length Ld1 of the suction-side first vibration-proof pipe 281d. The discharge-side second vibration-proof pipe 282u and the suction-side first vibration-proof pipe 281d are provided side by side in the left-right direction. The second vibration-proof pipe 282u on the discharge side and the first vibration-proof pipe 281d on the suction side are integrally connected by a connecting member 290. The connecting member 290 suppresses a large change in the relative distance between the portion of the refrigerant pipe 70 from the compressor 21 to the condenser 22 and the portion of the refrigerant pipe 70 from the compressor 21 to the evaporator 24. There is.

The discharge-side second anti-vibration pipe 282u is provided at a position closer to the condenser 22 than the compressor 21 which is a vibration source in the refrigerant pipe 70 from the compressor 21 to the condenser 22. Further, the discharge-side second anti-vibration pipe 282u is provided at a position closer to the condenser 22 than the compressor 21 with respect to the components in the front-rear direction in the length of the refrigerant pipe 70 from the compressor 21 to the condenser 22. .. Further, the discharge-side first anti-vibration pipe 281u is provided at a position closer to the condenser 22 than the compressor 21 with respect to the component in the left-right direction in the length of the refrigerant pipe 70 from the compressor 21 to the condenser 22. .. In other words, the discharge-side first vibration-proof pipe 281u is provided at a position closer to the condenser 22 than the compressor 21 in the left-right direction, which is the traveling direction of vibration, in the left-right direction. Further, the discharge-side second anti-vibration pipe 282u is provided at a position closer to the condenser 22 than the compressor 21 in the front-rear direction, which is the traveling direction of vibration.

The refrigerant pipe 70 from the compressor 21 to the evaporator 24 includes a plurality of bent portions, and includes a plurality of portions extending in the left-right direction and a plurality of portions extending in the front-rear direction. In other words, the length component of the refrigerant pipe 70 from the compressor 21 to the evaporator 24 can be divided into a left-right direction component and a front-rear direction component. The left-right component indicates the total length of the pipes in the left-right direction, and the front-rear component indicates the total length of the pipes in the front-rear direction. The refrigerant pipe 70 from the compressor 21 to the evaporator 24 is provided in a U shape by being folded back in the left-right direction. Therefore, as the left-right components, the left-right component of the suction pipe 71d, the left-right component of the suction-side connecting pipe 79d, the left-right component of the suction-side second anti-vibration pipe 282d, and the left-right component of the evaporator-side pipe 72d. It is the total with the directional component. The vertical components include the vertical component of the suction pipe 71d, the vertical component of the suction side first vibration isolation pipe 281d, the vertical component of the suction side connection pipe 79d, and the vertical component of the evaporator side pipe 72d. It is the total with the ingredients. The left-right component of the refrigerant pipe 70 from the compressor 21 to the evaporator 24 is longer than the left-right component of the main body case 15. In the length component of the refrigerant pipe 70 from the compressor 21 to the evaporator 24, the left-right component is larger than the front-rear component.

The suction-side second anti-vibration pipe 282d is provided at a position closer to the evaporator 24 than the compressor 21 which is a vibration source in the refrigerant pipe 70 from the compressor 21 to the evaporator 24. More specifically, the suction side second vibration isolation pipe 282d is provided at a position closer to the evaporator 24 than the compressor 21 with respect to the front-rear direction component in the length of the refrigerant pipe 70 from the compressor 21 to the evaporator 24. ing. Further, the suction side second anti-vibration pipe 282d is provided at a position closer to the evaporator 24 than the compressor 21 with respect to the left-right component in the length of the refrigerant pipe 70 from the compressor 21 to the evaporator 24. In other words, the suction-side second anti-vibration pipe 282d is provided at a position closer to the condenser 22 than the compressor 21 in the left-right direction, which is the traveling direction of vibration, in the left-right direction.

In summary, the anti-vibration pipe 280 is provided at a position closer to the heat exchanger than the compressor 21 which is the vibration source in the refrigerant pipe 70 from the compressor 21 to the heat exchanger. As a result, the vibration generated in the compressor 21 is transmitted to the vibration isolation pipe 280 at a position closer to the heat exchanger than the compressor 21. In other words, it is easy to secure a long length from the compressor 21 which is the vibration source to the vibration isolation pipe 280. Therefore, the spring constant with respect to the displacement can be reduced as compared with the case where the anti-vibration pipe 280 is arranged at a position close to the compressor 21.

