JPH06137695A - Refrigerating cycle - Google Patents

Abstract

PURPOSE:To make it possible to simplify mutual connections of functional components of a refrigerating cycle such as an ejector, a first refrigerant evaporator, a vapor-liquid separator, a second refrigerant evaporator, etc., and to obtain a cooling capacity being stable at all times when the refrigerating cycle is mounted on a vehicle of any kind. CONSTITUTION:A refrigerant compressor, a refrigerant condenser, an ejector 4, a first refrigerant evaporator 13 and a vapor-liquid separator 6 are connected in a loop sequentially by a refrigerant piping and the bottom part of the vapor- liquid separator 6 and a suction part of the ejector 4 are connected by a bypass piping 9 provided with a second refrigerant evaporator 14. The ejector 4, a distributor 12 and the vapor-liquid separator 6 are fitted integrally to the first and second refrigerant evaporators 13 and 14 and thereby passage lengths of the distributor 12 and pipings 17, 19 and 20 connecting the functional components of a refrigerating cycle mutually are shortened.

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art Conventionally, for example, as shown in FIG. 10, a refrigerant compressor 101, a refrigerant condenser 102, an ejector 103, a first refrigerant evaporator 104 and a gas-liquid separator 105.
Is connected in an annular shape 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 second refrigerant evaporator 108.
A refrigeration cycle 100 has been proposed in which the suction section of the ejector 103 is caused to suck the gas through the 09. The refrigerating cycle 100 having such a configuration reduces the refrigerant evaporation pressure of the first refrigerant evaporator 104 that functions as a refrigerant evaporator during the cooling operation to prevent the suction pressure of the refrigerant compressor 101 from decreasing. The cooling capacity of the refrigerant evaporator 104 is improved.

[0003]

However, when the above refrigeration cycle 100 is mounted on a vehicle, it is subject to restrictions on mounting, so that the refrigeration cycle 10 can be changed depending on the vehicle type.
The mounting position of each functional component forming 0 is changed. Therefore, the ejector 103 and the first refrigerant evaporator 104 are connected to the pipe 110, and the first refrigerant evaporator 104 and the gas-liquid separator 1 are connected.
The connection of the pipe 111 with 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 become complicated. There was a problem of being lost. Further, the ejector 103, the first refrigerant evaporator 104, the gas-liquid separator 1
05, the resistance of one of the pipes 110 to 113 changes due to the difference in the mutual positions of the second refrigerant evaporator 108 when the vehicle is mounted, and thus the pressure loss of the pipes 110 to 113 changes. As a result, the suction pressure of the refrigerant compressor 101 also fluctuates, which causes a problem that the cooling capacity of the first and second refrigerant evaporators 104 and 108 also fluctuates.

According to the present invention, the connection of functional parts such as an ejector, a gas-liquid separator, a refrigerant evaporator and the like can be simplified, and a stable air conditioning capacity can always be obtained no matter what type of vehicle the refrigeration cycle is equipped with. For the purpose of provision.

[0005]

The present invention is directed to a refrigerant compressor,
A refrigeration cycle in which a refrigerant condenser, an ejector, and a gas-liquid separator are annularly connected by a refrigerant pipe, and a liquid-phase refrigerant side of the gas-liquid separator and a suction portion of the ejector are connected by a bypass pipe in which a refrigerant evaporator is arranged. In the above, the technical means in which the refrigerant evaporator, the gas-liquid separator and the ejector are integrated is adopted.

[0006]

According to the present invention, by integrating the gas-liquid separator and the ejector in the refrigerant evaporator, the functional parts of the refrigeration cycle can be easily connected to each other and the resistance between the ejector and the gas-liquid separator can be improved. The resistance of the bypass pipe is constant even when the type of vehicle is different. As a result, the passage length between the ejector and the gas-liquid separator and the passage length of the bypass pipe are shortened compared to the case where the ejector, the refrigerant evaporator, and the gas-liquid separator are independently installed in the vehicle. The fluctuation of pressure loss can be suppressed.

