JPS59153075A - Refrigeration cycle device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention provides heating and cooling systems using non-azeotropic mixed refrigerants.
'Relating to a cryocycle device that performs refrigeration.

Conventional Structure and Problems The structure shown in FIG. 1 has been proposed as a refrigeration cycle device using a non-azeotropic mixed refrigerant. In Figure 1,
1 is a compressor, 2 is a compressor, 3 and 4 are throttling devices, and 5 is an evaporator, which are successively connected by piping as shown in the figure, and the refrigerant is injected from an intermediate pressure between the throttling devices 3 and 4 through an injection circuit 6. A part of the compressor 1 is arranged to be placed inside the cylinder of the compressor 1. In such a configuration, the compressor 1
The discharge temperature can be lowered, and an increase in heating capacity can be expected. However, no increase in cooling capacity can be expected, and the fact that the high and low pressures are controlled by the heat source temperatures on the cooling side and the heating side is the same as in the case without the injection circuit 6. In other words, if the heating side is used to supply high-l crystal water and the temperature of the heat source on the cooling side drops extremely, or if the cooling side is used as an air conditioner and the heat source temperature on the heating side rises extremely, the compressor 1 Not only does the compression ratio of the engine increase, resulting in an excessive load, but it also becomes useless.

Purpose of the Invention The present invention eliminates the drawbacks of the conventional example described above, increases the capacity when using the heating side and the cooling side, and improves the compression ratio even when the difference in heat source temperature between the heating side and the cooling side increases. This is to suppress the increase as much as possible and enable stable operation.

Structure of the Invention The refrigeration cycle device of the present invention uses a non-azeotropic mixed refrigerant to reduce the pressure of a liquid refrigerant containing a large amount of high-boiling components separated during the condensation process to an intermediate pressure, and then compresses a part of the liquid refrigerant. The refrigerant is injected into the cylinder of the machine and contains more of the remaining high-boiling components and is further depressurized to a low pressure, and the other is the refrigerant that is separated in a gaseous state during the condensation process and contains more of the low-boiling components that are further condensed and depressurized. It is constructed so that the refrigerant is combined and guided to the evaporator.

DESCRIPTION OF THE EMBODIMENTS An embodiment of the refrigeration cycle apparatus according to the present invention is shown in FIG. In FIG. 2, 11 is a compressor, 12 is a first condenser, and 13 is a gas-liquid separator. When a non-azeotropic mixed refrigerant is used, the liquid refrigerant in the gas-liquid separator 13 has a higher boiling point. gas refrigerant will contain more low-boiling components. 14 is a second a-condensing type for condensing the gas refrigerant separated by the gas-liquid separator 13, 15 is a first throttle device, and 16 is an evaporator. Ushita 17 is a bypass pipe that guides the liquid refrigerant separated by the gas-liquid separator 13 to the evaporator 16, and second and third throttle devices 18 and 19 are installed in the middle of the pipe, and injection is carried out from the intermediate pressure. The circuit 20 is configured to inject a portion of the refrigerant into a cylinder (not shown) of the compressor 11.

The mode of operation of such a device will be explained with reference to FIG. Figure 3 is a temperature versus composition diagram of a non-azeotropic mixed refrigerant at constant high pressure, intermediate pressure, and low pressure.In the case of a non-azeotropic mixed refrigerant, it has a lens shape as shown in Figure 3, and the upper side is saturated gas. The line below is the saturated liquid line. Diagram J2 in FIG. 3 shows the pressure and temperature of each part of the apparatus shown in FIG. In FIG. 3, gas refrigerant a in a high pressure state at the outlet of the compressor 11 is partially condensed in the first compression type 12.
-- Once the refrigerant is in the state, it is separated into gas refrigerant C and liquid refrigerant d in the gas-liquid separator 13. The gas refrigerant C, which is rich in low boiling point components, is further condensed and liquefied to a supercooled state e by the second condenser 14, and then reduced in pressure to a low-pressure gas-liquid coexistence state 5 by the first expansion device 15.