The anti-vibration pipe 280 is a cylindrical pipe made of a material softer than metal. The anti-vibration pipe 280 is deformed in the axial direction by being pulled or compressed by an external force applied in the direction along the axial direction. The anti-vibration pipe 280 is deformed in the radial direction by an external force applied in the radial direction, which is a direction orthogonal to the axial direction. In other words, it deforms in the radial direction due to the shearing force. When an external force of the same magnitude is applied to each of the axial direction and the radial direction of the anti-vibration pipe 280, the amount of deformation in the radial direction is larger than the amount of deformation in the axial direction. Further, the anti-vibration pipe 280 has a larger amount of deformation in the axial direction and a larger amount of deformation in the radial direction than the pipe made of metal. That is, the vibration-proof pipe 280 is more likely to reduce the vibration in the axial direction and the radial direction than the pipe made of at least metal.

The axial direction of the first anti-vibration pipe 281u on the discharge side is a direction along the left-right direction. The discharge-side first anti-vibration pipe 281u can effectively reduce the vibration of the components in the front-rear direction and the up-down direction, which are the directions intersecting in the axial direction. The axial direction of the second anti-vibration pipe 282u on the discharge side is a direction along the front-rear direction. The discharge-side second anti-vibration pipe 282u can effectively reduce the vibration of the components in the left-right direction and the up-down direction, which are the directions intersecting in the axial direction.

The axial direction of the suction-side first anti-vibration pipe 281d is a direction along the front-rear direction. The suction-side first anti-vibration pipe 281d can effectively reduce the vibration of the components in the left-right direction and the up-down direction, which are the directions intersecting in the axial direction. The axial direction of the second vibration isolation pipe 282d on the suction side is a direction along the left-right direction. The suction-side second anti-vibration pipe 282d can effectively reduce the vibration of the components in the front-rear direction and the up-down direction, which are the directions intersecting in the axial direction.

In summary, the vibration-proof pipe 280 includes a discharge-side first vibration-proof pipe 281u and a suction-side second vibration-proof pipe 282d as pipes capable of effectively reducing vibrations of components in the front-rear direction and the vertical direction. .. Further, the vibration-proof pipe 280 includes a discharge-side second vibration-proof pipe 282u and a suction-side first vibration-proof pipe 281d as pipes capable of effectively reducing vibrations of components in the left-right direction and the up-down direction. In other words, the anti-vibration pipe 280 can effectively reduce the vibration of the components in all directions of the front-rear direction, the left-right direction, and the up-down direction.

The detailed structure of the anti-vibration pipe 280 will be described below. The discharge-side first vibration-proof pipe 281u, the discharge-side second vibration-proof pipe 282u, the suction-side first vibration-proof pipe 281d, and the suction-side second vibration-proof pipe 282d have the same shape. In other words, the structure of the vibration-proof pipe 280 other than the discharge-side first vibration-proof pipe 281u is the same as the structure of the discharge-side first vibration-proof pipe 281u. Hereinafter, the detailed structure of the vibration-proof pipe 280 will be described by taking the discharge-side first vibration-proof pipe 281u as an example.

In FIG. 9, the center line CL in the discharge-side first anti-vibration pipe 281u is shown by a alternate long and short dash line. The inner diameter dimension Da of the first anti-vibration pipe 281u on the discharge side is the same as the inner diameter dimension of the cylindrical connecting portion 77. Further, the inner diameter dimension Da of the first vibration isolation pipe 281u on the discharge side is equal to the inner diameter dimension of the discharge pipe 71u and the inner diameter dimension of the discharge side connection pipe 79u. In other words, the inner diameter of the refrigerant pipe 70 is the same for the anti-vibration pipe 280 and the other pipes. On the other hand, the outer diameter dimension Db of the first anti-vibration pipe 281u on the discharge side is larger than the outer diameter dimension of the cylindrical connecting portion 77.

The wall thickness of the thickest portion of the first vibration isolation pipe 281u on the discharge side is larger than the wall thickness of the tubular connecting portion 77. The wall thickness of the cylindrical connection portion 77 is equal to the wall thickness of the discharge pipe 71u and the discharge side connection pipe 79u. In other words, the wall thickness of the refrigerant pipe 70 is different between the anti-vibration pipe 280 and the other pipes. The length Lu1 of the first anti-vibration pipe 281u on the discharge side is not more than twice the inner diameter Da of the first anti-vibration pipe 281u on the discharge side. The length Mu1 from the end to the center of the discharge-side first vibration-proof pipe 281u is smaller than the outer diameter dimension Db of the discharge-side first vibration-proof pipe 281u. For example, the outer diameter dimension Db of the first anti-vibration pipe 281u on the discharge side is 12 mm, and the inner diameter dimension Da is 6 mm. For example, the length Lu1 of the discharge-side first vibration-proof pipe 281u is 9 mm, and the length Mu1 from the end to the center of the discharge-side first vibration-proof pipe 281u is 4.5 mm. For example, the wall thickness of the refrigerant pipe 70 is 1 mm, and the wall thickness of the thickest portion of the discharge-side first vibration isolation pipe 281u is 3 mm.

