KR20110065000A - Refrigerant cycle of air conditioner for vehicles - Google Patents

Abstract

PURPOSE: A freezing cycle of an air conditioner for a vehicle is provided to prevent the performance decrease of the air conditioner or the irregular flow of refrigerant by decreasing the remaining amount of refrigerant and oil in an evaporator. 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 condenser condenses refrigerant compressed in the compressor. The expansion valve throttles the refrigerant condensed in the condenser. The ejector sucks refrigerant using an intake part using suction pressure, which is generated in a process refrigerant throttled in the expansion valve passes through the inside of the ejector. The evaporator comprises a first evaporating unit(61), a second evaporating unit(62), a first outlet, and a second outlet. The refrigerant evaporated by the first evaporating unit is discharged to the compressor through the first outlet.

Description

Refrigerant cycle of air conditioner for vehicles

The present invention relates to a refrigeration cycle of a vehicle air conditioner, and more particularly, to configure an ejector incorporating a Coanda effect between an expansion valve and an evaporator, and to divide the refrigerant discharged from the ejector into first and second evaporators, respectively. Supplying and evaporating, by disposing a first outlet for discharging the refrigerant evaporated in the first evaporator to the compressor side and a second outlet for discharging the refrigerant evaporated in the second evaporator to the suction side of the ejector, In addition, by reducing the amount of refrigerant and oil remaining in the evaporator, the air conditioner performance and the flow of refrigerant are not deteriorated due to the refrigerant and oil remaining in the evaporator when the air conditioner is operating. It is possible to prevent, and at low flow rate of the refrigerant sucked from the second evaporator to the suction part of the ejector only by the suction pressure of the ejector It relates to a refrigeration cycle of a vehicle air conditioner that can smoothly flow.

The vehicle air conditioner is a vehicle interior that is installed for the purpose of securing the driver's front and rear field of view by removing the frost that is caught in the windshield during rainy or winter seasons. In general, such an air conditioner is equipped with a heating system and a cooling system at the same time, and selectively introduces outside air or bet to heat or cool the air, and then blows it into the interior of the vehicle to cool, heat or ventilate 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. The refrigerant is evaporated from the evaporator (4) is discharged to a low-temperature low-pressure gas state and again sucked 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 then passed through a straight section for a predetermined period, and then boosted again by the diffuser 6c. 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.

And, when the low flow rate (when the flow rate of the refrigerant circulating the refrigeration cycle is low) or the air conditioner off according to the vehicle operating conditions, the refrigerant and oil is accumulated in the lower portion of the evaporator (4a, 4b),

In the prior art, as the suction part 6b of the ejector 6 is connected with an outlet (not shown) formed on the upper side of the auxiliary evaporator 4b, that is, the suction part 6b of the ejector 6 is connected. Since the refrigerant is sucked in from the upper side of the auxiliary evaporator 4b, the suction pressure generated by the ejector 6 during the low flow rate is also reduced, so that only the suction pressure of the ejector 6 is lower than the auxiliary evaporator 4b. Difficult to inhale refrigerant and oil accumulated in the tank.

Therefore, the refrigerant and oil remaining in the auxiliary evaporator 4b cause the performance and efficiency of the air conditioner to deteriorate and cause the flow of the refrigerant to be irregular.

In addition, there is a problem in that evaporation noise of the refrigerant remaining when the air conditioner is turned off while refrigerant and oil remain in the auxiliary evaporator 4b.

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 separately evaporate by supplying the refrigerant discharged from the ejector to the first and second evaporators, respectively. By disposing the first outlet for discharging the refrigerant evaporated in the first evaporator to the compressor side and the second outlet for discharging the refrigerant evaporated in the second evaporator to the suction part side of the ejector, remaining in the evaporator, By reducing the amount of refrigerant and oil to be prevented from deteriorating air conditioner performance or irregular flow of refrigerant due to the refrigerant and oil remaining in the evaporator when the air conditioner is operating, it is also possible to prevent the evaporation noise of the refrigerant remaining when the air conditioner is turned off. When the flow rate is low, only the suction pressure of the ejector can smoothly flow the refrigerant sucked from the second evaporator to the suction part of the ejector. To provide a refrigeration cycle of a vehicular air conditioning.

