JP3265649B2 - Refrigeration cycle - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration cycle used in a home air conditioner, a vehicle air conditioner, and the like.

[0002]

2. Description of the Related Art Conventionally, as shown in FIG. 10, for example, a refrigerant compressor 101, a refrigerant condenser 102, an ejector 103, a first refrigerant evaporator 104 and a gas-liquid separator 105.
Are connected annularly by a refrigerant pipe 106, and the liquid-phase refrigerant separated from the gas-phase refrigerant by the gas-liquid separator 105 is provided with a decompression device 107 and a bypass pipe 1 provided with a second refrigerant evaporator 108.
There has been proposed a refrigeration cycle 100 in which the suction portion of the ejector 103 is sucked through the suction port 09. Such a configuration of the refrigeration cycle 100, by the suction pressure of the refrigerant compressor 101 is not adversely, and to improve the cooling capacity of the first refrigerant evaporator 104.

[0003]

However, when the above-described refrigeration cycle 100 is mounted on a vehicle, there are restrictions on mounting the refrigeration cycle 100.
The mounting position of each functional component constituting 0 is changed. Therefore, the connection of the pipe 110 between the ejector 103 and the first refrigerant evaporator 104, the connection between the first refrigerant evaporator 104 and the gas-liquid separator 1
05, the connection of the pipe 112 between the gas-liquid separator 105 and the second refrigerant evaporator 108, and the connection of the pipe 113 between the second refrigerant evaporator 108 and the suction part of the ejector 103 are complicated. There was a problem of getting it. In addition, the ejector 103, the first refrigerant evaporator 104, the gas-liquid separator 1
05, the pressure loss of the pipes 110 to 113 changes due to a change in the resistance of any of the pipes 110 to 113 due to a difference in the mutual position of the second refrigerant evaporator 108 when the vehicle is mounted. As a result, the suction pressure of the refrigerant compressor 101 also fluctuates, so that there is a problem that the cooling capacity of the first and second refrigerant evaporators 104 and 108 fluctuates.

[0004] The present invention provides a refrigeration cycle which can simplify connection between functional parts such as an ejector, a gas-liquid separator, and a refrigerant evaporator, and can always obtain a stable air-conditioning ability when mounted on any vehicle. For the purpose of providing.

[0005]

SUMMARY OF THE INVENTION The present invention provides a refrigerant compressor,
A refrigeration cycle in which a refrigerant condenser, an ejector, and a gas-liquid separator are circularly connected by a refrigerant pipe, and a liquid-phase refrigerant side of the gas-liquid separator and a suction part of the ejector are connected by a bypass pipe provided with a refrigerant evaporator. In the above, technical means in which the refrigerant evaporator, the gas-liquid separator and the ejector are integrated is adopted.

[0006]

According to the present invention, the integration of the gas-liquid separator and the ejector with the refrigerant evaporator simplifies the connection between the functional components of the refrigeration cycle and the resistance between the ejector and the gas-liquid separator. In addition, the resistance of the bypass pipe is constant even when the type of the mounted vehicle is different. As a result, the length of the passage between the ejector and the gas-liquid separator and the length of the bypass pipe are shorter than when the ejector, the refrigerant evaporator, and the gas-liquid separator are independently installed in the vehicle. In addition, fluctuations in pressure loss can be suppressed.

[0007]

Next, a refrigerating cycle according to the present invention will be described with reference to a plurality of embodiments shown in FIGS. FIG. 1 to FIG. 5 show a first embodiment of the present invention, and FIG. 1 shows a refrigeration cycle used in an air conditioner for a vehicle. The refrigeration cycle 1 includes a refrigerant compressor 2, a refrigerant condenser 3, an ejector 4, a first refrigerant evaporator 13 of an indoor heat exchanger 5, and a gas-liquid separator 6
Are sequentially connected in a ring shape by a refrigerant pipe 7,
The liquid-phase refrigerant side of the gas-liquid separator 6 and the suction part 8 of the ejector 4 are connected by a bypass pipe 9 provided with the second refrigerant evaporator 14 of the indoor heat exchanger 5. The refrigerant compressor 2 is rotationally driven by a driving device such as an engine or an electric motor mounted in an engine room of an automobile, compresses a gas-phase refrigerant sucked inside, and converts a high-temperature and high-pressure gas-phase refrigerant into a refrigerant condenser. Discharge to the 3 side.