The tubular connecting portion 77 includes a flange portion 278 at an axial end portion. The flange portion 278 is provided in an annular shape that is continuous along the circumferential direction. The flange portion 278 includes an orthogonal portion 278a and an inclined portion 278b. The orthogonal portion 278a is a portion of the flange portion 278 that extends along a direction orthogonal to the axial direction of the pipe. In other words, the orthogonal portion 278a is a portion extending along the radial direction of the pipe. The inclined portion 278b is a portion of the flange portion 278 that extends along a direction that intersects both the axial direction and the radial direction of the pipe. The inclined portion 278b is inclined by, for example, 45 ° with respect to the axial direction and the radial direction of the pipe. The orthogonal portion 278a is located outside the inclined portion 278b in the radial direction of the pipe.

The discharge-side first vibration-proof pipe 281u includes a contact surface 288 that is in contact with the flange portion 278. The contact surface 288 includes an orthogonal surface 288a and an inclined surface 288b. The orthogonal surface 288a is a surface of the contact surface 288 that extends along a direction orthogonal to the axial direction of the discharge-side first vibration isolation pipe 281u. In other words, the orthogonal surface 288a is a surface extending along the radial direction of the discharge-side first vibration isolation pipe 281u. The inclined surface 288b is a surface of the contact surface 288 that extends along a direction intersecting both the axial direction and the radial direction of the discharge side first vibration isolation pipe 281u. The inclined surface 288b is inclined by, for example, 45 ° with respect to the axial direction and the radial direction of the first vibration isolation pipe 281u on the discharge side. The orthogonal surface 288a is located outside the inclined surface 288b in the radial direction of the discharge-side first vibration isolation pipe 281u.

The contact surface 288 of the first anti-vibration pipe 281u on the discharge side is in continuous annular contact with the flange portion 278. More specifically, the orthogonal surface 288a of the contact surface 288 and the orthogonal portion 278a of the flange portion 278 are in contact with each other. Further, the inclined surface 288b of the contact surface 288 and the inclined portion 278b of the flange portion 278 are in contact with each other. As a result, the leakage of the refrigerant from between the first vibration-proof pipe 281u on the discharge side and the cylindrical connection portion 77 is suppressed.

The discharge-side first vibration-proof pipe 281u is fixed to the cylindrical connecting portion 77 by adhering the flange portion 278 and the contact surface 288. The first anti-vibration pipe 281u on the discharge side and the cylindrical connection portion 77 are adhered to each other without a gap, and the leakage of the refrigerant is suppressed.

In a state where a high-pressure refrigerant is flowing through the refrigerant pipe 70, a force that tries to expand from the inside to the outside of the refrigerant pipe 70 acts due to the pressure of the refrigerant. Therefore, the discharge-side first vibration-proof pipe 281u is pushed by the refrigerant pressure and applies a force to push the flange portion 278 outward in the radial direction. On the other hand, the flange portion 278 applies a reaction force that pushes the discharge-side first vibration-proof pipe 281u inward in the radial direction with respect to the pressing force from the discharge-side first vibration-proof pipe 281u. Here, the inclined portion 278b intersects in both the axial direction and the radial direction. Therefore, the inclined portion 278b can exert a large reaction force to push back inward in the radial direction as compared with the orthogonal portion 278a having no component intersecting in the radial direction. In this way, by providing the inclined portion 278b on the flange portion 278 and providing the inclined surface 288b on the contact surface 288, the reaction force in the radial direction is effectively applied to the first vibration isolation pipe 281u on the discharge side. Local stress can be relaxed.

When the discharge-side first vibration-proof pipe 281u is deformed so as to bulge outward, a shearing force is generated between the discharge-side first vibration-proof pipe 281u and the flange portion 278. This shearing force can act as a local stress that deforms the first vibration isolation pipe 281u on the discharge side. By providing the flange portion 278 with the orthogonal portion 278a and providing the contact surface 288 with the orthogonal surface 288a, the local stress caused by this shearing force can be relaxed.

The vibration transmission when the air conditioner 1 is driven will be described below. In FIG. 8, in the compressor 21 which is a vibration source, vibration including components in all directions of the left-right direction, the front-back direction, and the up-down direction can be generated. The vibration generated in the compressor 21 is transmitted to the first vibration isolation pipe 281u on the discharge side via the discharge pipe 71u. In the first vibration-proof pipe 281u on the discharge side, among the transmitted vibrations, mainly the components in the front-rear direction and the components in the vertical direction are reduced.