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 first evaporator to evaporate the divided refrigerant by dividing the ejector which sucks the refrigerant through the suction unit by using the suction pressure generated in the process of passing the refrigerant through the inside, and the refrigerant discharged from the ejector; A first outlet for discharging the refrigerant evaporated in the first evaporator to the compressor side and a second outlet for discharging the refrigerant evaporated in the second evaporator to the suction side of the ejector are provided below the second evaporator. Characterized in that consisting of the evaporator.

The present invention constitutes an ejector incorporating the Coanda effect between the expansion valve and the evaporator, and separates and evaporates the refrigerant discharged from the ejector into the first and second evaporators, respectively, and evaporates the refrigerant evaporated from the first evaporator. Air outlet by reducing the amount of refrigerant and oil remaining in the evaporator by disposing the first outlet for discharging the gas to the compressor side and the second outlet for discharging the refrigerant evaporated from the second evaporator to the suction side of the ejector. The refrigerant and oil remaining in the evaporator during operation can prevent the air conditioner performance from being deteriorated or the flow of the refrigerant become irregular, and also prevent the evaporation noise of the refrigerant remaining in the evaporator when the air conditioner is turned off.

In addition, since the amount of refrigerant and oil remaining in the evaporator is reduced, it is possible to smoothly flow the refrigerant sucked from the second evaporator to the suction part of the ejector only at the suction pressure of the ejector at low flow rate.

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 a connection state of the evaporator and the ejector in Figure 4, Figure 6 is another of the refrigeration cycle of the vehicle air conditioner according to the present invention FIG. 7 is a schematic perspective view illustrating a state in which an ejector is mounted in an evaporator in FIG. 6, and FIG. 8 is a combined perspective view illustrating an ejector in a refrigeration cycle of a vehicle air conditioner according to the present invention. An exploded perspective view showing an ejector in a refrigeration cycle of a vehicle air conditioner according to the present invention, Figure 10 is a cross-sectional view showing the ejector in the refrigeration cycle of a vehicle air conditioner according to the present invention.

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 is provided with a first evaporator 61 and a second evaporator 62 to divide the refrigerant discharged from the ejector 50 to evaporate the divided refrigerant.

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. have. 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 evaporator 60 has one inlet 61c connected to the ejector 50 and two outlets 61d for connecting to the compressor 10 and the suction unit 55 of the ejector 50, respectively. 62c).

That is, a first outlet 61d for discharging the evaporated refrigerant to the compressor 10 is formed in the first evaporator 61, and the evaporated refrigerant is ejected to the second evaporator 62. The second outlet 62c for discharging to the suction part 55 side of is formed.

In addition, the inlet 61c of the evaporator 60 is disposed above the evaporator 60, and the first outlet 61d and the second outlet 62c are disposed below the evaporator 60. The inlet 61c is formed at one side between the upper tanks 61a and 62a of the first and second evaporators 61 and 62, and the first outlet 61d is the lower portion of the first evaporator 61. The tank 61b is formed in communication with one side, and the second outlet 62c is formed in communication with one side of the lower tank 62b of the second evaporation part 62.

Here, the inlet 61c and the first and second outlets 61d and 62c may be formed in the same direction as shown in FIG. 7, or may be formed in opposite directions as shown in FIG. 5.

As such, the first and second outlets 61d and 62c of the first and second evaporators 61 and 62 are disposed under the evaporator 60, so that the refrigerant and oil remaining in the lower part of the evaporator 60 may be first. It flows smoothly to the compressor 10 side and the suction part 55 side of the ejector 50 through the 2 outlets 61d and 62c and remains in the evaporator 60 at the time of low flow rate or the air conditioner off according to the vehicle driving conditions. To reduce the refrigerant and oil.

