JP2000356420A - System for circulating refrigerant - Google Patents

Abstract

PROBLEM TO BE SOLVED: To control a flow rate of a refrigerant without changing a rotation frequency of a compressor by controlling composition of the refrigerant circulating through the inside of a refrigerant circuit in a refrigerating cycle using a nonazeotropic mixed refrigerant blended with plural kinds of hydrofluorocarbon as the refrigerant. SOLUTION: A refrigerating cycle using a nonazeotropic mixed refrigerant blended with plural kinds of hydrofluorocarbon as the refrigerant is provided with a low pressure receiver 35 located between an evaporator and a compressor 31, a high pressure receiver 42 located between a condenser and a throttling device, an intermediate pressure receiver 79, liquid refrigerant piping for introducing liquid refrigerant from the high pressure receiver 42 to the intermediate pressure receiver 79, gas refrigerant piping from the high pressure receiver 42 to the intermediate pressure receiver 79, a bypass pipe connected with low pressure gas piping via a second throttling device 75 and a third throttling device 80, and a heat exchanger for rectification performing heat exchange with the refrigerant inside the intermediate pressure receiver 79 between the second throttling device 75 and the third throttling device 80.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant circulating system for use in a refrigerating / air-conditioning apparatus using a non-azeotropic mixed refrigerant obtained by blending several kinds of hydrofluorocarbons into a refrigerant.

[0002]

FIG. 34 shows, for example, Japanese Patent Publication No. 6-12201.
Is a conventional refrigeration / air-conditioning apparatus using a non-azeotropic mixed refrigerant, wherein 1 is a compressor, 2 is a load side heat exchanger,
Reference numerals 3 and 4 denote main expansion devices, and reference numeral 6 denotes a heat source side heat exchanger, which are connected by a refrigerant pipe to form a main circuit of a refrigeration cycle. A rectification column 8 has a refrigerant pipe 17 at the top.
The tower reservoir 11 is connected by a refrigerant pipe 18 in which the cooling source 9 is disposed, and a refrigerant pipe 19 and a refrigerant pipe 20 in which the heating source 10 is disposed at the bottom of the rectification tower. The bottom reservoir 12 is connected.

The top reservoir 11 is connected between the load side heat exchanger 2 and the heat source side heat exchanger 6 by a refrigerant pipe 21 provided with an on-off valve 15, and an on-off valve 16 is provided. The tower bottom reservoir 12 is connected by the refrigerant pipe 22.
On the upstream side of the heat source side heat exchanger 6, the tower top reservoir 11 is connected by a refrigerant pipe 23 provided with the sub-throttle device 5 and the on-off valve 13, and the sub-throttle device 5 and the on-off valve 14 are provided. The tower bottom reservoir 12 is connected by the refrigerant pipe 24. The outlet from the top reservoir 11 to the refrigerant pipe 23 is at the bottom of the top reservoir 11, and the outlet from the bottom reservoir 12 to the refrigerant pipe 24 is at the bottom of the bottom reservoir 12. is set up.

In the above configuration, the vapor of the high-temperature and high-pressure non-azeotropic refrigerant (hereinafter referred to as refrigerant) compressed in the compressor 1 flows in the direction of arrow A, and is condensed in the load-side heat exchanger 2 to be condensed. The diaphragm device 3 is entered. During normal operation, since the on-off valves 15 and 16 are closed, the refrigerant enters the main throttle device 4 as it is, and the low temperature and low pressure refrigerant evaporates in the heat source side heat exchanger 6 and returns to the compressor 1 again.

When the composition of the refrigerant flowing through the main circuit is changed, first, the on-off valves 13 and 15 are closed and the on-off valve 14 is turned on in order to make the composition of the refrigerant flowing through the main circuit very rich in high boiling point components. , 16 are opened. Then, a part of the refrigerant flowing out of the main circuit from the main throttle device 3 is diverted to the open / close valve 16, and the rest flows into the main throttle device 4 and flows in the same circuit as in the normal operation. The refrigerant flowing into the on-off valve 16 enters the tower bottom reservoir 12. Part of the refrigerant that has entered the tower bottom reservoir 12 enters the sub-throttle device 5 through the open / close valve 14, merges with the refrigerant flowing in the main circuit upstream of the heat source side heat exchanger 6, and Enters the refrigerant pipe 20 in which the heating source 10 is installed, is heated, and rises as vapor in the refrigerant rectification column 8. At this time, the refrigerant liquid stored in the top reservoir 11 also descends from the refrigerant pipe 17 in the refrigerant rectification column 8,
The so-called rectification is performed by gas-liquid contact with the rising refrigerant vapor.

[0006] Thus, the refrigerant vapor becomes rich in low-boiling components as it rises, is introduced into the refrigerant pipe 18 in which the cooling source 9 is installed, liquefies, and is stored at the top due to the on-off valve 13 being closed. Is stored in the vessel 11. Such rectification is repeated, and finally, the top reservoir 11
, Only the refrigerant having a very low boiling point component is stored. Therefore, the composition of the refrigerant flowing through the main circuit is:
It was designed to be very rich in high boiling components.

To make the composition of the refrigerant flowing in the main circuit rich in low boiling point components, the on-off valves 13 and 15 are opened and the on-off valves 14 and 16 are closed. Then, a part of the refrigerant flowing out of the main circuit exiting the main throttle device 3 is divided and flows into the tower top reservoir 11 through the open on-off valve 15, but the on-off valve 13 is also open. A part of the inflowing refrigerant passes through the refrigerant pipe 23 and passes through the sub-throttling device 5 to join the main circuit. Then, the remaining refrigerant enters the refrigerant rectification tower 8 from the refrigerant pipe 17 and descends. At this time, a part of the refrigerant in the tower bottom reservoir 12 is heated by the heating source 10 and rises in the refrigerant rectification tower, and comes into gas-liquid contact with the descending liquid to perform a so-called rectification action. In this manner, the descending refrigerant liquid gradually becomes rich in the high boiling point component, and is stored in the tower bottom reservoir 12 because the on-off valve 14 is closed. Then, such a rectifying operation is repeated, and finally, only the refrigerant having a very high boiling point component is stored in the tower bottom storage device 12. Therefore, the composition of the refrigerant flowing through the main circuit is:
It was intended to be very rich in low boiling components.

[0008]

The refrigerant circulation system used in such a conventional refrigeration / air-conditioning apparatus is configured to store the components rectified by the rectification tower. There is a problem that it is not possible to cope with sudden pressure fluctuations at the time of starting the compressor which is not constant in the circuit, and the structure of the rectification column itself is complicated, large and costly. The present invention solves the above-mentioned problem, and quickly adjusts the composition in the refrigerant circuit not only during steady operation but also during non-steady operation such as startup, and simplifies the composition adjustment mechanism to reduce cost. Is realized.

[0009]

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected to each other, and a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant is used. A piping for bypassing each device and an opening / closing mechanism are provided in the piping, and the opening / closing mechanism is opened / closed to adjust the composition of the refrigerant while circulating in the refrigerant circuit.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, and a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant. Alternatively, a bypass pipe to the low pressure pipe is provided.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, and a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended into a refrigerant is used. In this configuration, a bypass pipe is provided.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, and a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended into the refrigerant is used. In this configuration, a bypass pipe is provided.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant, and the throttle device is bypassed from an outlet of the condenser. The configuration is such that a bypass pipe leading to the evaporator inlet is provided.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant, and a refrigerant between the evaporator and the compressor. A low-pressure receiver is provided on the low-pressure side, and the degree of supercooling at the condenser outlet is changed according to the load.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant, and a high-pressure refrigerant is applied between the condenser and the throttle device. It is configured to include a receiver.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant, and a refrigerant is located between the evaporator and the compressor. And a high-pressure receiver located between the condenser and the expansion device.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant, and a refrigerant is located between the evaporator and the compressor. , A high-pressure receiver located between the condenser and the expansion device, and the low-pressure receiver and the high-pressure receiver. Further, a bypass pipe for bypassing the space is provided.
Further, an opening and closing mechanism is provided in the bypass pipe.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant, and a refrigerant is located between the condenser and the throttle device. And a bypass pipe that exchanges heat with the high-pressure refrigerant liquid pipe via the expansion device from the high-pressure receiver and then merges with the low-pressure component device or the low-pressure pipe.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant, and a refrigerant is located between the condenser and the throttle device. A high-pressure receiver, and a bypass pipe connected to a pipe at the evaporator outlet from the upper part of the high-pressure receiver through a second expansion device and a second evaporator,
A heat exchanger for exchanging heat between a pipe between the high-pressure receiver and the second expansion device and a pipe between the expansion device and the evaporator is provided.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, and a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant is provided between the condenser and the throttle device. A high-pressure receiver, a bypass pipe connected to a pipe at the evaporator outlet from the upper part of the high-pressure receiver through a second expansion device, a heat storage heat exchanger, and a refrigerant gas pump; and A pipe that connects the heat storage tank and the evaporator outlet, a pipe between the high-pressure receiver and the second throttle device, and a heat exchanger that exchanges heat with the pipe between the throttle device and the evaporator are provided. Things.