The vibration that cannot be completely reduced by the discharge-side first vibration-proof pipe 281u is transmitted to the discharge-side second vibration-proof pipe 282u via the discharge-side connection pipe 79u. In the second vibration-proof pipe 282u on the discharge side, among the transmitted vibrations, mainly the left-right component and the vertical component are reduced. As a result, the vibration transmitted to the condenser side pipe 72u is in a state in which the components in all directions of the left-right direction, the front-rear direction, and the up-down direction are reduced. Therefore, even when the condenser 22 vibrates, the vibration can be reduced. Therefore, the vibration transmitted from the condenser 22 to the air-conditioned space via the air-conditioned air can be reduced. In other words, it is possible to reduce the abnormal noise generated in the air-conditioned space when the air-conditioning device 1 is driven.

Vibration is reduced on the evaporator 24 side as well as on the condenser 22. More specifically, the vibration generated in the compressor 21 is transmitted to the suction side first vibration isolation pipe 281d via the suction pipe 71d. In the suction side first vibration isolation pipe 281d, among the transmitted vibrations, mainly the left-right component and the vertical component are reduced.

The vibration that cannot be completely reduced by the suction side first vibration isolation pipe 281d is transmitted to the suction side second vibration isolation pipe 282d via the suction side connection pipe 79d. In the second vibration isolation pipe 282d on the suction side, among the transmitted vibrations, mainly the components in the front-rear direction and the components in the vertical direction are reduced. As a result, the vibration transmitted to the evaporator side pipe 72d is in a state in which the components in all directions of the left-right direction, the front-rear direction, and the up-down direction are reduced. Therefore, even when the evaporator 24 vibrates, the vibration can be reduced. Therefore, the vibration transmitted from the evaporator 24 to the air-conditioned space via the air-conditioned air can be reduced. In other words, it is possible to reduce the abnormal noise generated in the air-conditioned space when the air-conditioning device 1 is driven.

According to the above-described embodiment, the contact surface 288 includes an inclined surface 288b inclined in a direction intersecting both the axial direction and the radial direction of the discharge side first vibration isolation pipe 281u. In other words, the contact surface 288 includes an inclined surface 288b that is inclined in a direction that intersects both the axial direction and the radial direction of the vibration isolator pipe 80. Therefore, a large reaction force from the inclined portion 278b of the flange portion 278 toward the inside in the radial direction can be applied to the inclined surface 288b. Therefore, the local stress applied to the vibration-proof pipe 80 can be relaxed, and large deformation of the vibration-proof pipe 80 can be suppressed.

The discharge-side second vibration-proof pipe 282u and the suction-side first vibration-proof pipe 281d are integrally formed by a connecting member 290. In other words, the discharge-side vibration-proof pipe and the suction-side vibration-proof pipe are integrally formed with the connecting member 290. Therefore, the number of parts can be reduced as compared with the case where the discharge-side vibration-proof pipe and the suction-side vibration-proof pipe are separately provided with connecting parts for connecting the pipes.

Other Embodiments The disclosure in this specification, drawings and the like is not limited to the exemplified embodiments. The disclosure includes exemplary embodiments and modifications by those skilled in the art based on them. For example, disclosure is not limited to the parts and / or element combinations shown in the embodiments. Disclosure can be carried out in various combinations. The disclosure can have additional parts that can be added to the embodiment. Disclosures include those in which the parts and / or elements of the embodiment are omitted. Disclosures include replacements or combinations of parts and / or elements between one embodiment and the other. The technical scope disclosed is not limited to the description of the embodiments. Some technical scopes disclosed are indicated by the claims description and should be understood to include all modifications within the meaning and scope equivalent to the claims statement.

Disclosure in the description, drawings, etc. is not limited by the description of the scope of claims. The disclosure in the description, drawings, etc. includes the technical ideas described in the claims, and further covers a wider variety of technical ideas than the technical ideas described in the claims. Therefore, various technical ideas can be extracted from the disclosure of the description, drawings, etc. without being bound by the description of the claims.