In addition, as the refrigerant and oil remaining in the evaporator 60 is reduced, the refrigerant sucked into the suction part 55 of the ejector 50 from the second evaporator 62 only by the suction pressure of the ejector 50 during low flow rate. You can smoothly flow.

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.

In addition, the ejector 50 is configured to suck the refrigerant through the suction unit 55 by using the suction pressure generated during the passage of the refrigerant throttling in the expansion valve 40 and passing therein. That is, the ejector 50 is configured to suck the refrigerant through the suction unit 55 by applying a Coanda effect to the refrigerant passing through the inside.

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 ( In the opposite direction of 54), suction flow due to suction pressure is generated.

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.

In addition, the ejector 50 may be mounted in two ways as shown in FIGS. 5 and 7 to minimize the length of the mounting space and the connecting pipe and to optimize the refrigerant flow in the evaporator 60.

FIG. 5 shows that the ejector 50 is located at the lower side of the evaporator 60. At this time, the inlet 61c formed in the upper portion of the evaporator 60 is connected to the discharge pipe 54 of the ejector 50. The first outlet 61d formed at the lower portion of the first evaporation portion 61 is connected to the compressor 10 via the expansion valve 40, and the second outlet 62c is formed at the lower portion of the second evaporation portion 62. ) Is connected to the suction unit 55 of the ejector 50.

In addition, a communication hole 64 communicating with the first evaporator 61 and the second evaporator 62 is formed in the evaporator 60, and is introduced into the evaporator 60 from the ejector 50. The refrigerant is divided through the communication hole 64 to be supplied to the first evaporator 61 and the second evaporator 62, respectively.

The communication hole 64 is formed through the partition wall 63 partitioning the upper tank 61a of the first evaporator 61 and the upper tank 61a of the second evaporator 62.

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.

Therefore, the refrigerant discharged through the discharge pipe 54 of the ejector 50 flows into the inlet 61c formed between the upper tanks 61a and 62a of the first and second evaporation parts 61 and 62. In this case, the introduced refrigerant is divided through the communication hole 64, and part of the refrigerant is evaporated while flowing inside the first evaporator 61, and the other is evaporated while flowing inside the second evaporator 62. .

The refrigerant evaporated from the first evaporator 61 is discharged through the first outlet 61d formed in the lower portion and flows to the compressor 10 via the expansion valve 40, and the second evaporator 62 The refrigerant evaporated at is discharged through the second outlet 62c formed at the lower portion thereof, and is then sucked into the suction unit 55 by the suction pressure due to the coanda effect of the ejector 50.

The reason why the refrigerant discharged through the first outlet 61d of the first evaporator 61 passes through the expansion valve 40 depends on the temperature of the refrigerant flowing from the evaporator 60 to the compressor 10. This is to adjust the amount of refrigerant flowing from the condenser 20 to the evaporator 60 side.

7 is a configuration in which the mounting space of the ejector 50 and the length of the connection pipe are further minimized, and only a different part from FIG. 5 will be described. The discharge pipe 54 of the ejector 50 is the evaporator 60. It is a configuration installed directly inserted into the inlet (61c) side of.

Due to this, the upper tank 61a of the first evaporator 61 and the upper tank 62a of the second evaporator 62 are partitioned by the discharge pipe 54, in which the discharge pipe 54 The communication between the first evaporation part 61 and the second evaporation part 62 communicates through the communication hole 64 so that the discharged refrigerant is divided into the first evaporation part 61 and the second evaporation part 62. do.

The discharge pipe 54 serves as a partition wall between the upper tank 61a of the first evaporator 61 and the upper tank 62a of the second evaporator 62.

In addition, the communication hole 64 is formed on the opposite side of the side on which the ejector 50 is installed, that is, the communication hole 64 is formed on the end side of the discharge pipe 54 so that the first evaporation part 61 is formed. The upper tank (61a) and the upper tank (62a) of the second evaporation portion 62 of the communication.