The present invention relates to a compressor, a condenser, a throttle device,
A heat storage heat exchanger and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended into the refrigerant, a high-pressure receiver located between the condenser and the expansion device, and from the upper portion of the high-pressure receiver, A second expansion device, a bypass pipe connected to a low-pressure two-phase pipe through a second heat storage heat exchanger, and heat energy through the heat storage heat exchanger and the second heat storage heat exchanger. A heat storage medium that stores the heat storage medium, a heat storage tank that stores the heat storage medium, and a heat exchanger that exchanges heat between a pipe between the high-pressure receiver and the second expansion device and a pipe between the expansion device and the evaporator. It is configured.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant, and a refrigerant is located between the evaporator and the compressor. Low pressure receiver, a high pressure receiver located between the condenser and the throttle device, an intermediate pressure receiver, a bypass pipe connecting the high pressure receiver to the low pressure gas piping via the intermediate pressure receiver, and the intermediate pressure receiver Means for controlling the internal temperature.

According to the present invention, a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are blended as a refrigerant, and a refrigerant is located between the evaporator and the compressor. A low-pressure receiver, a high-pressure receiver located between the condenser and the throttle device, an intermediate-pressure composition adjuster containing a rectifying heat source unit, and a liquid refrigerant from the high-pressure receiver to the intermediate-pressure composition adjuster. A liquid refrigerant pipe, a gas refrigerant pipe that guides a gas refrigerant from the high-pressure receiver to the intermediate-pressure composition adjuster, and a configuration that includes a bypass pipe that is connected to the low-pressure side component device or the low-pressure side pipe from the intermediate-pressure composition adjuster. It was done.

[0024]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The operation of the present invention is as follows. The present invention controls the high and low pressure during steady-state operation and non-steady-state operation by adjusting the composition of the refrigerant circulating in the refrigerant circuit by bypassing the equipment of the refrigerant circuit by the refrigerant, thereby always stably and efficiently. Good driving can be done.

According to the present invention, the refrigerant is bypassed from the compressor discharge section to the low pressure side of the refrigerant circuit.

According to the present invention, the refrigerant rich in the low boiling point component discharged from the compressor is partially bypassed to the low pressure side component equipment or the low pressure side piping, thereby evaporating the liquid refrigerant rich in the high boiling point component trapped in the evaporator. As a result, the composition of the refrigerant can be quickly made constant.

According to the present invention, the opening and closing mechanism can be opened and closed with high accuracy by detecting physical quantities such as time, temperature change, pressure change, and liquid level, as necessary.

According to the present invention, the refrigerant rich in the low boiling point component is returned from the condenser outlet to the compressor suction side, thereby preventing a decrease in the compressor suction pressure and shortening the heating start-up time.

According to the present invention, at the time of startup, the bypass which bypasses the expansion device is opened, and the refrigerant circulation amount is increased to thereby quickly make the composition of the refrigerant constant.

According to the present invention, the amount of the high-boiling component flowing in the refrigerant circuit is adjusted by storing the refrigerant liquid in the low-pressure receiver, and the capacity is adjusted according to the load.

According to the present invention, since the excess refrigerant liquid is stored in the high-pressure receiver, the amount of change in the composition of the refrigerant flowing in the refrigerant circuit is reduced, and stable refrigeration cycle control can be performed.

According to the present invention, the amount of the refrigerant liquid stored in the low-pressure receiver and the high-pressure receiver is adjusted by adjusting the expansion device and the like, or by providing a bypass pipe connecting the low-pressure receiver and the high-pressure receiver to the inside of the refrigerant circuit. Quickly adjust the amount and composition of the flowing refrigerant.

According to the present invention, an opening / closing mechanism is provided in a bypass pipe between the low-pressure receiver and the high-pressure receiver to adjust the amount of refrigerant movement.

According to the present invention, the amount of the refrigerant liquid stored in the low-pressure side and the high-pressure receiver is adjusted through a bypass.
When the compressor discharge pressure rises by adjusting the amount of high-boiling components flowing in the refrigerant circuit, the liquid in the high-pressure receiver is once squeezed, and then heat-exchanges with the main high-pressure liquid refrigerant. The compressor discharge pressure can be suppressed while evaporating and maintaining the capacity.

According to the present invention, a low-pressure gas-liquid two-phase refrigerant is divided by a high-pressure receiver into a liquid refrigerant rich in a high-boiling component and a gas refrigerant rich in a low-boiling component. After that, heat exchange is performed with a gas refrigerant rich in low-boiling components to liquefy, and the liquid refrigerant rich in low-boiling components is squeezed to obtain a low-pressure gas-liquid two-phase state. Thus, by obtaining a low-pressure two-phase refrigerant rich in high-boiling components and a low-pressure two-phase refrigerant rich in low-boiling components, it is possible to obtain evaporation temperatures having different temperatures.

According to the present invention, a low-pressure gas-liquid two-phase refrigerant is divided by a high-pressure receiver into a liquid refrigerant rich in high-boiling components and a gas refrigerant rich in low-boiling components. After that, heat exchange is performed with a gas refrigerant rich in low-boiling components to liquefy, and the liquid refrigerant rich in low-boiling components is squeezed to obtain a low-pressure gas-liquid two-phase state. Thus, by obtaining a low-pressure two-phase refrigerant rich in high-boiling components and a low-pressure two-phase refrigerant rich in low-boiling components, evaporation temperatures having different temperatures are obtained, and when the cooling load is light, heat energy is stored in the heat storage tank. When the load is high, air conditioning can be performed using the heat storage energy stored in the heat storage tank by driving the gas pump.

According to the present invention, a low-pressure gas-liquid two-phase refrigerant is divided by a high-pressure receiver into a liquid refrigerant rich in a high-boiling component and a gas refrigerant rich in a low-boiling component. After that, heat exchange is performed with a gas refrigerant rich in low-boiling components to liquefy, and the liquid refrigerant rich in low-boiling components is squeezed to obtain a low-pressure gas-liquid two-phase state. Thus, by obtaining a low-pressure two-phase refrigerant rich in high-boiling components and a low-pressure two-phase refrigerant rich in low-boiling components, evaporation temperatures having different temperatures are obtained, and when the cooling load is light, heat energy is stored in the heat storage tank. And the degree of supercooling of the refrigerant flowing through the main circuit can be increased by the heat storage energy stored in the heat storage tank.

According to the present invention, by controlling the temperature in the intermediate pressure receiver, the composition of the refrigerant accumulated at the intermediate pressure is changed, and the composition of the refrigerant circulating in the refrigerant circuit is changed.

According to the present invention, in a high-pressure receiver, a liquid refrigerant rich in a high-boiling-point refrigerant and a gas refrigerant rich in a low-boiling-point refrigerant are divided in advance and rectified by a rectifying heat source device in an intermediate-pressure composition controller. Since the high-boiling refrigerant or the low-boiling refrigerant is selected and stored in the intermediate-pressure composition controller, the composition of the refrigerant flowing through the main circuit can be adjusted.

Embodiment 1 An embodiment of the present invention will be described below with reference to FIG. FIG. 1 is a refrigerant circuit diagram showing a basic system of the present invention. In FIG. 1, 31 is a compressor, 32 is a heat source side heat exchanger, 33 is a throttling device, 34 is a load side heat exchanger, and 35 is a low-pressure receiver, which are sequentially connected by refrigerant piping to form a main circuit. Also, 101
Is a bypass pipe for bypassing the refrigerant from the compressor discharge side to the low pressure receiver suction side, and 36 is an opening / closing mechanism located on the bypass pipe 101.

The operation will be described. As shown in the flow of the refrigerant in FIG. 1, the refrigerant discharged from the compressor 31 is sucked into the heat source side heat exchanger 32, the expansion device 33, the load side heat exchanger 34, and the flow compressor 31. On the other hand, when the compressor 31 is started,
The opening / closing mechanism 36 is opened to guide the refrigerant gas discharged from the compressor 31 to the low-pressure receiver 35. In many cases, the refrigerant liquid is trapped in the low-pressure receiver 35 due to heat capacity, the gas component is rich in low-boiling components, and the liquid component is rich in high-boiling components. When the compressor 31 is started, the discharge pressure of the compressor 31 rapidly rises because the compressor 31 absorbs a gas component rich in low boiling point components, but a part of the high temperature discharge gas of the compressor 31 is sucked into the low pressure receiver 35. By returning to the side,
The liquid component rich in high boiling point refrigerant is evaporated and vaporized, and the compressor 3
The composition of the refrigerant sucked into 1 is adjusted to suppress a rise in high pressure.