1 Air conditioner, 20 Refrigeration cycle equipment, 21 Compressor, 22 Condenser (heat exchanger), 23 Decompression unit, 24 Evaporator (heat exchanger), 70 Coolant piping, 71 Compressor side piping, 71u Discharge piping, 71d Suction piping, 72 heat exchanger side piping, 72u condenser side piping, 72d evaporator side piping, 77 tubular connection, 79 connection piping, 79u discharge side connection piping, 79d suction side connection piping, 80 vibration isolation piping, 81u Discharge side 1st vibration isolation pipe (1st vibration isolation pipe, discharge side vibration isolation pipe), 81d Suction side 1st vibration isolation pipe (1st vibration isolation pipe, suction side vibration isolation pipe), 82u Discharge side 2nd vibration isolation pipe Piping (second anti-vibration piping, discharge side anti-vibration piping), 82d suction side second anti-vibration piping (second anti-vibration piping, suction side anti-vibration piping), 88 contact surface, 280 anti-vibration piping, 281u discharge side first 1 Anti-vibration piping (1st anti-vibration piping, discharge side anti-vibration piping), 281d Suction side 1st anti-vibration piping (1st anti-vibration piping, suction side anti-vibration piping), 282u Discharge side 2nd anti-vibration piping (1st) 2 Anti-vibration piping, Discharge side anti-vibration piping), 282d Suction side 2nd anti-vibration piping (2nd anti-vibration piping, Suction side anti-vibration piping), 288 contact surface, 288a orthogonal surface, 288b inclined surface, 290 connecting member

Claims (11)

A compressor (21) that compresses the refrigerant,
A decompression unit (23) that decompresses the refrigerant,
Heat exchangers (22, 24) that exchange heat between the refrigerant and the surrounding air,
A refrigerant pipe (70) for connecting the compressor, the decompression unit, and the heat exchanger to provide an annular refrigerant flow path is provided.
The refrigerant pipe
The compressor side piping (71) continuously extending from the compressor and
The heat exchanger side piping (72) that continuously extends from the heat exchanger,
A vibration-proof pipe (80) provided between the compressor-side pipe and the heat exchanger-side pipe to reduce vibration transmitted from the compressor to the heat exchanger is provided.
The anti-vibration pipe is a pipe made of a material softer than the compressor-side pipe, and the length from the axial end to the center of the anti-vibration pipe is the length of the anti-vibration pipe. A refrigeration cycle device whose piping is shorter than the outer diameter. The anti-vibration pipe exchanges heat more than the compressor with respect to a directional component orthogonal to the vibration direction, which is the direction in which the compressor vibrates most, among the refrigerant pipes from the compressor to the heat exchanger. The refrigeration cycle apparatus according to claim 1, which is provided at a position close to the vessel. The refrigeration cycle apparatus according to claim 2, wherein the axial direction of the anti-vibration pipe is a direction orthogonal to the vibration direction. The anti-vibration pipe exchanges heat more than the compressor with respect to a directional component along the vibration direction, which is the direction in which the compressor vibrates most, among the refrigerant pipes from the compressor to the heat exchanger. The refrigeration cycle apparatus according to claim 1, which is provided at a position close to the vessel. The refrigeration cycle apparatus according to claim 4, wherein the axial direction of the vibration isolation pipe is a direction along the vibration direction. The anti-vibration piping
With the first anti-vibration piping (81u, 81d),
The refrigeration cycle apparatus according to any one of claims 1 to 5, further comprising a second anti-vibration pipe (82u, 82d) provided between the first anti-vibration pipe and the heat exchanger. .. The refrigeration cycle apparatus according to claim 6, wherein the axial direction of the second anti-vibration pipe is a direction intersecting the axial direction of the first anti-vibration pipe. The anti-vibration pipe includes a contact surface (288) that is in contact with a material that is harder than the anti-vibration pipe.
The contact surface according to any one of claims 1 to 7, wherein the contact surface includes an inclined surface (288b) inclined in a direction intersecting both the axial direction and the radial direction of the anti-vibration pipe. Refrigeration cycle equipment. The heat exchanger is
A condenser (22) that condenses the refrigerant and
Equipped with an evaporator (24) that evaporates the refrigerant
The heat exchanger side piping
The condenser side pipe (72u) extending continuously from the condenser and
The evaporator side pipe (72d) extending continuously from the evaporator is provided.
The anti-vibration piping
Discharge-side vibration-proof pipes (81u, 82u) provided between the compressor-side pipe and the condenser-side pipe to reduce vibration transmitted from the compressor to the condenser, and
The claim is provided with suction-side vibration-proof pipes (81d, 82d) provided between the compressor-side pipe and the evaporator-side pipe to reduce vibration transmitted from the compressor to the evaporator. The refrigeration cycle apparatus according to any one of 1 to 8. The refrigeration cycle device according to claim 9, wherein the discharge-side vibration-proof pipe and the suction-side vibration-proof pipe are integrally formed of a connecting member (290). The refrigeration cycle apparatus according to any one of claims 1 to 10, wherein the anti-vibration pipe is made of a rubber material.

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