[0007]

EXAMPLES Next, the refrigerating cycle of the present invention will be explained based on a plurality of examples shown in FIGS. [Structure of First Embodiment] FIGS. 1 to 5 show a first embodiment of the present invention, and FIG. 1 is a view showing a refrigeration cycle used in an air conditioner for an automobile. 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 an annular shape by the refrigerant pipe 7,
The liquid-phase refrigerant side of the gas-liquid separator 6 and the suction section 8 of the ejector 4 are connected by a bypass pipe 9 in which the second refrigerant evaporator 14 of the indoor heat exchanger 5 is arranged. The refrigerant compressor 2 is rotatably driven by a driving device such as an engine or an electric motor mounted in an engine room of an automobile, compresses the gas-phase refrigerant sucked therein, and converts the high-temperature and high-pressure gas-phase refrigerant into a refrigerant condenser. Discharge to the 3 side.

The refrigerant condenser 3 is installed in the engine room of an automobile at a place where it is likely to receive traveling wind, and is connected to the discharge side of the refrigerant compressor 2. Refrigerant condenser 3 of this embodiment
Heat-exchanges the vapor-phase refrigerant flowing in from the refrigerant compressor 2 with the outdoor air sent by an electric fan (not shown) or the like to condense and liquefy the vapor-phase refrigerant.
As shown in FIG. 2, the ejector 4 includes an indoor heat exchanger 5
It is attached to the side of. As shown in FIG. 3, the ejector 4 ejects the liquid-phase refrigerant condensed and liquefied in the refrigerant condenser 3 from the nozzle 10, thereby sucking the gas-phase refrigerant from the suction portion 8 and liquid in the diffuser 11. After the phase refrigerant and the gas phase refrigerant are mixed and the pressure is increased, the refrigerant in the gas-liquid two-phase state is sent to the first refrigerant evaporator 13 via the distributor 12 described later.

The indoor heat exchanger 5 is arranged in a duct (not shown) for sending conditioned air into the passenger compartment of the automobile, and as shown in FIG. 2, the ejector 4, the gas-liquid separator 6 and the distributor 12 are connected to each other. It becomes one. The indoor heat exchanger 5 of this embodiment is provided in the middle of the bypass pipe 9 and the first refrigerant evaporator 13 provided between the distributor 12 and the gas-liquid separator 6, as shown in FIG. The second refrigerant evaporator 14 is divided inside. 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 has a plurality of plate-like fins 15 common to the second refrigerant evaporator 14.
It is composed of multiple tubes that penetrate through. The first refrigerant evaporator 13 of this embodiment heats the refrigerant in the gas-liquid two-phase state that has flowed in from the ejector 4 via the distributor 12 and the indoor air or the outdoor air sent by an electric fan (not shown). The refrigerant is exchanged and the refrigerant is vaporized. As shown in FIG. 2, the second refrigerant evaporator 14 is composed of a plurality of tubes penetrating the plurality of plate-shaped fins 15 and an outlet-side header 16 connected to the outlet side of the plurality of tubes. The second refrigerant evaporator 14 of this embodiment is
The liquid-phase refrigerant flowing from the lower part of the gas-liquid separator 6 and the indoor air or the outdoor air sent by the electric fan are heat-exchanged to evaporate the refrigerant.

As shown in FIG. 2, the gas-liquid separator 6 also serves as an outlet-side header of the first refrigerant evaporator 13 and an inlet-side header of the second refrigerant evaporator 14, and the inflowing refrigerant is vapor-phased. It separates into a refrigerant and a liquid-phase refrigerant. The inlet part of the gas-liquid separator 6 is connected to a plurality of tubes of the first refrigerant evaporator 13 via a pipe 17, and the outlet part on the 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) has a bypass pipe 9
Is connected to a plurality of tubes of the second refrigerant evaporator 14 via. The bypass pipe 9 connects the bottom outlet of the gas-liquid separator 6 with the inlets of the plurality of tubes of the second refrigerant evaporator 14, and the outlet header 16 of the second refrigerant evaporator 14. And a pipe 20 connecting the suction unit 8 of the ejector 4 to each other.

