KR20110064999A - Refrigerant cycle of air conditioner for vehicles - Google Patents

Abstract

PURPOSE: A freezing cycle of an air conditioner for a vehicle is provided to reduce noise due to refrigerant flow since refrigerant passing through a first evaporating unit flows to a compressor and other refrigerant passing through a second evaporating unit flows to the intake part of an ejector. CONSTITUTION: A freezing cycle of an air conditioner for a vehicle comprises a compressor(10), a condenser(20), an expansion valve(40), an ejector(50) and an evaporator(60). The compressor sucks and compresses refrigerant. The condenser condenses the compressed refrigerant. The expansion valve throttles the condensed refrigerant. The ejector applies Coanda effect to the refrigerant throttled by the expansion valve to suck the refrigerant through an intake part. The evaporator splits refrigerant discharged from the ejector through a splitting unit(65) and evaporates the split refrigerant. The evaporator a first evaporating unit(61) for sending evaporated refrigerant to the compressor and a second evaporating unit(62) for sending evaporated refrigerant to the intake part of the ejector.

Description

Refrigerant cycle of air conditioner for vehicles

The present invention relates to a refrigeration cycle of an air conditioner for a vehicle, and more particularly, to configure an ejector incorporating a Coanda effect between an expansion valve and an evaporator, and to separate the refrigerant discharged from the ejector through a splitting means (communication hole). After separately supplying the first and second evaporators, the refrigerant passing through the first evaporator flows to the compressor side and the refrigerant passing through the second evaporator flows to the suction side of the ejector, thereby being injected into the nozzle part of the ejector. The refrigerant can be dispersed by the annular nozzle to reduce the flow of refrigerant. Since the nozzle is annular, the flow volume can be increased to lower the suction pressure, and the ejector structure is simple and easy to manufacture. Cooling of automotive air conditioners with low suction pressure and improved performance and efficiency compared to conventional ejector systems It relates to a cycle.

The vehicle air conditioner is a vehicle interior that is installed for the purpose of securing the driver's front and rear view by removing the frost from the windshield or heating in the summer or winter, or during the rain or winter season. Such an air conditioning apparatus is usually equipped with a heating system and a cooling system at the same time, thereby cooling, heating, or ventilating the interior of a vehicle by selectively introducing outside air or bet, heating or cooling the air, and then blowing the air into the interior of the vehicle.

In general, the refrigeration cycle of such an air conditioning apparatus, as shown in Figure 1, a compressor (Compressor 1) for compressing and sending out the refrigerant, a condenser (Condenser) for condensing the high-pressure refrigerant from the compressor ( 2) an expansion valve 3 for condensing the liquefied refrigerant condensed in the condenser 2, and a low pressure liquid refrigerant condensed by the expansion valve 3 is blown to the vehicle interior. The evaporator 4 or the like that cools the air discharged to the room by the endothermic action of the evaporative latent heat of the refrigerant by evaporating by exchanging heat with the air is connected to the refrigerant pipe 5, and the following refrigerant circulation process is performed. Cool the interior of the car through.

When the cooling switch (not shown) of the vehicle air conditioner is turned on, the compressor 1 first drives the engine power and sucks and compresses the low-temperature, low-pressure gaseous refrigerant to the condenser 2 in a high-temperature, high-pressure gas state. The condenser 2 exchanges the gaseous refrigerant with outside air to condense it into a liquid of high temperature and high pressure. Subsequently, the liquid refrigerant discharged from the condenser 2 in the state of high temperature and high pressure is rapidly expanded by the throttling action of the expansion valve 3 and is sent to the evaporator 4 in the low temperature low pressure wet state, and the evaporator 4 is The refrigerant is heat-exchanged with the air blower (not shown) blowing into the vehicle interior. Accordingly, the refrigerant is evaporated from the evaporator 4, discharged into a gas state at low temperature and low pressure, and then sucked back into the compressor 1 to recycle the refrigeration cycle as described above. In the above refrigerant circulation process, the cooling of the vehicle interior is cooled by latent heat of evaporation of the liquid refrigerant circulating in the evaporator 4 while the air blown by the blower (not shown) passes through the evaporator 4 as described above. It is made by discharging the inside of the vehicle in the cold state.