[0008] The refrigerant condenser 3 is installed in an engine room of an automobile at a place where the traveling wind is easily received, and is connected to the discharge side of the refrigerant compressor 2. Refrigerant condenser 3 of this embodiment
Heat exchanges gas-phase refrigerant flowing into the inside from the refrigerant compressor 2 with outdoor air sent by an electric fan (not shown) or the like, thereby condensing and liquefying the gas-phase refrigerant.
The ejector 4 is, as shown in FIG.
It is attached to the side of. The ejector 4 sucks the gas-phase refrigerant from the suction part 8 by ejecting the liquid-phase refrigerant condensed and liquefied in the refrigerant condenser 3 from the nozzle 10 as shown in FIG. After the phase refrigerant and the gas-phase refrigerant are mixed and pressurized, the refrigerant in a gas-liquid two-phase state is sent to a first refrigerant evaporator 13 via a distributor 12 described later.

The indoor heat exchanger 5 is disposed in a duct (not shown) for sending conditioned air into the cabin of the automobile. As shown in FIG. 2, the indoor heat exchanger 5 connects the ejector 4, the gas-liquid separator 6, and the distributor 12 to each other. Become one. As shown in FIG. 2, the indoor heat exchanger 5 of this embodiment is provided with a first refrigerant evaporator 13 provided between the distributor 12 and the gas-liquid separator 6, and provided in the middle of the bypass pipe 9. And the second refrigerant evaporator 14. As shown in FIG. 3, the distributor 12 is a pipe that evenly distributes the gas-liquid two-phase refrigerant flowing out of the ejector 4 to each of the plurality of tubes of the first refrigerant evaporator 13.

As shown in FIG. 2, the first refrigerant evaporator 13 includes a plurality of plate-like fins 15 common to the second refrigerant evaporator 14.
It is composed of a plurality of tubes penetrating through. The first refrigerant evaporator 13 of this embodiment heats the refrigerant in a gas-liquid two-phase state flowing from the ejector 4 via the distributor 12 and indoor air or outdoor air sent by an electric fan (not shown). The refrigerant is exchanged to evaporate the refrigerant. As shown in FIG. 2, the second refrigerant evaporator 14 includes a plurality of tubes penetrating the plurality of plate-like fins 15 and an outlet header 16 connected to outlets of the plurality of tubes. The second refrigerant evaporator 14 of this embodiment includes:
The liquid-phase refrigerant flowing from the lower part of the gas-liquid separator 6 exchanges heat with the indoor air or the outdoor air sent by the electric fan to evaporate the refrigerant.

The gas-liquid separator 6 also serves as an outlet header of the first refrigerant evaporator 13 and an inlet header of the second refrigerant evaporator 14, as shown in FIG. The refrigerant is separated into a refrigerant and a liquid-phase refrigerant. An inlet of the gas-liquid separator 6 is connected to a plurality of tubes of the first refrigerant evaporator 13 via a pipe 17, and an outlet on an upper side (gas phase refrigerant side) is connected via a pipe 18 to a refrigerant compressor. 2 is connected to the suction side, and the outlet on the bottom side (liquid phase refrigerant side)
Is connected to a plurality of tubes of the second refrigerant evaporator 14 via the. The bypass pipe 9 is connected to a pipe 19 connecting an outlet on the bottom side of the gas-liquid separator 6 and inlets of a plurality of tubes of the second refrigerant evaporator 14, and an outlet header 16 of the second refrigerant evaporator 14. And a pipe 20 for connecting the suction part 8 of the ejector 4.