On the other hand, the liquid refrigerant d rich in high-boiling components separated by the gas-liquid separator 13 is in a state q where the pressure is reduced to an intermediate pressure by the second throttle device 18, and a part of it is further transferred to the third throttle device 19.
The pressure is reduced to a low pressure, resulting in a state where gas and liquid coexist. Here, a part of the intermediate pressure refrigerant q is injected into the compressor 11, and since the mass of the refrigerant rich in high boiling point components in the state decreases, the states f and h of the evaporator 16 are mixed. In state 1, lower boiling point components are more abundant than in state a at the outlet of the compressor 1. The refrigerant 1 in a gas-liquid coexistence state is evaporated by the evaporator 16 to become a superheated gas state j, and is sucked into the compressor 11 and compressed to an intermediate pressure gas state at -i. Although the state inside the compressor 11 is not shown, the gas refrigerant in the state is mixed with the refrigerant q in the 6'-di-floating state, both gas and liquid, led from the injection circuit 20, and the temperature is reduced to the state l. It becomes a gas refrigerant and is further compressed to become an outlet refrigerant d of the -C compressor 11.

Here, since the refrigerant q in the gas-liquid coexistence state is injected into the cylinder of the compressor 1, the temperatures in the state 1 and the discharge state a are lowered, and the amount of refrigerant discharged from the compressor 1 is increased. Second condenser 12. The increase in heating capacity in i4 is almost the same as in the conventional example shown in FIG.

The feature of the present invention is that the refrigerant flowing through the evaporator 16
The refrigerant discharged from the compressor 11 is richer in low boiling point components than the refrigerant discharged from the compressor 11. That is, the temperature of the refrigerant flowing through the evaporator 16 is largely controlled by the temperature of the cooling side heat source, and when the heat source temperature is the same, the specific volume of the suction gas of the compressor 11 becomes smaller as the amount of low boiling point components increases. It becomes possible to circulate more refrigerant, and the cooling capacity of the evaporator 16 increases. The cooling capacity can be controlled by controlling the amount of refrigerant flowing through the injection circuit 20, and in the embodiment shown in FIG. This becomes possible by adjusting the resistance of 18 and 19 according to the cooling side load, and at the same time it becomes possible to control the heating capacity.

Note that the width of the fraction f111I is expected to be the largest when all of the liquid refrigerant separated by the gas-liquid separator 13 is injected into the compressor 11 after being decompressed by the second expansion device 18. The third aperture device 19 becomes unnecessary.

In FIG. 3, when the low pressure is constant, the temperature at the inlet and outlet state l+ of the evaporator 16 shifts to the lower temperature side as the low-boiling point components are richer, but conversely, the temperature at the state i+ shifts to the lower temperature side.

When the temperature is kept almost constant at j, the richer the low boiling point components are, the more the low pressure can be increased.

In other words, when the heating side is used to supply high-temperature water and the temperature of the heat source on the cooling side drops dramatically, or when the cooling side is used as an air conditioner and the heat source temperature on the heating side rises extremely,
In the device according to the present invention, the second and third throttle devices 18 and 19 are set to m to increase the amount of refrigerant flowing through the injection circuit 2o, and the first throttle device 15
By controlling the opening of the evaporator so that the low pressure increases, the composition filled in the device remains constant, so more low boiling point components stay on the evaporator 16 side, and the low boiling point components stay on the first condenser 12 side. In this case, more high-boiling components will remain. That is, in the heat source temperature state at that time, the low pressure increases and the high pressure decreases, making it possible to reduce the compression ratio and reduce the load on the compressor 11.