Meanwhile, a receiver dryer (not shown) is provided between the condenser 2 and the expansion valve 3 to separate the refrigerant in the gas phase and the liquid phase, so that only the liquid refrigerant can be supplied to the expansion valve 3. .

And, Figure 2 is a configuration diagram showing a dual air conditioner system is applied to the conventional ejector, when explaining only the difference with the system of Figure 1, the refrigerant condensed in the condenser 2 is branched by the primary expansion valve (3a) and secondary After entering and expanding the expansion valve 3b, the refrigerant expanded in the primary expansion valve 3a is supplied to the ejector 6, and the refrigerant expanded in the secondary expansion valve 3b is the auxiliary evaporator 4b. Is supplied.

As the refrigerant supplied to the ejector 6 is injected through the nozzle 6a provided therein, the flow velocity is changed to a supersonic flow, whereby the pressure of the refrigerant passing through the nozzle 6a decreases to generate suction flow. Done. That is, as the refrigerant expanded from the primary expansion valve 3a is supplied to the ejector 6 and passes through the nozzle 6a, suction flow occurs at a pressure dropped by the increased flow rate. The refrigerant evaporated in the auxiliary evaporator 4b is sucked into the ejector 6 through the suction part 6b.

Inside the ejector 6, the refrigerant passing through the nozzle 6a and the refrigerant sucked from the auxiliary evaporator 4b are mixed, and after passing through a straight section for a predetermined period, the pressure is increased by the diffuser 6c again. The refrigerant boosted by the diffuser 6c flows into the compressor 1 after being introduced into the main evaporator 4a and evaporated.

On the other hand, the nozzle 6a provided in the ejector 6 is located in the same line as the refrigerant flow direction, and the ejector 6 carries the main flow and the suction part 6b passing through the nozzle 6a. Two flow evaporators (4a, 4b) can be used by forming a flow path that is separated into the suction flow sucked through and then merged into one outlet (diffuser).

As described above, in the system employing the ejector 6, the system performance and efficiency can be increased by using the suction flow and the boosting effect obtained by the ejector 6 effect.

However, in the prior art, a nozzle 6a must be installed inside to configure the ejector 6, in which an O-ring (not shown) is inserted in order to install the nozzle 6a, and the nozzle 6a is precisely installed. There is a problem in that the manufacturing cost increases because it must be processed and combined by indentation.

In addition, in order to increase the suction flow or lower the suction pressure, the flow rate of the main refrigerant passing through the nozzle 6a should be increased, but the performance of the optimized nozzle area is improved because the vehicle operating conditions vary from low flow rate to high flow rate. There was a limit to.

In addition, since the nozzle 6a is located at the center of the flow path inside the ejector 6, there is a problem that excessive noise occurs when the refrigerant flow rate increases.

In addition, a pipe for flowing refrigerant to the main evaporator 4a and the auxiliary evaporator 4b is required, respectively, and the refrigerant flowing to the auxiliary evaporator 4b requires a secondary expansion valve 3b for expansion. There was also an increasing problem.

An object of the present invention for solving the above problems is to configure the ejector incorporating the Coanda effect between the expansion valve and the evaporator, and to separate the refrigerant discharged from the ejector through the splitting means (communication holes). After each of the divided supply to the evaporator, the refrigerant passing through the first evaporator flows to the compressor side and the refrigerant passing through the second evaporator flows to the suction side of the ejector, whereby the refrigerant injected into the nozzle of the ejector is annular. It is dispersed by the nozzle part to reduce the refrigerant flow noise, and because the nozzle part is annular, the flow volume can be increased to lower the suction pressure, and the ejector structure is simple to manufacture and to reduce the cost. The low suction pressure provides a refrigeration cycle for vehicle air conditioners that can improve performance and efficiency compared to conventional ejector systems. The.

The present invention for achieving the above object is a compressor for sucking and compressing a refrigerant, a condenser for condensing the refrigerant compressed in the compressor, an expansion valve for condensing the refrigerant condensed in the condenser, and an throttling in the expansion valve The Coanda effect is applied to the flowing refrigerant, and the ejector which sucks the refrigerant through the suction unit and the refrigerant discharged from the ejector are divided by the dividing means to evaporate the divided refrigerant, respectively. An evaporator comprising a first evaporator for flowing to the compressor side and a second evaporator for flowing the evaporated refrigerant to the suction side of the ejector.