Next, the operation of the refrigeration cycle 1 will be briefly described with reference to FIGS. 1 to 5. Here, FIG. 4 shows the state points of the refrigerant in the refrigerant circuit of the refrigeration cycle 1 in FIG. 1 on a Mollier diagram, and the states of the refrigerants a to f on the refrigerant circuit of the refrigeration cycle 1 in FIG. A to on the Mollier diagram of FIG.
corresponds to f. The high-temperature and high-pressure gas-phase refrigerant compressed by the refrigerant compressor 2 (state point b) is condensed and liquefied by the refrigerant condenser 3 to become a high-temperature and high-pressure liquid-phase refrigerant (state point c). After that, it flows into the ejector 4. The liquid-phase refrigerant that has flowed into the ejector 4 is decompressed when passing through the nozzle 10 and reaches a state point d1 , and is further pressurized when passing through the diffuser 11 to reach a state point d.

At this time, by utilizing the pressure drop around the refrigerant ejected at high speed from the nozzle 10 when the liquid-phase refrigerant passes through the nozzle 10, the suction point 8 of the ejector 4 is connected to the suction pipe 8 at the state point d 2 from the bypass pipe 9. The phase refrigerant is sucked. For this reason,
The liquid-phase refrigerant flowing from the refrigerant condenser 3 and the gas-phase refrigerant sucked from the pipe 20 are mixed in the diffuser 11. Thereby, the refrigerant in the gas-liquid two-phase state flowing out of the ejector 4 is changed to the state points d1, d2 and the state point d determined by the refrigerant circulation amount from the refrigerant condenser 3 and the refrigerant circulation amount from the second refrigerant evaporator 14. Becomes

The gas-liquid two-phase refrigerant flowing into the plurality of tubes of the first refrigerant evaporator 13 via the distributor 12 is evaporated and vaporized (state point e), and then the gas-liquid separator 6 And separated into a gas-phase refrigerant and a liquid-phase refrigerant. Thereafter, the gas-phase refrigerant (state point a) in the gas-liquid separator 6 is sucked into the refrigerant compressor 2 through the pipe 18 by the suction force of the refrigerant compressor 2. Further, the liquid-phase refrigerant at the state point f stored in the bottom of the gas-liquid separator 6 passes through the pipe 19 due to the suction effect of the ejector 4 and passes through the second refrigerant evaporator 1.
It is sucked into 4. The liquid-phase refrigerant flowing into the plurality of tubes of the second refrigerant evaporator 14 is evaporated and vaporized (state point
d2 ) Later, the suction unit 8 of the ejector 4 passes through the pipe 20.
Is sucked.

[Effects of the First Embodiment] As described above, the refrigeration cycle 1 of this embodiment causes the liquid-phase refrigerant condensed and liquefied by the refrigerant condenser 3 to be ejected from the nozzle 10, and the second refrigerant evaporator to be used. The vapor-phase refrigerant evaporated and vaporized at 14 is sucked into the suction unit 8 of the ejector 4. Thereby, when viewed from the air side, since the pressure temperature of the second refrigerant evaporator 14 can be lowered by one step at the same suction pressure of the refrigerant compressor 2, heat exchange can be performed at a lower temperature than a normal refrigerant evaporator. it can. Distributor 12, piping 1
By unifying 7, 18, 20 these machines
When the vessels are not integrated (shown by broken lines in FIG. 4; d1 ', d
2 Distributing rather than 'd → e' → a ', f1)
Pressure loss ΔPA in the motor 12, the pipes 17, 19, and 20
ΔPD can be reduced. Therefore, when viewed from the refrigerant side, if the pressure temperature of the second refrigerant evaporator 14 is the same as normal, the suction pressure of the refrigerant compressor 2 can be increased, and the refrigerant circulation amount can be increased due to the suction density. Cooling capacity can be increased. For this reason, as shown in FIG. 5, the cooling capacity in the interior of the vehicle with respect to the rotation speed of the refrigerant compressor 2 can be improved as compared with the cooling capacity before the integration.