[Operation of First Embodiment] Next, the operation of the refrigeration cycle 1 will be briefly described with reference to FIGS. 1 to 5. Here, FIG. 4 is a diagram in which the state of the refrigerant of the refrigerant circuit of the refrigeration cycle 1 in FIG. 1 is drawn on the Mollier diagram, and the states of the refrigerant of a to f on the refrigerant circuit of the refrigeration cycle 1 of FIG. It corresponds to a to f on the Mollier diagram of FIG. The gas-phase refrigerant (state point b) that is compressed by the refrigerant compressor 2 and becomes high temperature and high pressure 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, the ejector 4
Flows in. The liquid-phase refrigerant flowing into the ejector 4 is
When passing through the nozzle 10, the pressure is reduced to reach the state point d2, and when passing through the diffuser 11, the pressure is raised to reach the state point d2.

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

The refrigerant in the gas-liquid two-phase state that has flowed 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 It flows in and separates into a vapor phase refrigerant and a liquid phase refrigerant. After that, 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 accumulated at the bottom of the gas-liquid separator 6 passes through the pipe 19 by the suction effect of the ejector 4, and the second refrigerant evaporator 1
4 is sucked. The liquid-phase refrigerant that has flowed into the plurality of tubes of the second refrigerant evaporator 14 is evaporated and vaporized (state point d1), and then passes through the pipe 20 to draw in the suction portion 8 of the ejector 4.
Is sucked into.

[Effects of the First Embodiment] As described above, in the refrigeration cycle 1 of this embodiment, the liquid-phase refrigerant condensed and liquefied in the refrigerant condenser 3 is ejected from the nozzle 10 to generate the second refrigerant evaporator. The vapor-phase refrigerant evaporated and vaporized in 14 is sucked into the suction portion 8 of the ejector 4. As a result, when viewed from the air side, the second refrigerant evaporator 14 has the same suction pressure of the refrigerant compressor 2.
Since the pressure temperature of can be lowered by one step, heat exchange can be performed at a temperature lower than that of a normal refrigerant evaporator. Also,
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, so that the refrigerant circulation amount can be increased due to the suction density, thereby increasing the cooling capacity. Can be increased. Therefore, as shown in FIG. 5, it is possible to improve the cooling capacity in the passenger compartment of the automobile with respect to the rotation speed of the refrigerant compressor 2 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 automobile in which the refrigeration cycle 1 is mounted is different, the distributor 12 and the pipe 17 are provided. , 19 and 20 can always have a constant internal resistance. In addition, the distributor 12, the piping 17, 1
Since the passage lengths of 8 and 20 are shorter than before integration, as shown in FIG. 4, the pressure loss ΔPA to ΔPD in the distributor 12 and the pipes 17, 19 and 20 before integration (broken line in the drawing) d1. ', D2' → d → e '→ a', f
It can be reduced more than

With these, fluctuations in the suction pressure of the refrigerant compressor 2 can be reduced, so fluctuations in the cooling capacity of the first and second refrigerant evaporators 13 and 14 can be reduced. Further, the passage lengths of the distributor 12 and the pipes 17, 18, and 20 are shortened as compared with those before the integration, so that the pipes between the functional parts are shortened and eliminated, so that the refrigeration cycle 1
It is possible to realize the miniaturization of.

[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 laminated indoor heat exchanger 30 in which a plurality of corrugated fins 31 and a pair of thin plate-shaped forming plates 32 are laminated 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 to be joined to the outer peripheral edge of the body by means such as brazing
3 is formed. A partition wall 34 is formed at the central portion of the molding plate 32 so as to be joined to the central portion of the other molding plate 32 which faces the molding plate 32 by means such as brazing.

Around the partition wall 34, a substantially U-shaped refrigerant evaporation passage 35 for evaporating and evaporating the refrigerant by exchanging heat with the refrigerant is formed in a shallow dish shape. In the refrigerant evaporation passage 35, a large number of rib portions 36 for allowing the refrigerant to spread widely in the entire width direction are formed so as to protrude toward the other molding plate 32 side facing each other. As shown in FIGS. 7 and 8, by stacking a plurality of the pair of molding plates 32, that is, by stacking a plurality of the refrigerant evaporation passages 35, the left side of the stacked indoor heat exchanger 30 shown in the drawing. A plurality of refrigerant evaporation passages 3
5 is formed, and the second refrigerant evaporator 38 having a plurality of refrigerant evaporation passages 35 is formed on the right side of the laminated indoor heat exchanger 30 in the drawing.