The present invention constitutes an ejector incorporating the Coanda effect between the expansion valve and the evaporator, and separately supplies and supplies the refrigerant discharged from the ejector to the first and second evaporators through the splitting means (communication holes). The refrigerant passing through the first evaporator flows to the compressor side and the refrigerant passing through the second evaporator flows to the suction side of the ejector, whereby the refrigerant discharged from the expansion valve and injected into the nozzle portion of the ejector rides on the inner wall of the annular nozzle portion. Since it is dispersed as it flows, refrigerant flow noise is reduced, and the nozzle portion is annular to increase the flow volume to lower the suction pressure, thereby lowering the suction pressure, thereby improving performance and efficiency compared to conventional ejector systems.

In addition, the structure of the ejector is simple, so that the manufacturing is easy and the cost is reduced.

In addition, by using only one expansion valve and forming a communication hole for dividing the refrigerant into the first and second evaporators inside the evaporator, a separate pipe for branching the refrigerant to the first and second evaporators is not required. You can save money.

In addition, by increasing the effect of boosting the refrigerant by the diffuser formed in the ejection pipe of the ejector, the overall efficiency of the air conditioner is improved.

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

Figure 4 is a block diagram showing a refrigeration cycle of a vehicle air conditioner according to the present invention, Figure 5 is a schematic perspective view showing the connection state of the evaporator and the ejector in the refrigeration cycle of the vehicle air conditioner according to the present invention, Figure 6 FIG. 7 is an exploded perspective view illustrating an ejector in a refrigeration cycle of a vehicle air conditioner according to the present invention, and FIG. 8 is an exploded perspective view of the ejector in the refrigeration cycle of a vehicle air conditioner according to the present invention. It is a cross section.

As shown, the refrigeration cycle of the vehicle air conditioner according to the present invention, the compressor (10)-> condenser 20-> internal heat exchanger (30)-> expansion valve (40)-> evaporator (60) refrigerant pipe ( In the refrigeration cycle configured by 5), the evaporator 60 is composed of a first evaporation unit 61 and a second evaporation unit 62 separated into two evaporation zones, and the expansion valve 40 and the evaporator. Between the 60, an ejector 50 incorporating a Coanda effect is provided.

First, the compressor 10 is driven by receiving power from a power supply source (engine or motor, etc.) while being discharged from the evaporator 60 to suck and compress the gaseous refrigerant that has passed through the internal heat exchanger 30, thereby compressing the high temperature and high pressure. It is discharged to the condenser 20 in the gas state of.

The condenser 20 heat-exchanges the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 10 with the outside air to condense it into a high-temperature, high-pressure liquid to discharge the expansion valve 40.

The expansion valve 40 rapidly expands the liquid refrigerant of high temperature and high pressure discharged from the condenser 20 by throttling to be in a wet state of low temperature and low pressure, and then passes through the ejector 50 to the evaporator ( 60).

Meanwhile, a receiver dryer (not shown) is installed between the condenser 20 and the expansion valve 40 to separate the refrigerant in the gas phase and the liquid, so that only the liquid refrigerant may be supplied to the expansion valve 40.

The evaporator 60 is throttled by the expansion valve 40 and passes through the ejector 50 to exchange heat with the air that is blown to the vehicle air. The discharged air is cooled.

The evaporator 60 divides the refrigerant discharged from the ejector 50 through the dividing means 65 to evaporate the divided refrigerants, and the first evaporator to flow the evaporated refrigerant to the compressor 10. 61 and a second evaporation part 62 for flowing the evaporated refrigerant to the suction part 55 side of the ejector 50.

That is, the single evaporator 60 is separated into two evaporation zones to form the first evaporator 61 and the second evaporator 62.

In addition, the first evaporator 61 and the second evaporator 62 are configured to overlap in the flow direction of air passing through the evaporator 60.

On the other hand, the first evaporator 61 and the second evaporator 62, the upper tank (61a, 62a) and the lower tank (61b, 62b) are provided, respectively, the upper tank (61a, 62a) and A plurality of tubes (not shown) are provided between the lower tanks 61b and 62b, and a heat dissipation fin (not shown) is interposed between the plurality of tubes. The evaporator 60 illustrated in the drawing is schematically illustrated, and various types of evaporator 60 may be used.