Further, by integrating the ejector 4, the gas-liquid separator 6, and the distributor 12 into the indoor heat exchanger 5, even if the type of the vehicle on which the refrigeration cycle 1 is mounted is different, the distributor 12, the pipe 17 , 19, and 20 can always be kept constant. Therefore, the fluctuation of the suction pressure of the refrigerant compressor 2 is reduced.
The first and second refrigerant evaporators 13 and 1
4 can reduce the fluctuation of the cooling capacity.

[0017] In addition, the distributor 12, the pipe 1
By integrating 7 , 18, and 20 , the passage length is reduced.
In this way, as shown in FIG.
The viewer 12, the pipes 17, 18, and 20 are integrated to form a passage.
By reducing the length, the refrigeration cycle 1 can be reduced in size by shortening and eliminating the piping between the functional components.

[Second Embodiment] FIGS. 6 to 8 show a second embodiment of the present invention, and FIG. 6 is a view showing a single tank type laminated indoor heat exchanger. In this embodiment, a single-tank type indoor heat exchanger 30 in which a plurality of corrugated fins 31 and a pair of thin plate-shaped forming plates 32 are stacked by means such as brazing is used.
The forming plate 32 is formed by pressing a thin plate-shaped aluminum alloy. On the outer peripheral edge of this forming plate, the other opposing forming plate 32
Wall 3 joined to the outer peripheral edge of the member by brazing or the like
3 are formed. A partition wall 34 is formed at the center of the forming plate 32 and joined to the center of the other forming plate 32 by brazing or the like.

Around the partition wall 34, a substantially U-shaped refrigerant evaporation passage 35 for exchanging heat between the refrigerant and air to evaporate the refrigerant is formed in a shallow dish shape. The refrigerant evaporating passage 35 is formed with a large number of ribs 36 for allowing the refrigerant to spread widely throughout the width direction so as to protrude toward the other forming plate 32 facing the other. Note that, by stacking a plurality of paired forming plates 32, that is, by stacking a plurality of refrigerant evaporating passages 35, as shown in FIGS. A plurality of refrigerant evaporation passages 3
5 is formed, and a second refrigerant evaporator 38 having a plurality of refrigerant evaporation passages 35 is formed on the right side of the stacked indoor heat exchanger 30 in the drawing.

Further, tank portions 39 and 40 are formed on the upper portion of the forming plate 32, respectively. The tank portions 39 and 40 communicate with each other via the refrigerant evaporation passage 35, and are formed in a substantially bowl shape so as to be joined to upper portions of a pair of adjacent forming plates 32 by means such as brazing. I have. In addition, the tank units 39 and 40 include:
Circular communication holes 39a and 40a for communicating with a pair of adjacent molding plates 32 are formed respectively. Note that, by stacking a plurality of the pair of forming plates 32, that is, by stacking a plurality of the tank portions 39 and 40, as shown in FIG. 41 and an intermediate tank 42 are formed, and an intermediate tank 43 and an outlet tank 44 are formed above the second refrigerant evaporator 38.

The inlet tank 41 is provided with a gas-liquid two-phase refrigerant flowing through an inlet hole 46 from an inlet pipe 45 connected to the diffuser 11 of the ejector 4.
Are distributed to the plurality of refrigerant evaporation passages 35. The intermediate tank 42 is a passage that collects the vaporized refrigerant vaporized and vaporized when passing through the plurality of refrigerant evaporation passages 35 of the first refrigerant evaporator 37 and guides the collected refrigerant to the intermediate tank 43. Intermediate tank 43
Is a passage for dispersing the refrigerant flowing from the intermediate tank 42 into the plurality of refrigerant evaporation passages 35 of the second refrigerant evaporator 38. The plurality of refrigerant evaporation passages 3 of the second refrigerant evaporator 38
5 also functions as a gas-liquid separator 6, so that a gas-phase refrigerant accumulates at the top of the pair of forming plates 32 and a liquid-phase refrigerant (shown by oblique lines in FIG. 8) accumulates at the bottom. Therefore, the intermediate tank 43
The pipe 18 for returning the gaseous-phase refrigerant to the refrigerant compressor 2 is connected to the communication hole of the tank portion 39 of a part of the forming plate 32 by brazing or the like.