In the description of FIG. 1, the bypass pipe 101 is connected to the low-pressure pipe between the low-pressure receiver 35 and the load-side heat exchanger 34 (evaporator) to blow out the discharge gas. The same effect can be obtained in any place where there is a possibility that the refrigerant liquid may fall asleep. In the above description, the opening / closing mechanism 36 is opened when the compressor 31 is started. However, a condition requiring a composition adjustment, for example, a physical quantity such as a decrease in capacity may be detected, or the opening may be performed at regular intervals.

Embodiment 2 Hereinafter, a second embodiment of the present invention will be described with reference to FIG. In the figure, the first embodiment
The same parts as those described above are denoted by the same reference numerals, and description thereof will be omitted. FIG.
As shown in FIG. 1, the component of the first embodiment shown in FIG. 1 includes a bypass pipe 102 that bypasses the discharge side of the compressor 31 and the outlet of the main throttle device 33, and an opening / closing mechanism 37 located on the bypass pipe 102. Configuration. Further, the bypass pipe 101 and the opening / closing mechanism 36 may be eliminated,
You may leave it as it is.

The operation will be described. The refrigerant flows as shown. On the other hand, when the compressor is started, the opening / closing mechanism 37 is opened,
The refrigerant gas discharged from the compressor 31 is transferred to the load-side heat exchanger 3.
4 to the entrance. In many cases, the refrigerant liquid is stagnant in the load side heat exchanger 34 due to heat capacity, and the liquid component is rich in high boiling point components. At startup, the compressor 31 sucks a gas component rich in low boiling point components, so that the discharge pressure of the compressor 31 rises rapidly, but a part of the high temperature compressor 31 discharge gas is transferred to the load side heat exchanger. By bypassing to
The liquid component rich in high boiling point refrigerant is evaporated and vaporized, and the compressor 3
The composition of the refrigerant sucked into 1 is adjusted to suppress a rise in high pressure.

In the description of FIG. 2, the bypass pipe 102 is connected to the pipe between the inlet of the load-side heat exchanger 34 and the outlet of the main expansion device 33. However, the bypass pipe 102 and the bypass pipe 101 described in FIG. By providing two or more bypass pipes that connect different parts at different positions, hot gas can flow through the entire area where laying is likely to occur, so that the time until the composition of the refrigerant becomes constant can be further reduced. become.

If the room temperature drops when the system is stopped,
The heat exchange and the header of the heat exchanger will be filled with liquid.

The opening and closing mechanism (FIGS. 136 and 23)
7) is opened when the composition is adjusted or when the system is started. For example, the open time may be detected and closed after a few minutes. By flowing the refrigerant only for a predetermined time, the capacity loss due to the bypass of the refrigerant can be eliminated during the steady operation in which the opening / closing mechanism is closed. In addition to the time detection, a change in temperature or a change in pressure, such as after the liquid level of the low-pressure receiver 35 has dropped (eliminated), after the superheat of the suction of the compressor 31 has increased, or after the high-pressure has stopped rising. May be detected and closed. That is, to detect that the composition has become constant,
Alternatively, when the liquid is no longer laid down, the opening / closing mechanism is closed to return to the normal operation circuit. 1 and 2
In the above description, an example of the refrigerant circuit is shown, but it goes without saying that a heating circuit may be used. When the predetermined physical quantity does not reach a certain value as described above, the opening and closing timing of the opening and closing mechanism becomes appropriate, so that efficient operation can be performed.

Embodiment 3 Hereinafter, a third embodiment of the present invention will be described with reference to FIG. In the figure, the first embodiment
The same parts as those described above are denoted by the same reference numerals, and description thereof will be omitted. FIG.
As shown in the figure, the outlet side of the heat source side heat exchanger 32 and the compressor 3
(1) A structure including a bypass pipe 103 that bypasses the suction side and an opening / closing mechanism 38 located on the bypass pipe 103 is adopted.

The operation will be described. The refrigerant flows as shown. When the compressor 31 is started, the opening / closing mechanism 38 is opened, and the uncondensed refrigerant gas at the outlet of the heat source side heat exchanger 32, which is a condenser rich in low boiling point components, is guided to the compressor 31 suction.
During the suction of the compressor 31, the pressure is suppressed from becoming lower than the atmospheric pressure, and damage to the compressor is prevented. This configuration is for heating
It is effective when the outside air is very low.

Embodiment 4 Hereinafter, a fourth embodiment of the present invention will be described with reference to FIG. In the figure, the first embodiment
The same parts as those described above are denoted by the same reference numerals, and description thereof will be omitted. FIG.
As shown in FIG. 1, in the components of the first embodiment in FIG. 1, a bypass pipe 104 that bypasses the main throttle device from the outlet side of the heat source side heat exchanger 32 and connects to the inlet of the load side heat exchanger 34, And an opening / closing mechanism 39 located above.

The operation will be described. The refrigerant flows as shown. When the compressor 31 is started, the opening / closing mechanism 39 is opened to reduce the high / low pressure and increase the circulation amount of the refrigerant,
The concentration distribution of the refrigerant in the refrigerant circuit is quickly made uniform while suppressing a rise in high pressure at the time of startup, and stable refrigeration cycle control can be performed from the time of startup. This configuration is effective at the time of cooling, especially when restarting in about 3 minutes. When a high-pressure receiver (not shown) is used, the position of the throttle changes, but there is no distinction between cooling and heating.

By opening the opening / closing mechanism at startup, the stability of the refrigeration cycle at startup can be improved. The reason why the refrigerant is bypassed from the outlet of the heat source side heat exchanger 32 as a condenser and not from the downstream of the throttle outlet is that the refrigerant is in a low-pressure two-phase state, so that a differential pressure is hardly generated and the bypass hardly flows. The opening / closing mechanism 39 in FIG. 4 may be fully opened, provided that the flow rate of the refrigerant flowing through the bypass is too large.
Since a large amount of liquid is backed up, it is necessary to provide the bypass pipe itself with a certain throttling function. With such a configuration, the concentration distribution of the refrigerant can be made uniform in a short time. The effect of eliminating the concentration distribution of the refrigerant present in the refrigerant circuit and increasing the composition quickly by taking a large amount of refrigerant circulation. Is obtained.

Embodiment 5 FIG. 5 is a refrigerant circuit diagram showing the basic system of the present invention. In the figure, 31 is a compressor, 40 is a four-way valve, 32 is a heat source side heat exchanger, 33 is a main throttle device, 34 is a load side heat exchanger, 35 is a low pressure receiver, and these are sequentially connected by refrigerant piping. Form the main circuit.

The operation will be described. The flow of the refrigerant at the time of heating and at the time of cooling is shown in the figure. The refrigerant is charged in advance so that the surplus refrigerant accumulates in the low-pressure receiver, and the degree of supercooling at the heat exchanger outlet of the heat source side heat exchanger 32 is changed according to the load. When the load is heavy, the degree of supercooling at the heat exchanger outlet of the heat source side heat exchanger 32 is reduced, and an operation is performed in which excess refrigerant is stored in the low-pressure receiver 35. The excess liquid refrigerant accumulated in the low-pressure receiver 35 is rich in high-boiling components, and therefore, the composition of the refrigerant circulating in the main circuit is a refrigerant rich in low-boiling components. For this reason, the density of the refrigerant sucked into the compressor 31 increases, the refrigerant circulation amount increases, and the capacity increases. When the load is light, the degree of supercooling at the heat exchanger outlet on the side of the heat source side heat exchanger 32 is increased, and the excess refrigerant is moved from the low-pressure receiver 35 to the heat exchanger or the refrigerant pipe. By operating without storing, the amount of circulating refrigerant is reduced,
Decrease ability.

The degree of supercooling is changed, for example, by changing the degree of opening of the expansion device based on temperature and pressure data in the low-pressure receiver 35. Here, a heavy load indicates a high air condition (DB / WB), and a light load indicates a low air condition. The degree of supercooling is defined as the difference between the saturated liquid temperature at the outlet pressure of the condenser (at the time of cooling: heat source side heat exchanger 32 / at the time of heating: load side heat exchanger 34) and the refrigerant temperature at the outlet of the condenser. Since the temperature of the saturated liquid depends on the composition of the refrigerant, it needs to be estimated in advance by sensing (pressure and temperature of the low-pressure receiver). The difference between the filling composition (the composition of the refrigerant sealed in the unit) and the circulation composition (the composition of the refrigerant when the unit is operated) occurs.
This is due to the gas-liquid slip in the gas-liquid two-phase line, that is, the velocity of the R32-rich gas is higher than that of the R134a-rich liquid, so that R134a is close to staying in place. The limit is a low-pressure receiver (accumulator).