Further, tank portions 39 and 40 are formed on the upper portion of the molding plate 32, respectively. The tank portions 39, 40 are in communication with each other through the refrigerant evaporation passages 35, and are formed in a substantially bowl shape so as to be joined to the upper portions of the pair of adjacent molding plates 32 by means such as brazing. There is. In addition, in the tank parts 39 and 40,
Circular communication holes 39a, 40a for communicating with a pair of adjacent molding plates 32 are formed, respectively. In addition, by stacking a plurality of the pair of molding plates 32, that is, by stacking a plurality of tank portions 39 and 40, as shown in FIG. 7, an inlet tank is provided at an upper portion of the first refrigerant evaporator 37. 41 and an intermediate tank 42 are formed, and an intermediate tank 43 and an outlet tank 44 are formed in an upper portion of the second refrigerant evaporator 38.

The inlet tank 41 has a first refrigerant evaporator 37 for the refrigerant in a gas-liquid two-phase state that has flowed in through an inlet hole 46 from an inlet pipe 45 connected to the diffuser 11 of the ejector 4.
Of the refrigerant evaporation passages 35. The intermediate tank 42 is a passage that collects the vaporized refrigerant that has been vaporized when passing through the plurality of refrigerant evaporation passages 35 of the first refrigerant evaporator 37 and guides it 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
Since 5 also functions as the gas-liquid separator 6, the vapor-phase refrigerant is accumulated in the upper part of the pair of molding plates 32, and the liquid-phase refrigerant (shown by the diagonal lines in FIG. 8) is accumulated in the bottom part. Therefore, the intermediate tank 43
A pipe 18 for returning the vapor-phase refrigerant to the refrigerant compressor 2 is connected to the communication hole of the tank portion 39 of a part of the molding plate 32 by means such as brazing.

The outlet tank 44 collects the vapor-phase refrigerant vaporized and vaporized when passing through the plurality of refrigerant evaporation passages 35 of the second refrigerant evaporator 38, and is introduced into the suction portion 8 of the ejector 4 through the outlet hole 47. The gas-phase refrigerant flows out into the bypass pipe 9 communicating with it. 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 the partition portion 48.
It is divided by.

[Third Embodiment] FIG. 9 shows a third embodiment of the present invention and is a view showing a refrigeration cycle. 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
Connected by 9 only.

[Modification] In the present embodiment, the present invention is applied to the vehicle air conditioner, but the present invention may be applied to a domestic air conditioner. In this embodiment, the gas-liquid separator 6 and the second refrigerant evaporator 14 are directly connected by the pipe 19, but a pressure reducing device is connected between the gas-liquid separator 6 and the second refrigerant evaporator 14. Good.

[0025]

The present invention can simplify the connection of functional parts such as an ejector, a gas-liquid separator, a refrigerant evaporator, etc., and is always stable even when a refrigeration cycle is mounted on a vehicle subject to mounting restrictions. It is possible to obtain the required air conditioning capacity.

[Brief description of 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 an indoor heat exchanger according to the first embodiment of the present invention.

3A and 3B are cross-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 the relationship between the cooling capacity ratio and the rotation speed of the refrigerant compressor according to the first embodiment of the present invention.

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

FIG. 9 is a configuration diagram showing 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 Codes] 1 Refrigeration cycle 2 Refrigerant compressor 3 Refrigerant condenser 4 Ejector 5 Indoor heat exchanger 6 Gas-liquid separator 7 Refrigerant pipe 8 Suction part 9 Bypass pipe 13 First refrigerant evaporator 14 Second refrigerant evaporator

Claims (1)

[Claims] 1. A refrigerant compressor, a refrigerant condenser, an ejector and a gas-liquid separator are annularly connected by a refrigerant pipe, and a liquid-phase refrigerant side of the gas-liquid separator and a suction portion of the ejector are connected to a refrigerant evaporator. A refrigeration cycle in which the refrigerant evaporator, the gas-liquid separator, and the ejector are integrated in a refrigeration cycle that is connected by an arranged bypass pipe.