In addition, a partition wall 63 for partitioning both tanks 61a and 62a is formed between the upper tank 61a of the first evaporator 61 and the upper tank 62a of the second evaporator 62. It is. Of course, a partition wall is formed between the lower tank 61b of the first evaporator 61 and the lower tank 62b of the second evaporator 62 to partition both tanks 61b and 62b.

In addition, the dividing means 65 forms a communication hole 64 communicating the first evaporator 61 and the second evaporator 62 in the evaporator 60, and the ejector 50. Is configured to be connected to any one of the first evaporator 61 and the second evaporator 62, by dividing the refrigerant introduced into the evaporator 60 from the ejector 50 through the communication hole 64 The first evaporator 61 and the second evaporator 62 are respectively supplied.

Although the ejector 50 is configured to be connected to the first evaporator 61 in the drawing, it may be configured to be connected to the second evaporator 62.

In addition, the communication hole 64 is formed through the partition wall 63 for partitioning the upper tank 61a of the first evaporator 61 and the upper tank 61a of the second evaporator 62. , A plurality are formed spaced apart from each other.

In addition, the communication hole 64 is preferably formed adjacent to the inlet (61c) side of the evaporator 60 is connected to the ejector 50, the amount of the refrigerant distribution by adjusting the size of the communication hole (64). I can regulate it.

Therefore, the coolant discharged from the ejector 50 flows into the upper tank 61a of the first evaporator 61. At this time, the introduced coolant is divided through the communication hole 64, and part of the first evaporator is evaporated. While evaporating while flowing the inside of the portion 61, the rest flows into the upper tank 62a of the second evaporation portion 62 through the communication hole 64 and flows inside the second evaporation portion 62. It will evaporate.

The refrigerant discharged to the first evaporator 61 flows to the compressor 10 via the expansion valve 40, and the refrigerant discharged from the second evaporator 62 is the nose of the ejector 50. The suction flows to the suction unit 55 by the suction flow.

The reason that the refrigerant discharged from the first evaporator 61 passes through the expansion valve 40 is because the temperature of the refrigerant flowing from the evaporator 60 to the compressor 10 varies from the condenser 20 to the evaporator 60. This is to adjust the amount of refrigerant flowing to the side.

As such, the evaporator 60 is configured to be separated into a first evaporation unit 61 and a second evaporation unit 62, one inlet 61c connected to the ejector 50, and the compressor 10. And two outlets 61d and 62c for connecting with the suction part 55 of the ejector 50, respectively.

On the other hand, an internal heat exchanger (30) for exchanging heat between the refrigerant flowing from the condenser 20 to the expansion valve 40 and the refrigerant flowing from the evaporator 60 to the compressor 10 is installed.

The internal heat exchanger 30 exchanges heat of the refrigerant flowing into the evaporator 60 by mutually heat-exchanging the high temperature and high pressure liquid refrigerant before being throttled by the expansion valve 40 and the low temperature and low pressure gaseous refrigerant discharged from the evaporator 60. It stabilizes and reduces the amount of refrigerant pressure drop in the evaporator 60 and reduces the overheating area of the evaporator 60 having a relatively high temperature by setting the refrigerant to be completely vaporized to prevent the inflow of the liquid refrigerant into the compressor 10. Make it possible.

And, the ejector 50 is configured to suck the refrigerant through the suction unit 55 by applying a Coanda effect (Coanda effect) to the refrigerant flowing by throttling in the expansion valve (40).

The Coanda effect is a wall adsorption phenomenon of ultra-high velocity fluid. When the high-pressure fluid is injected into the annular nozzle 51, the fluid moves on the inner wall of the nozzle 51. At this time, a vacuum is generated in the center to suck the fluid in the opposite direction of the fluid movement direction.

The ejector 50 to which the Coanda effect is applied is connected to the second evaporation unit 62 and the suction unit 55 through which the suction hole 55a is penetrated, and the annular nozzle unit 51 is bolted. Are constructed in combination. At this time, an O-ring 58 is provided between the outer circumferential surface of the suction unit 55 and the inner circumferential surface of the nozzle unit 51 for sealing.

In the annular nozzle part 51, the suction part 55 is coupled to one side opening 52a, and the discharge pipe 54 connected to the evaporator 60 is connected to the other closing wall 52b. .