By storing the refrigerant liquid in the low-pressure receiver 35 in this manner, the amount of the high-boiling component refrigerant flowing in the refrigerant circuit is adjusted, and the capacity is adjusted according to the load.

The capacity indicates the amount of heat exchange in the heat exchanger.
When the low-pressure receiver 35 stores the excess liquid refrigerant, the liquid refrigerant rich in high-boiling components is stored therein, and the composition of the refrigerant flowing through the main refrigerant circuit becomes rich in low-boiling components. Therefore, by controlling the amount of the liquid refrigerant accumulated in the low-pressure receiver 35, the composition of the refrigerant flowing through the main refrigerant circuit can be changed. Further, in order to change the liquid level in the low-pressure receiver 35, the throttle moves down to move the refrigerant from inside the low-pressure receiver 35 to the condenser. The component of the excess liquid refrigerant is rich in high-boiling components, and if the circulating composition becomes rich in low-boiling components, the density of the refrigerant gas absorbed by the compressor 31 increases, and the refrigerant circulation amount increases. Increase.

Embodiment 6 FIG. FIG. 6 is a refrigerant circuit diagram showing the basic system of the present invention. In the figure, the fifth embodiment
The same parts as those described above are denoted by the same reference numerals, and description thereof will be omitted. FIG.
In addition to the components of the fifth embodiment, a sub-throttle device 41 and a high-pressure receiver 42 are newly provided, and the sub-throttle device 41 and the high-pressure receiver 42 are connected between the heat source side heat exchanger 32 and the main throttle device. .

The operation will be described. The refrigerant flows as shown. The surplus refrigerant is filled beforehand so as to accumulate in the low-pressure receiver 35 or the high-pressure receiver 42. When cooling,
The refrigerant gas discharged from the compressor 31 passes through the four-way valve 40 and is condensed in the heat source side heat exchanger 32 to become a liquid refrigerant. After being slightly throttled by the sub-throttle device 41, it enters the high-pressure receiver 42. The liquid refrigerant passing through the high-pressure receiver 42 is supplied to the main throttle device 3
3, the pressure is reduced to a low pressure, evaporated in the load-side heat exchanger 34, and compressed through the four-way valve 40 and the low-pressure receiver 35.
Return to 1. When the liquid refrigerant is stored in the high-pressure receiver 42, the outlet superheat degree of the load-side heat exchanger 34, which is an evaporator, is controlled to be constant, and when the liquid refrigerant is stored in the low-pressure receiver 35, a condenser is used. Control is performed to keep the degree of supercooling constant at the outlet of a certain heat source side heat exchanger 32.

When the load is heavy, the sub-throttle device 41 is tightly throttled so that the refrigerant enters the two-phase state at the outlet of the sub-throttle device 41. Moves to the low-pressure receiver 35. Since the refrigerant liquid rich in the high boiling point component is stored in the low pressure receiver 35, the refrigerant circulating in the main circuit is a refrigerant rich in the low boiling point component. For this reason, the density of the refrigerant sucked into the compressor 31 increases, the refrigerant circulation amount increases, and the capacity increases. That is, the sub-aperture device 41 is squeezed tightly,
That the refrigerant flowing into the high-pressure receiver 42 has two phases,
Both the effect of transferring the liquid from the high-pressure receiver 42 to the low-pressure receiver 35 causes the high-pressure receiver 42 to run out of liquid.

When the load is light, the main throttle device 33 is throttled tightly, and the liquid refrigerant is supplied from the low pressure receiver 35 to the high pressure receiver 4.
By moving to 2, the composition of the refrigerant approaches the composition of the charged refrigerant, so that the capacity can be reduced.

Even when a low pressure is applied when the outside air is at a low temperature during heating, the lowering of the low pressure can be suppressed by storing the liquid refrigerant in the low-pressure receiver 35.

Similarly, in the case of heating, the capacity can be adjusted by storing the liquid refrigerant in the high-pressure receiver 42 or the low-pressure receiver 35 according to the load. In this way, by storing the refrigerant liquid in the low-pressure receiver 35, the amount of the high-boiling component flowing in the refrigerant circuit is adjusted, and the capacity is adjusted according to the load.

By storing the excess refrigerant liquid in the high-pressure receiver 42, the amount of change in the composition of the refrigerant flowing in the refrigerant circuit can be reduced, and stable refrigeration cycle control can be performed. Further, by operating the main throttle and the sub-aperture, the composition can be easily adjusted during operation using each receiver.
This means that the amount of the refrigerant in the high-pressure receiver 42 can be adjusted by operating the expansion device 33, that is, the opening of the expansion device 33 is controlled so that the degree of superheat of the refrigerant at the outlet of the heat source side heat exchanger 32 as an evaporator becomes constant. Will control the degree.

When the load is heavy (air temperature is high), FIG.
As shown by the arrow A, the refrigerant entering the receiver is in a two-phase state,
Since the refrigerant indicated by the arrow B coming out of the receiver is saturated,
The refrigerant flows out in a single phase, so that the amount of refrigerant taken out of the high-pressure receiver 42 increases, and the liquid level in the high-pressure receiver 42 drops.

When the load is light (air temperature is low), arrow A
When the expansion device 33 is throttled so that the single-phase liquid refrigerant entering the high-pressure receiver 42 is supercooled, the supercooled liquid refrigerant entering the high-pressure receiver 42 condenses the gas refrigerant in the high-pressure receiver 42 and becomes itself. The liquid refrigerant becomes a saturated single-phase liquid refrigerant and is taken out from the high-pressure receiver 42 as shown by the arrow B. Therefore, as much as the gas in the high-pressure receiver 42 is condensed, the high-pressure receiver 4
The amount of liquid in 2 increases. In the configuration shown in FIG. 4, the heat exchanger has a function as a liquid reservoir,
By providing the high-pressure receiver 42 on the high-pressure side, the amount of adjustment can be significantly increased.

When the load is heavy at the time of heating, the main throttle device 33 is tightly throttled to make the above-mentioned state at the time of heavy load, and the liquid refrigerant in the high-pressure receiver 42 is reduced. Conversely, when the load is light, the sub-throttle device 41 is squeezed tightly to make the above-mentioned state where the load is light.

As described above, by disposing the high-pressure receiver 42 on the outlet side of the heat exchanger serving as a condenser, the liquid refrigerant condensed in the condenser accumulates in the high-pressure receiver 42. Since the circulating refrigerant is all condensed and in a liquid single phase state, the composition of the liquid refrigerant is close to the circulating composition, which is different from the case where excess refrigerant is stored in the low-pressure receiver 35. Further, by providing the sub-throttle device 41, the high-pressure receiver can be positioned in the high-pressure liquid line during cooling and heating. By providing a means for changing the pressure between the heat exchanger serving as a condenser and the high-pressure receiver 42, the dryness of the refrigerant flowing into the high-pressure receiver 42 is changed, and the liquid in the high-pressure receiver 42 is easily changed. The surface can be controlled.

Embodiment 7 FIG. 7 is a refrigerant circuit diagram showing the basic system of the present invention. In the figure, the sixth embodiment
The same parts as those described above are denoted by the same reference numerals, and description thereof will be omitted. FIG.
In addition to the components of the sixth embodiment, the bypass pipe 1 extending from the bottom of the high-pressure receiver 42 to the low-pressure receiver 35
05 and an opening and closing device 43 are provided, and the opening and closing device 43 is installed in the middle of the bypass pipe 105.

The operation will be described. The refrigerant flows as shown. The surplus refrigerant is filled beforehand so as to accumulate in the low-pressure receiver 35 or the high-pressure receiver 42. When cooling,
The refrigerant gas discharged from the compressor 31 passes through the four-way valve 40 and is condensed in the heat source side heat exchanger 32 to become a liquid refrigerant. After being slightly throttled by the sub-throttle device 41, it enters the high-pressure receiver 42. The liquid refrigerant passing through the high-pressure receiver 42 is supplied to the main throttle device 3
3, the pressure is reduced to a low pressure, evaporated in the load-side heat exchanger 34, and compressed through the four-way valve 40 and the low-pressure receiver 35.
Return to 1.