In the embodiment shown in FIG. 2, the injection circuit 2o is led from between the second and third throttle devices 18, 19, but what is necessary is to control the pressure of the injection circuit 20 between high pressure and low pressure. Set it to an intermediate pressure. Therefore, another throttle device (not shown) or a flow control valve (not shown) may be provided in the injection circuit 20, or
The present invention also includes a configuration in which another gas-liquid separator (not shown) is provided between the second and third throttling devices 18 and 19 to control the distribution of gas and liquid injected into the compressor 1. It is something that can be done. In addition, in the embodiment shown in FIG. 2, one compressor 11 is provided, and the compressor 11 is placed at a position where the pressure is intermediate within the cylinder.
Although the refrigerant is guided from the injection circuit 20,
Of course, it is possible to use a plurality of compressors (not shown), such as a low-stage compressor and a high-stage compressor, and to inject refrigerant between them, and the amount of refrigerant to be injected may vary. may be controlled to close if not necessary.

As another embodiment of the trench, FIG. 4 shows an example of its application as a heating and cooling device. In Fig. 4, compressor 21, four-way valve 2
2, heat source side exchangers 23, 24, load side heat exchanger 25,
26, gas-liquid separator 27, 28, throttle device 29, 30,
31, consists of an injection circuit 32, etc. During cooling, the heat source side heat exchangers 23 and 24 are a compression type, and the load side heat exchangers 25 and 26 function as evaporators, and during heating they function in the opposite way. . The difference between the embodiment shown in FIG. 4 and the embodiment shown in FIG. 2 is that the gist of the present invention is utilized when switching the four-way valve 22 to perform both cooling and heating functions.
Heat source side heat exchanger 23.24 and load side heat exchanger 25.2
6, separate gas/liquid separators 10', .

As described in detail, the refrigeration cycle device of the present invention separates the liquid refrigerant in the a-condensation process from the gas refrigerant in a refrigeration cycle using a non-azeotropic mixed refrigerant, and separates the liquid refrigerant into an intermediate between high pressure and low pressure. After reducing the pressure to low pressure, part or all of it is injected into the intermediate pressure position of the compressor, and the remaining pressure is reduced to low pressure, and the gas refrigerant separated in the condensation process is combined with the liquefied and reduced pressure. It is configured so that the low boiling point components flow into the evaporator in large quantities, increasing the cooling capacity or reducing the compression ratio. This also makes it possible to reduce the heating capacity and increase the heating capacity. Therefore, the applications on the heating side and the cooling side are not particularly limited, and by performing control according to the application, it is possible to guarantee operation even under wide temperature changes on the heat source side. This is the result.

11

[Brief explanation of the drawing]

Fig. 1 is a refrigerant circuit diagram showing a conventional refrigeration cycle device, Fig. 2 1d: a refrigerant circuit diagram showing an embodiment of the refrigeration cycle device according to the present invention, and Fig. 3 is an operation of the refrigeration cycle device shown in Fig. 2. FIG. 4 is a refrigerant circuit diagram according to another embodiment of the present invention. 11... Compressor, 12.14... θ alliance,
13... Gas-liquid separator, 17... Bypass pipe, 16°18.19... Squeezing device, 16...
...Evaporator, 20...Injection circuit. Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
Figure 3 Mr. Lee style 5. Tun, 〃＼Minute thread 1p＼ Figure 4

Claims (2)

[Claims] (1) In a refrigeration cycle device using a non-azeotropic mixed refrigerant and connecting a compressor, a condenser, a throttle device, and an evaporator,
The liquid refrigerant in the condensation process is separated from the gas refrigerant in a gas-liquid separator.
The liquid refrigerant is reduced in pressure to an intermediate pressure between high pressure and low pressure using a throttling device, and part or all of it is injected into the intermediate pressure position of the compressor through an injection circuit, and the remainder is reduced to a low pressure using a throttling device. A refrigeration cycle device in which the gas refrigerant separated during the condensation process is liquefied, combined with the reduced pressure, and then flows into the evaporator. (2) The refrigeration cycle device according to claim 1, which controls the amount of refrigerant injected into the intermediate pressure position of the compressor.