In addition, an inlet 53 is formed through the outer circumferential surface of the nozzle unit 51 so that refrigerant flowing from the expansion valve 40 is introduced, and a plurality of inlets 53 are formed on the outer circumferential surface of the nozzle unit 51. May be

A portion where the inner surface of the closing wall 52b and the discharge pipe 54 meet is preferably formed of a curved portion 52c.

That is, the refrigerant injected into the annular nozzle portion 51 is changed along the curved portion 52c formed on the discharge pipe 54 side to flow along the discharge pipe 54, where the discharge pipe ( Suction flow occurs in the opposite direction of 54).

At this time, the suction pressure is a performance difference according to the cross-sectional area in the annular nozzle portion 51 and the radius size of the curved portion 52c, and thus the curved portion 52c optimized for the cross-sectional area of the annular nozzle portion 51. It is desirable to set the radius.

Meanwhile, the suction part 55 and the discharge pipe 54 are formed on the concentric shaft, and the inlet 53 and the discharge pipe 54 formed on the outer circumferential surface of the nozzle part 51 are formed at right angles.

In addition, an outlet end of the suction part 55 is formed to be inserted into the nozzle 51, and is formed to maintain a predetermined gap with the closing wall 52b, and is injected into the nozzle 51 The refrigerant can be smoothly flowed to the discharge pipe (54).

In addition, a step portion 57 is formed on an outer circumferential surface of the suction part 55 inserted into the nozzle part 51 to secure a space for smooth flow of the refrigerant injected into the nozzle part 51.

In addition, a diffuser 54a having an increased inner diameter is formed on the outlet inner circumferential surface of the discharge pipe 54 to increase the pressure of the refrigerant.

On the other hand, the outer peripheral surface of the suction unit 55, the flange 56 for bolting the nozzle unit 51 is formed protruding.

Hereinafter, the operation of the refrigeration cycle of the vehicle air conditioner according to the present invention will be described.

First, the high temperature / high pressure gaseous refrigerant compressed by the compressor 10 is discharged into the condenser 20, and the gaseous refrigerant introduced into the condenser 20 is condensed through heat exchange with external air. After phase change to a high pressure liquid refrigerant, it is introduced into the internal heat exchanger (30).

After the high temperature / high pressure refrigerant introduced into the internal heat exchanger 30 performs mutual heat exchange with the low temperature / low pressure refrigerant flowing out of the evaporator 60 and flowing to the compressor 10, the refrigerant flows to the expansion valve 40. It flows in and decompresses / expands.

The refrigerant depressurized / expanded in the expansion valve 40 becomes a low temperature / low pressure atomized state and is injected into the nozzle unit 51 through an inlet 53 formed in the nozzle unit 51 of the ejector 50.

At this time, the Coanda effect is applied to the refrigerant injected into the nozzle unit 51. That is, the refrigerant injected into the nozzle unit 51 flows through the inner wall surface of the nozzle unit 51 and discharge pipe 54. The direction of the refrigerant is changed along the curved portion 52c formed at the side to be discharged through the discharge pipe 54. In this process, suction flow is generated in the opposite direction of the discharge pipe 54. Through the suction of the refrigerant discharged from the second evaporator 62.

Subsequently, the refrigerant discharged from the discharge pipe 54 of the ejector 50 flows into the upper tank 61a of the first evaporation unit 61 of the evaporator 60. At this time, the introduced refrigerant passes through the communication hole ( The upper tank (2) of the second evaporation unit 62 is evaporated through the heat exchange with the outside air while a part flows through the interior of the first evaporation unit 61, and the other portion through the communication hole 64. 62a) flows through the inside of the second evaporation part 62 and evaporates through external air and heat exchange.

The refrigerant discharged to the first evaporator 61 flows to the internal heat exchanger 30 via the expansion valve 40, and the refrigerant flowing to the internal heat exchanger 30 is expanded to the expansion valve in the condenser 20. After the heat exchange with the refrigerant flowing to 40, it is introduced into the compressor (10).

The refrigerant discharged from the second evaporator 62 is sucked into the suction unit 55 by suction flow due to the coanda effect of the ejector 50.

Thereafter, the refrigerant sucked into the suction unit 55 from the second evaporator 62 is mixed with the refrigerant injected into the nozzle unit 51 through the inlet 53 of the nozzle unit 51 and then the evaporator ( 60) is repeated to repeat the above process.