When the load is heavy, the switching device 43 is opened,
The liquid refrigerant in the high-pressure receiver 42 moves to the low-pressure receiver 35 through the bypass pipe 105 by tightly restricting the sub-throttle device 41. If the refrigerant is made to be in a two-phase state at the outlet of the sub-throttle device 41, the liquid refrigerant does not accumulate in the high-pressure receiver 42, and the liquid refrigerant is secured in the low-pressure receiver 35. Since the refrigerant liquid rich in the high boiling point component is accumulated in the low-pressure receiver 35, the refrigerant circulating in the main circuit is:
It becomes a refrigerant rich in low boiling point components. For this reason, the compressor 31
The density of the refrigerant sucked into the air increases, the refrigerant circulation amount increases,
Ability increases.

When the load is light, the main throttle device 33 is tightly throttled, and the liquid refrigerant is supplied from the low-pressure receiver 35 to the high-pressure receiver 4.
By moving to 2, the composition of the refrigerant approaches the composition of the charged refrigerant, so that the capacity can be reduced.

Similarly, at the time of heating, according to the load,
The capacity can be adjusted by storing the liquid refrigerant in the high-pressure receiver 42 or the low-pressure receiver 35. As described above, the refrigeration / air-conditioning apparatus adjusts the amount of the refrigerant liquid stored in the low-pressure receiver 35 and the high-pressure receiver 42 by using the bypass pipe 105 that connects the low-pressure receiver 35 and the high-pressure receiver 42, so that the refrigerant circuit Quickly adjust the amount of high boiling components flowing through and adjust the capacity according to the load.
By providing the bypass pipe 105 as described above, the composition can be quickly adjusted and the refrigeration cycle can be stabilized.

Embodiment 8 FIG. FIG. 8 is a refrigerant circuit diagram showing the basic system of the present invention. In the figure, the sixth embodiment
The same parts as those described above are denoted by the same reference numerals, and description thereof will be omitted. FIG.
In addition to the components of the sixth embodiment, the bypass pipe 1 extending from the upper part of the high-pressure receiver 42 to the low-pressure receiver 35
06 and the opening and closing device 44 are provided, and the opening and closing device 44 is installed in the middle of the bypass pipe 106.

The operation will be described. The surplus refrigerant is filled beforehand so as to accumulate in the low-pressure receiver 35 or the high-pressure receiver 42. In the case of cooling, the refrigerant gas discharged from the compressor 31 passes through the four-way valve 40 and is condensed in the heat source side heat exchanger 32 to become a liquid refrigerant. enter. The liquid refrigerant that has passed through the high-pressure receiver 42 is throttled to a low pressure by the main throttle device, evaporates in the load-side heat exchanger 34, and returns to the compressor 31 via the four-way valve 40 and the low-pressure receiver 35.

During operation, when the outside air is at a low temperature during heating, and when the low pressure is low, the switch 44 is opened to guide the uncondensed gas rich in the low boiling point component to the low pressure receiver 35 as shown in the figure.
The compressor 31 suppresses a decrease in suction pressure.

Embodiment 9 Hereinafter, a ninth embodiment of the present invention will be described with reference to FIG. 31 is a compressor, 40 is a four-way valve, 32 is a heat source side heat exchanger, 41 is a sub-throttle device, 42
Is a high-pressure receiver, 33 is a main throttle device, 34 is a load-side heat exchanger, and 35 is a low-pressure receiver, which are sequentially connected by refrigerant piping to form a main circuit. Reference numerals 47 and 48 denote opening and closing mechanisms for opening and closing the inlet and outlet of the high-pressure receiver 42, respectively. Also,
107 is a first bypass pipe from the high-pressure receiver 42 to the low-pressure receiver, and 45 is an opening / closing mechanism provided on the first bypass pipe. 108 is a high voltage receiver 42
And a second bypass pipe that bypasses the opening and closing mechanisms 47 and 48, and 46 is an opening and closing mechanism provided on the second bypass pipe 108.

The operation will be described. The refrigerant flows as shown in FIG. The surplus refrigerant is filled beforehand so as to accumulate in the low-pressure receiver 35 or the high-pressure receiver 42. In the case of cooling, the refrigerant gas discharged from the compressor 31 is supplied to the four-way valve 40.
Through the heat source side heat exchanger 32 to be condensed into a liquid refrigerant,
After being slightly throttled by the sub-throttle device 41, the high-pressure receiver 42
to go into. The liquid refrigerant that has passed through the high-pressure receiver 42 is throttled to a low pressure by the main throttle device, evaporates in the load-side heat exchanger 34, and passes through the four-way valve 40 and the low-pressure receiver 35.
Return to 1.

When the load is heavy, the opening / closing mechanism 45 is opened,
The liquid refrigerant in the high-pressure receiver 42 moves to the low-pressure receiver 35 through the bypass pipe 107 by tightly restricting the sub-throttle device 41. If the refrigerant is made to be in a two-phase state at the outlet of the sub-throttle device 41, the liquid refrigerant will not accumulate in the high-pressure receiver 42, and the liquid refrigerant will
Is held. The liquid refrigerant held in the low-pressure receiver 35 is different from the composition of the refrigerant circulating in the main circuit, and becomes a refrigerant rich in high-boiling components. After detecting the state secured in the low-pressure receiver 35, the opening and closing mechanisms 47 and 48 are closed, and the opening and closing mechanism 46 is opened so that the refrigerant bypasses the high-pressure receiver 42 and the distribution of the refrigerant in the refrigerant circuit is always kept constant. Stabilizes driving. To detect the state that the liquid refrigerant is in the receiver, the liquid level detection circuit, that is, heat the outer wall of the accumulator by a certain amount, detect the temperature rise and compare the heating position, or detect the circulation composition as described later. There is a method of determining the amount of refrigerant in the receiver.

When the load is light, the opening / closing mechanisms 47 and 48
Is opened, the opening / closing mechanism 46 is closed, the main throttle device 33 is tightly throttled, and the state of the refrigerant is changed to a liquid state at the outlet of the heat source side heat exchanger 32 acting as a condenser, so that the high-pressure receiver 42 Store refrigerant. With the liquid refrigerant stored in the high-pressure receiver 42, the opening and closing mechanisms 47 and 48 are closed, and the opening and closing mechanism 46 is opened to maintain the state in which the liquid refrigerant is stored in the high-pressure receiver 42. At this time, the liquid refrigerant held in the high-pressure receiver 42 has a composition close to the composition when the refrigerant circuit is filled with the refrigerant, and the composition of the refrigerant circulating in the refrigerant circuit also has the composition when the refrigerant is filled. It will be close.

In the case of heating, the refrigerant gas discharged from the compressor 31 passes through the four-way valve 40 and is condensed in the load-side heat exchanger 34 to become a liquid refrigerant. Enter the receiver 42. The liquid refrigerant that has passed through the high-pressure receiver 42 is throttled to a low pressure by the sub-throttle device 41, evaporates in the heat-source-side heat exchanger 32, and returns to the compressor 31 via the four-way valve 40 and the low-pressure receiver 35.

When the load is heavy, the switching device 45 is opened,
The liquid refrigerant in the high-pressure receiver 42 moves to the low-pressure receiver 35 through the bypass pipe 107 by tightly restricting the main expansion device 33. If the refrigerant is made to be in a two-phase state at the outlet of the main throttle device 33, the liquid refrigerant will not accumulate in the high-pressure receiver 42, and the liquid refrigerant will
Is held. The liquid refrigerant held in the low-pressure receiver 35 is different from the composition of the refrigerant circulating in the main circuit, and becomes a refrigerant rich in high-boiling components. After an appropriate amount of refrigerant has moved to the low-pressure receiver 35, the opening and closing mechanisms 47 and 48 are closed, and the opening and closing mechanism 46 is opened, so that the refrigerant bypasses the high-pressure receiver 42, and the refrigerant distribution in the refrigerant circuit is always constant. This stabilizes driving.

When the load is light, the opening / closing mechanisms 47 and 48
Is opened, the opening / closing mechanism 46 is closed, the sub-throttle device 41 is tightly throttled, and at the outlet of the load-side heat exchanger 32 acting as a condenser, the state of the refrigerant is changed to a liquid state. Store refrigerant. With the liquid refrigerant stored in the high-pressure receiver 42, the opening and closing mechanisms 47 and 48 are closed, and the opening and closing mechanism 46 is opened to maintain the state in which the liquid refrigerant is stored in the high-pressure receiver 42. At this time, the liquid refrigerant held in the high-pressure receiver 42 has a composition close to the composition when the refrigerant circuit is filled with the refrigerant, and the composition of the refrigerant circulating in the refrigerant circuit also has the composition when the refrigerant is filled. Can be close.