The outlet tank 44 collects the vapor-phase refrigerant vaporized when passing through the plurality of refrigerant evaporating passages 35 of the second refrigerant evaporator 38, and flows through the outlet hole 47 to the suction portion 8 of the ejector 4. The gas-phase refrigerant flows out into the communicating bypass pipe 9. The first refrigerant evaporator 37 and the second refrigerant evaporator 38 communicate with each other via the intermediate tanks 42 and 43, but the inlet tank 41 and the outlet tank 44 are separated from each other by a partition 48.
Is divided by

Third Embodiment FIG. 9 shows a refrigeration cycle according to a third embodiment of the present invention. In this embodiment, the first refrigerant evaporator 13 is eliminated, and only the second refrigerant evaporator 14 is provided in the refrigeration cycle 1.
In this case, the ejector 4 and the gas-liquid separator 6 are connected to the pipe 4
9 only.

[Modification] In the present embodiment, the present invention is applied to an air conditioner for a vehicle. However, the present invention may be applied to an air conditioner for home use. In this embodiment, the gas-liquid separator 6 and the second refrigerant evaporator 14 are connected directly by the pipe 19, but a decompression device is connected between the gas-liquid separator 6 and the second refrigerant evaporator 14. May be.

[0025]

According to the present invention, the connection between each functional component such as an ejector, a gas-liquid separator, and a refrigerant evaporator can be simplified, and even when a refrigeration cycle is mounted on a vehicle subject to mounting restrictions, the present invention is always stable. The improved air-conditioning capacity can be obtained.

[Brief description of the drawings]

FIG. 1 is a configuration diagram showing a refrigeration cycle according to a first embodiment of the present invention.

FIG. 2 is a perspective view showing the indoor heat exchanger according to the first embodiment of the present invention.

FIGS. 3A and 3B are sectional views showing an ejector and a distributor according to the first embodiment of the present invention.

FIG. 4 is a Mollier diagram of the refrigeration cycle according to the first embodiment of the present invention.

FIG. 5 is a graph showing a relationship between a cooling capacity ratio and a rotation speed of a refrigerant compressor according to the first embodiment of the present invention.

FIG. 6 is a perspective view showing a single-tank stacked indoor heat exchanger according to a second embodiment of the present invention.

FIG. 7 is a configuration diagram showing a schematic structure of a single-tank stacked indoor heat exchanger according to a second embodiment of the present invention.

FIG. 8 is a configuration diagram showing a schematic structure of a single-tank stacked indoor heat exchanger according to a second embodiment of the present invention.

FIG. 9 is a configuration diagram illustrating a refrigeration cycle according to a third embodiment of the present invention.

FIG. 10 is a configuration diagram showing a conventional refrigeration cycle.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Refrigeration cycle 2 Refrigerant compressor 3 Refrigerant condenser 4 Ejector 5 Indoor heat exchanger 6 Gas-liquid separator 7 Refrigerant piping 8 Suction part 9 Bypass piping 13 First refrigerant evaporator 14 Second refrigerant evaporator

Claims (1)

(57) [Claims] 1. A refrigerant compressor, a refrigerant condenser, an ejector, and a gas-liquid separator are connected in a ring by a refrigerant pipe, and a refrigerant evaporator is connected between a liquid-phase refrigerant side of the gas-liquid separator and a suction part of the ejector. A refrigeration cycle connected by an arranged bypass pipe, wherein the refrigerant evaporator, the gas-liquid separator, and the ejector are integrated.