On the other hand, in the refrigerant circulation process as described above, the cooling of the vehicle interior is air blown by a blower (not shown) of the vehicle air conditioner while passing through the evaporator 60, the first evaporator 61 and the second evaporator ( 62 is cooled by the latent heat of evaporation of the liquid refrigerant circulating 62 and is discharged to the vehicle interior in a cool state.

1 is a configuration diagram showing a refrigeration cycle of a general vehicle air conditioner,

2 is a block diagram showing a dual air conditioning system to which a conventional ejector is applied,

3 is a cross-sectional view showing the ejector in FIG.

4 is a configuration diagram showing a refrigeration cycle of a vehicle air conditioner according to the present invention,

5 is a schematic perspective view illustrating a connection state between an evaporator and an ejector in a refrigeration cycle of a vehicle air conditioner according to the present invention;

6 is a perspective view showing an ejector in a refrigeration cycle of a vehicle air conditioner according to the present invention;

7 is an exploded perspective view showing an ejector in a refrigeration cycle of a vehicle air conditioner according to the present invention;

8 is a cross-sectional view showing an ejector in a refrigeration cycle of a vehicle air conditioner according to the present invention.

<Code Description of Main Parts of Drawing>

10: compressor 20: condenser

30: internal heat exchanger 40: expansion valve

50: ejector 51: nozzle unit

52a: opening 52b: closed wall

52c: curved portion 53: inlet

54: discharge pipe 54a: diffuser

55: suction part 55a: suction hole

56: flange 57: stepped portion

58: O-ring 60: evaporator

61: first evaporator 62: second evaporator

63: partition wall 64: communication hole

65: dividing means

Claims (8)

Compressor 10 for sucking and compressing the refrigerant, A condenser 20 for condensing the refrigerant compressed by the compressor 10, Expansion valve 40 for throttling the refrigerant condensed in the condenser 20, Ejector 50 for sucking the refrigerant through the suction unit 55 by applying a Coanda effect (Coanda effect) to the refrigerant flowing through the expansion valve 40, The refrigerant discharged from the ejector 50 is divided through the dividing means 65 to evaporate the divided refrigerant, and the first evaporator 61 and the evaporated refrigerant flowing the evaporated refrigerant to the compressor 10 side. A refrigeration cycle of a vehicle air conditioner, characterized in that consisting of an evaporator (60) consisting of a second evaporator (62) flowing to the suction part (55) side of the ejector (50). The method of claim 1, The dividing means (65) forms a communication hole (64) for communicating the first evaporator (61) and the second evaporator (62) in the evaporator (60). The first evaporator 61 and the second evaporator 62 are configured to be connected to each other, and the refrigerant introduced into the evaporator 60 from the ejector 50 is divided through the communication hole 64 and the first evaporator. Refrigeration cycle of a vehicle air conditioner, characterized in that to be supplied to each of the portion 61 and the second evaporation (62). The method of claim 2, The communication hole (64) is a refrigerating cycle of a vehicle air conditioner, characterized in that formed through the partition wall (63) for partitioning the first evaporation (61) and the second evaporation (62). The method of claim 1, The ejector 50, A suction part 55 connected to the second evaporation part 62, The suction part 55 is coupled to one side opening 52a, and the discharge pipe 54 connected to the evaporator 60 is formed in communication with the other closing wall 52b, and the expansion valve 40 is formed on an outer circumferential surface thereof. Refrigerating cycle of a vehicle air conditioner, characterized in that consisting of a nozzle unit 51 formed with an inlet (53) so that the refrigerant flowing from the inlet. The method of claim 4, wherein A portion where the inner surface of the closing wall (52b) and the discharge pipe 54 meet is formed of a curved surface portion (52c), the refrigeration cycle of the vehicle air conditioner. The method of claim 4, wherein The outlet end of the suction unit 55 is formed to be inserted into the nozzle unit 51, the refrigeration cycle of the vehicle air conditioner, characterized in that formed to maintain a predetermined gap with the closing wall (52b). The method of claim 4, wherein The suction unit 55 and the discharge pipe 54 is a refrigeration cycle of a vehicle air conditioner, characterized in that formed on the concentric axis. The method of claim 4, wherein And a diffuser (54a) having an increased inner diameter on the outlet inner circumferential surface of the discharge pipe (54) to increase the pressure of the refrigerant.

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