As described above, by selectively storing the refrigerant liquid in the low-pressure receiver 35 or the high-pressure receiver 42 according to the load, the composition of the refrigerant circulating in the refrigerant circuit is changed, and the rotation frequency of the compressor 31 is changed. The ability can be changed without changing.

As described above, the refrigeration / air-conditioning system constituted by these refrigerant circuits uses the bypass pipe connecting the low-pressure receiver 35 and the high-pressure receiver 42 with the amount of the refrigerant liquid stored in the low-pressure receiver 35 and the high-pressure receiver 42. In this way, the amount of the high boiling point component flowing in the refrigerant circuit is quickly adjusted, and the capacity is adjusted according to the load.

Further, these refrigeration / air-conditioning apparatuses adjust the refrigerant liquid stored in the low-pressure receiver 35 and the high-pressure receiver 42, and when the pressure is reduced by the suction of the compressor 31, the boiling point is lower than that of the upper part of the high-pressure receiver 42. By returning the refrigerant gas rich in components to the suction side of the compressor 31, a decrease in compressor suction pressure is prevented.

In the seventh, eighth, and ninth embodiments, an example in which an opening / closing mechanism is provided in the bypass pipe has been described. Open to the public.

Embodiment 10 FIG. Hereinafter, a tenth embodiment of the present invention will be described with reference to FIG. 31 is a compressor, 4
0 is a four-way valve, 32 is a heat source side heat exchanger, 41 is a sub-throttle device, 42 is a high-pressure receiver, 33 is a main throttle device, 34 is a load-side heat exchanger, 35 is a low-pressure receiver, and these are refrigerant pipes. They are sequentially connected to form a main circuit. Reference numeral 109 denotes a bypass pipe from the high-pressure receiver 42 to the low-pressure receiver 35, and reference numeral 49 denotes a third throttle device provided on the first bypass pipe. Reference numeral 50 denotes a supercooling heat exchanger for exchanging heat between a main pipe between the main throttle device 33 and the sub-throttle device 41 and a bypass pipe between the third throttle device 49 and the low-pressure receiver 35.

The operation will be described. The refrigerant flows as shown in FIG. The surplus refrigerant is filled beforehand so as to accumulate in the low-pressure receiver 35 or the high-pressure receiver 42. In the case of cooling, the refrigerant gas discharged from the compressor 31 is supplied to the four-way valve 4.
After passing through 0, it is condensed in the heat source side heat exchanger 32 to become a liquid refrigerant, and after being slightly throttled by the sub-throttle device 41, it enters the high-pressure receiver. The liquid refrigerant that has passed through the high-pressure receiver 42 is throttled to a low pressure by the main throttle device, evaporates in the load-side heat exchanger 34, and passes through the four-way valve 40 and the low-pressure receiver 35.
Return to 1.

Here, the third expansion device 49 is opened, and the liquid refrigerant in the high-pressure receiver 42 is guided to the supercooling heat exchanger 50 as a low-pressure two-phase refrigerant. In the supercooling heat exchanger 50, the main pipe through which the high-pressure liquid refrigerant flows and the bypass pipe through which the low-pressure two-phase refrigerant flows exchange heat, and the degree of subcooling of the liquid refrigerant flowing through the main pipe can be increased. Thereby, the reliability of the flow control in the main throttle device 33 and the sub throttle device 41 can be improved.

When the increase in high pressure is remarkable, the main throttle device 33 and the sub-throttle device 41 are weakened, and the state of the refrigerant is changed to a two-phase state at the outlet of the heat source side heat exchanger 32 acting as a condenser. I do. At this time, the liquid refrigerant accumulated in the high-pressure receiver 42 becomes rich in high-boiling-point refrigerant, and the third expansion device 49 is opened to evaporate the high-boiling-point-rich refrigerant in the supercooling heat exchanger 50. Later, low-voltage receiver 35
By returning the pressure to, the compressor 31 sucks in the gas refrigerant rich in the high boiling point component, so that the discharge pressure of the compressor 31 can be suppressed.

In the case of heating, the refrigerant gas discharged from the compressor 31 passes through the four-way valve 40 and is condensed in the load-side heat exchanger 34 to become liquid refrigerant. Enter the receiver 42. The liquid refrigerant that has passed through the high-pressure receiver 42 is throttled to a low pressure by the sub-throttle device 41, evaporates in the heat-source-side heat exchanger 32, and returns to the compressor 31 via the four-way valve 40 and the low-pressure receiver 35.

Here, the third expansion device 49 is opened to guide the liquid refrigerant in the high-pressure receiver 42 to the supercooling heat exchanger 50 as a low-pressure two-phase refrigerant. In the supercooling heat exchanger 50, the main pipe through which the high-pressure liquid refrigerant flows and the bypass pipe through which the low-pressure two-phase refrigerant flows exchange heat, and the degree of subcooling of the liquid refrigerant flowing through the main pipe can be increased. Thereby, the reliability of the flow control in the main throttle device 33 and the sub throttle device 41 can be improved.

When the high pressure rise is remarkable, the main throttle device 33 and the sub-throttle device 41 are weakened, and the state of the refrigerant is changed to a two-phase state at the outlet of the load side heat exchanger 34 acting as a condenser. I do. At this time, the liquid refrigerant accumulated in the high-pressure receiver 42 becomes rich in high-boiling-point refrigerant, and the third expansion device 49 is opened to evaporate the high-boiling-point-rich refrigerant in the supercooling heat exchanger 50. Later, low-voltage receiver 35
By returning the pressure to, the compressor 31 sucks in the gas refrigerant rich in the high boiling point component, so that the discharge pressure of the compressor 31 can be suppressed.

That is, in this refrigeration / air-conditioning apparatus, the amount of the high-boiling component flowing in the refrigerant circuit is adjusted by adjusting the amount of the refrigerant liquid stored in the low-pressure receiver 35 and the high-pressure receiver 42, and the discharge pressure of the compressor 31 is reduced. When ascending, the liquid in the high-pressure receiver 42 is once squeezed, and then heat-exchanges with the main high-pressure liquid refrigerant to evaporate itself, thereby suppressing the discharge pressure of the compressor 31 while maintaining the capability. Can be. Thus, by providing the bypass pipe 109 that exchanges heat with the high-pressure refrigerant liquid pipe via the throttle from the high-pressure receiver 42 and then joins with the low-pressure gas pipe, the reliability of the flow rate control can be improved and the capacity can be improved. The discharge pressure of the compressor 31 can be suppressed while maintaining the pressure.

Embodiment 11 FIG. FIG. 11 is a refrigerant circuit diagram showing Embodiment 11 of the present invention. In the figure, 31 is a compressor, 54 is a four-way valve, 32 is a heat source side heat exchanger, 41 is a sub-throttle device, 42 is a high-pressure receiver, 33 is a main throttle device, 53
Is a refrigerant-refrigerant heat exchanger, 34 is a load-side heat exchanger, 35 is a low-pressure receiver, and these are sequentially connected to form a main pipe. Reference numeral 51 denotes a third expansion device, 52 denotes a second load-side heat exchanger, and a refrigerant-refrigerant heat exchanger 53, a third expansion device 51, and a second load-side heat exchanger 52 One end is connected to the high-pressure receiver 42 by a pipe 110,
The other end is connected to a pipe between the load side heat exchanger 34 and the four-way valve 54.

The operation will be described. Figure 1 shows the flow of the refrigerant
Write it in 1. In the case of cooling, the air enters the heat source side heat exchanger 32 from the compressor 31 via the four-way valve 54, is condensed here, is slightly throttled by the sub-throttle device 41, and then enters the high-pressure receiver 42. In the high pressure receiver 42, the refrigerant is separated into a gas rich in low boiling components and a liquid rich in high boiling components. The refrigerant rich in the high boiling point component is throttled to a low pressure by the main throttle device 33, slightly absorbed by the refrigerant-refrigerant heat exchanger 53, and enters the load-side heat exchanger 34. The refrigerant that has absorbed heat from the surroundings in the load side heat exchanger 34 and evaporated and returned to the compressor 31 via the four-way valve 54 and the low-pressure receiver 35.