Meanwhile, in FIG. 7, since the ejector 50 is directly mounted on the upper portion of the evaporator 60, the first and second outlets 61d and 62c disposed below the evaporator 60 are located on the side where the ejector 50 is mounted. It is preferable to arrange.

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 refrigerant direction is changed along the curved portion 52c formed on the side to be discharged through the discharge pipe 54. In this process, suction flow (suction pressure) is generated in the opposite direction of the discharge pipe 54. The refrigerant discharged from the second evaporator 62 is sucked through the unit 55.

Subsequently, the refrigerant discharged from the discharge pipe 54 of the ejector 50 is divided through the communication hole 64 formed inside the upper side of the evaporator 60, and a part of the refrigerant is discharged from the inside of the first evaporator 61. While evaporating through the heat exchange with the outside air, the rest is evaporated through the heat exchange with the outside air while flowing inside the second evaporator (62).

After being evaporated from the first evaporator 61, the refrigerant discharged through the first outlet 61d formed at the lower portion of the refrigerant flows to the internal heat exchanger 30 via the expansion valve 40. The internal heat exchanger 30 The refrigerant flowed into the heat exchanger with the refrigerant flowing from the condenser 20 to the expansion valve 40 is introduced into the compressor 10.

After being evaporated from the second evaporator 62, the refrigerant discharged through the second outlet 62c formed at the lower portion is sucked into the suction unit 55 by the suction pressure due to the coanda effect of the ejector 50. do.

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,

FIG. 5 is a schematic perspective view illustrating a connection state of an evaporator and an ejector in FIG. 4;

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

FIG. 7 is a schematic perspective view illustrating a state in which the ejector is mounted in the evaporator in FIG. 6;

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

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

10 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 evaporation unit 61a, 62a: upper tank

61b, 62b: lower tank 61c: inlet

61d: exit 1 62: second evaporator

62c: exit 2

63: partition wall 64: communication hole

Claims (11)

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 using the suction pressure generated during the passage of the refrigerant throttling in the expansion valve 40 passes through the inside, The first evaporator 61 and the second evaporator 62 are provided to divide the refrigerant discharged from the ejector 50 to evaporate the divided refrigerant, respectively, and the evaporated from the first evaporator 61. The first outlet 61d for discharging the refrigerant to the compressor 10 side and the second outlet 62c for discharging the refrigerant evaporated from the second evaporator 62 to the suction part 55 side of the ejector 50 are provided. Refrigeration cycle of a vehicle air conditioner, characterized in that consisting of the evaporator (60) disposed below. The method of claim 1, The inlet (61c) of the evaporator (60) for introducing the refrigerant discharged from the ejector (50) is a refrigeration cycle of a vehicle air conditioner, characterized in that disposed above. The method of claim 1, A communication hole 64 communicating with the first evaporator 61 and the second evaporator 62 is formed in the evaporator 60 to store the refrigerant introduced into the evaporator 60 from the ejector 50. The refrigeration cycle of a vehicle air conditioner, characterized in that the split through the communication hole (64) to be supplied to the first evaporator (61) and the second evaporator (62), respectively. The method of claim 3, wherein 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 is a refrigeration cycle of a vehicle air conditioner, characterized in that the Coanda effect (Coanda effect) is applied to the refrigerant passing through the inside. The method of claim 5, 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 6, 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) characterized in that the refrigeration cycle of the vehicle air conditioner. The method of claim 6, 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 6, 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 6, 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. The method of claim 6, The discharge pipe 54 of the ejector 50 is inserted into the inlet 61c side of the evaporator 60 to partition the first evaporator 61 and the second evaporator 62, but the discharge pipe The first evaporator 61 and the second evaporator 62 are supplied to the side 54 so that the refrigerant discharged from the discharge pipe 54 is divided into the first evaporator 61 and the second evaporator 62. Refrigeration cycle of a vehicle air conditioner, characterized in that the communication hole 64 is formed to communicate.

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