Further, the signals separated by the high pressure receiver 42
The refrigerant gas rich in low boiling point refrigerant is supplied to the refrigerant-refrigerant heat exchanger 53.
At this point, heat exchange is performed with the low-pressure two-phase refrigerant to condense. The high-pressure liquid refrigerant rich in the low-boiling-point component is throttled to a low pressure by the third throttle device 51, takes heat from the surroundings in the second load-side heat exchanger 52, evaporates itself, and loads the refrigerant. The refrigerant mixes with the high-boiling-point-rich refrigerant gas evaporated in the side heat exchanger 34 and returns to the compressor 31 via the four-way valve 54 and the low-pressure receiver 35. Here, since the refrigerant flowing through the second load-side heat exchanger 52 is rich in low-boiling components, the evaporation temperature can be different from that of the load-side heat exchanger 34 even at the same low pressure. By doing so, the low-boiling component-rich gas is condensed by the heat exchanger 53, so that the low-boiling component-rich refrigerant flows through the heat exchanger 52, and the high-boiling component-rich refrigerant flows through the heat exchanger 34. Refrigerant flows. Therefore, if the pressures are the same, the heat exchangers 34 and 52 have different evaporation temperatures, and in this example, the evaporation temperature of the heat exchanger 52 is lower.

Also, by controlling the amount of heat exchange in the heat source side heat exchanger 32, the composition of the gas and liquid of the refrigerant separated in the high pressure receiver 42 is controlled, and the load side heat exchanger 34 It is possible to control the difference between the evaporation temperatures obtained in the second load-side heat exchanger 52. The above is, for example, the division of the heat exchanger in the heat exchanger 32 or the air volume (water volume).
The amount of heat exchange is adjusted by adjusting the amount of heat exchange. The adjustment of the degree of adjustment is performed, for example, based on the degree of superheat of the refrigerant at the heat exchangers 34 and 52 at the outlet.

This refrigeration / air-conditioning apparatus has a high-pressure receiver 42
In, the liquid refrigerant rich in the high boiling point component and the gas refrigerant rich in the low boiling point component are divided, and the liquid refrigerant rich in the high boiling point component is once squeezed into a low-pressure gas-liquid two-phase refrigerant, and then rich in the low boiling point component. The liquid refrigerant is heat-exchanged with the gas refrigerant to be liquefied, and the liquid refrigerant rich in low-boiling components is squeezed to form a low-pressure gas-liquid two-phase state. Thus, by obtaining a low-pressure two-phase refrigerant rich in high-boiling components and a low-pressure two-phase refrigerant rich in low-boiling components, it is possible to obtain evaporation temperatures having different temperatures.

Embodiment 12 FIG. 12 to 15 are refrigerant circuit diagrams showing Embodiment 12 of the present invention. FIG.
2 to 15 show the flow of the refrigerant in each operation state. In the figure, the same portions as those of the eleventh embodiment are denoted by the same reference numerals, and the description is omitted. As shown in FIG. 12, the heat storage heat exchanger 55
, Heat storage medium 56, heat storage heat exchanger 55 and heat storage medium 5
6, a heat storage tank 57 for storing therein, a refrigerant gas pump 58,
A heat storage four-way valve 59 and opening / closing mechanisms 60, 61 and 62 are provided. As the heat storage medium 56, for example, water is used. The refrigerant-refrigerant heat exchanger 53, the third expansion device 51, the heat storage heat exchanger 55, and the opening / closing mechanism 62 are connected by a refrigerant pipe 110, one end of which is a high-pressure receiver 42 and the other end of which is a load-side heat exchanger 34. And a pipe between the four-way valve 54. Further, the heat storage four-way valve 59 and the gas pump 58 are connected by bypassing the opening / closing mechanism 62, and the ends thereof are connected to pipes before and after the opening / closing mechanism 62 via the opening / closing mechanisms 60 and 61.

The cold storage operation, that is, the operation for making ice will be described. 12, the opening and closing mechanisms 60 and 61 are closed, the opening and closing mechanism 62 is opened, and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 is condensed in the heat-source-side heat exchanger 32 and is slightly throttled by the sub-throttle device 41 before reaching the high-pressure receiver 42. When the high-pressure receiver 42 is filled with the liquid refrigerant, the liquid refrigerant is guided to the pipe 110 and is passed through the refrigerant-refrigerant heat exchanger 53 to the third throttle device 5.
1 narrows down to low pressure. At this time, the main throttle device 33 is opened and closed appropriately, and the refrigerant pipe 1
The degree of supercooling of the refrigerant flowing through 10 is adjusted. The low-temperature two-phase refrigerant throttled to a low pressure by the third expansion device 51 takes heat from the heat storage medium 56 in the heat storage tank 57, freezes the heat storage medium 56, and vaporizes itself. The vaporized refrigerant returns to the compressor 31 via the four-way valve 54 and the low-pressure receiver 35. FIG. 14 shows an example of the heat storage operation.

As shown in FIG. 14, the cooling operation, that is, the cooling operation by cooling the cold storage heat will be described. The opening and closing mechanisms 60 and 61 are opened, the opening and closing mechanism 62 is closed, and the gas pump 58 is driven. The refrigerant discharged from the gas pump 58 reaches the heat storage heat exchanger 55 through the heat storage four-way valve 59, is cooled and condensed and liquefied by the heat storage medium in the heat storage tank 57, and is a liquid refrigerant of about 9 kgf / cm ² G. Becomes This liquid refrigerant is slightly throttled by the heat storage throttle device 51 and then flows into the high-pressure receiver 42. The liquid refrigerant led out from the high-pressure receiver 42 is throttled down to low pressure by the main throttle device 33 to become a low-temperature low-pressure two-phase refrigerant. After slightly absorbing heat in the refrigerant-refrigerant heat exchanger 53, the liquid refrigerant is transferred to the load-side heat exchanger 34. Reach. The low-temperature and low-pressure two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool it, evaporates and vaporizes itself, and the heat storage four-way valve 5.
9 and return to the gas pump 58.

As shown in FIG. 12, the general cooling operation, that is, the operation of cooling only by the compressor 31 without using the cold storage heat will be described. The opening and closing mechanisms 60, 61 and 62 are closed, and the compressor 31 is driven. The refrigerant discharged from the compressor 31 reaches the heat source side heat exchanger 32 through the four-way valve 54, condensed and liquefied therein, is slightly throttled by the sub-throttle device 41, and flows into the high-pressure receiver 42. The liquid refrigerant discharged from the high-pressure receiver 42 is throttled down to a low pressure by the main throttle device 33 to become a low-temperature low-pressure two-phase refrigerant, and reaches the load-side heat exchanger 34.
The low-temperature low-pressure two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool it, evaporates itself, and returns to the compressor 31 through the four-way valve 54 and the low-pressure receiver 35. FIG. 15 shows an example of the general heating operation.

In general cooling as shown in FIG. 13, when the cooling load is light, the opening / closing mechanism 62 is opened and the high-pressure receiver 42 is opened.
A gas refrigerant rich in components having a low boiling point from the upper part
Lead to. The gas refrigerant rich in the low boiling point component releases heat in the refrigerant-refrigerant heat exchanger 53 and condenses, and is condensed by the heat storage expansion device. Since the refrigerant flowing through the refrigerant pipe 110 is rich in low boiling point components, the temperature of the refrigerant throttled by the heat storage expansion device can be lower than the evaporation temperature of the load-side heat exchanger 34, and the heat storage heat exchanger At 55, the heat storage medium 56 in the heat storage tank 57 is frozen by removing heat from the surroundings, and the storage medium 56 itself can perform cold storage heat while cooling by evaporating.

Referring to FIG. 13, a description will be given of a cooling operation combined with cold storage in which the general cooling operation and the cooling operation are simultaneously performed.
The opening and closing mechanisms 60 and 61 are opened, the opening and closing mechanism 62 is closed, and the compressor 31 and the gas pump 58 are driven. At this time, the liquid refrigerant condensed in the heat storage heat exchanger 55 on the gas pump 58 side is:
The refrigerant discharged from the compressor 31 and joined by the high-pressure receiver 42 with the refrigerant decompressed by the sub-throttling device 41 is further decompressed to a low pressure by the throttling device 33 and reaches the load-side heat exchanger 34.
While taking heat from the surroundings and cooling, it evaporates itself. The refrigerant vaporized in the load side heat exchanger 34 is divided into two parts, one of which returns to the compressor 31 through the four-way valve 54 and the low-pressure receiver 35, and the other returns to the gas pump 58 through the four-way valve 59 for heat storage. FIG. 15 shows an example of combined heating and heating.

This refrigeration / air-conditioning apparatus has a high-pressure receiver 42
In, the liquid refrigerant rich in the high boiling point component and the gas refrigerant rich in the low boiling point component are divided, and the liquid refrigerant rich in the high boiling point component is once squeezed into a low-pressure gas-liquid two-phase refrigerant, and then rich in the low boiling point component. The liquid refrigerant is heat-exchanged with the gas refrigerant to be liquefied, and the liquid refrigerant rich in low-boiling components is squeezed to form a low-pressure gas-liquid two-phase state. Thus, by obtaining a low-pressure two-phase refrigerant rich in high-boiling components and a low-pressure two-phase refrigerant rich in low-boiling components, evaporation temperatures having different temperatures are obtained, and when the cooling load is light, heat is stored in the heat storage tank 57. When energy is stored and the load is high, air conditioning can be performed using the heat storage energy stored in the heat storage tank 57 by driving the gas pump 58.

Embodiment 13 FIG. 16 to 18 are refrigerant circuit diagrams showing Embodiment 13 of the present invention. In the figure, 31
Is a compressor, 54 is a four-way valve, 32 is a heat source side heat exchanger, 41
Is a sub-throttle device, 42 is a high-pressure receiver, 33 is a main throttle device, 53 is a refrigerant-refrigerant heat exchanger, 63 is a first heat storage heat exchanger, 73 is a third throttle device, and 34 is load-side heat exchange. And a low-pressure receiver 35, which is connected in sequence to form a main refrigerant circuit. 51 is a heat storage throttle device,
64 is a second heat storage heat exchanger, which is connected by a refrigerant pipe 111, and has one end connected to the upper part of the high-pressure receiver and the other end connected to the refrigerant pipe between the load side heat exchanger 34 and the four-way valve 54. . An opening / closing mechanism 6 is provided at one end of the first heat storage heat exchanger 56.
8, an open / close mechanism 69 is provided at the other end, and open / close mechanisms 65 and 66 are provided at one end of the second heat storage heat exchanger 64, and open / close mechanisms 70 and 71 are provided at the other end. 112 is an opening / closing mechanism 65
And a piping between the opening and closing mechanism 68 and the main throttle device 33 via an opening and closing mechanism 67. Reference numeral 113 denotes a refrigerant pipe that connects a pipe between the opening / closing mechanisms 70 and 71 and a pipe between the opening / closing mechanism 69 and the load-side heat exchanger via an opening / closing mechanism 72.

The operation of cold storage, that is, the operation of making ice will be described. 16, the opening / closing mechanism 65 is closed, and the opening / closing mechanisms 66, 67, 68, 69, 70, 71, and 72 are opened, and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 is condensed in the heat-source-side heat exchanger 32 and is slightly throttled by the sub-throttle device 41 before reaching the high-pressure receiver 42. When the high-pressure receiver 42 is filled with the liquid refrigerant, the liquid refrigerant is guided to the pipe 111 and is throttled to a low pressure by the third throttle device 51 via the refrigerant-refrigerant heat exchanger 53. At this time, the main throttle device 33 opens and closes appropriately, and the refrigerant-
In the refrigerant heat exchanger 53, the degree of supercooling of the refrigerant flowing through the refrigerant pipe 110 is adjusted. The low-temperature two-phase refrigerant compressed to a low pressure by the third expansion device 51 is diverted to the first heat storage heat exchanger and the second heat storage heat exchanger, and from the heat storage medium 56 in the heat storage tank 57. The heat is taken away, the heat storage medium 56 is frozen, and the heat storage medium 56 itself evaporates. The vaporized refrigerant returns to the compressor 31 via the four-way valve 54 and the low-pressure receiver 35. FIG. 17 shows the heat storage operation.

The cooling operation will be described. As shown in FIG. 16, opening / closing mechanisms 65, 66, 67, 70, 71 and 72 are provided.
Is closed, the opening and closing mechanisms 68 and 69 are opened, and the compressor 31 is driven. The refrigerant discharged from the compressor 31 is supplied to the four-way valve 54.
After passing through the heat source side heat exchanger 32, the condensed liquid is condensed and liquefied. The liquid refrigerant derived from the high-pressure receiver 42 takes heat from the heat storage medium in the first heat storage heat exchanger 63 to increase the degree of supercooling, and is throttled to a low pressure by the third expansion device 73 to be cooled to a low temperature and low pressure. It becomes a two-phase refrigerant and reaches the load-side heat exchanger 34. The low-temperature low-pressure two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool it, evaporates itself, and returns to the compressor 31 through the four-way valve 54 and the low-pressure receiver 35. FIG. 18 shows the heating operation.

In the cooling operation, when the cooling load is light, the opening / closing mechanisms 65, 66, 70 and 71 are opened as shown in FIG. 17, and the high-pressure receiver 42 guides the gas refrigerant rich in low-boiling components to the refrigerant pipe 111. At this time, the main aperture device 3
3 is narrowed tightly, and a low-temperature low-pressure two-phase refrigerant rich in a high-boiling-point refrigerant is guided to a refrigerant-refrigerant heat exchanger. The gas refrigerant rich in low-boiling components guided from the high-pressure receiver 42 to the refrigerant pipe 111 radiates heat in the refrigerant-refrigerant heat exchanger 53, condenses, and is condensed by the heat storage restrictor. Since the refrigerant flowing through the refrigerant pipe 111 is rich in low boiling point components, the temperature of the refrigerant throttled by the heat storage expansion device 51 can be lower than the evaporation temperature of the load-side heat exchanger 34, and the second heat storage The heat storage medium 5 in the heat storage tank 57 by removing heat from the surroundings.
6 freezes and evaporates itself.

This refrigeration / air-conditioning apparatus is provided with a high-pressure receiver 42
In, the liquid refrigerant rich in the high boiling point component and the gas refrigerant rich in the low boiling point component are divided, and the liquid refrigerant rich in the high boiling point component is once squeezed into a low-pressure gas-liquid two-phase refrigerant, and then rich in the low boiling point component. The liquid refrigerant is heat-exchanged with the gas refrigerant to be liquefied, and the liquid refrigerant rich in low-boiling components is squeezed to form a low-pressure gas-liquid two-phase state. Thus, by obtaining a low-pressure two-phase refrigerant rich in high-boiling components and a low-pressure two-phase refrigerant rich in low-boiling components, evaporation temperatures having different temperatures are obtained, and when the cooling load is light, heat is stored in the heat storage tank 57. Energy can be stored, and the degree of supercooling of the refrigerant flowing through the main circuit can be increased by the heat storage energy stored in the heat storage tank 57.

In Embodiments 12 and 13 described above, the heat exchanger 53 has the function of condensing low-boiling components. As a result, the evaporation temperature of the load side heat exchanger 34 and the heat storage heat exchanger 55 is changed to enable air conditioning while storing (cooling) ice. (Evaporation temperature of cold storage −5 to 0 ° C., air conditioning 5 to 10 ° C.) Thus, for example, it is possible to perform cold storage (ice making) while air conditioning. Further, the effect of the low-pressure receiver 35 is that the circulating composition can be made rich in low-boiling components by storing the liquid in the low-pressure receiver 35. That is, the capacity is increased due to the increase in the refrigerant circulation amount. At this time, the high-pressure receiver 42
The surplus refrigerant amount of the low-pressure receiver 35 is adjusted, and gas-liquid separation is performed.

Embodiment 14 FIG. Hereinafter, a fourteenth embodiment of the present invention will be described with reference to FIG. In the figure, 31 is a compressor, 40 is a four-way valve, 32 is a heat source side heat exchanger, 41 is a sub-throttle device, 42 is a high-pressure receiver, 33 is a main throttle device, 34
Denotes a load-side heat exchanger, and 35 denotes a low-pressure receiver, which are sequentially connected by a refrigerant pipe to form a refrigerant main circuit. 7
Reference numeral 9 denotes an intermediate-pressure receiver, which is connected to the upper part of the high-pressure receiver 42 through the third expansion device 80 of the intermediate-pressure receiver 79 and the refrigerant pipe 114. 75 is a fourth diaphragm device, 76
Denotes an opening / closing mechanism, which is connected by a refrigerant pipe, and has one end connected to the upper part of the intermediate pressure receiver 79 and the other end connected to the suction pipe of the low pressure receiver 35. 77 is a low-temperature heat source, 78 is a high-temperature heat source, and the temperature can be adjusted. FIG. 19 shows the flow of the refrigerant.

The cooling operation will be described. Opening / closing mechanism 76
Is closed, and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. At the same time, the vaporizer vaporizes and returns to the compressor 31 through the four-way valve 40 and the low-pressure receiver 35.

To change the composition of the refrigerant flowing in the refrigerant circuit, the opening / closing mechanism 76 is opened, and the gas refrigerant rich in the high boiling point component is supplied from the upper part of the high-pressure receiver 42 through the refrigerant pipe 114 through the third expansion device 80. To the intermediate pressure receiver 79. In the intermediate pressure receiver 79, a predetermined temperature is set by a low-temperature heat source to condense the refrigerant gas. As a result,
The intermediate-pressure receiver 79 stores a liquid refrigerant rich in low-boiling components, and the uncondensed gas enters the low-pressure receiver 35 through the refrigerant pipe 115. Therefore, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

This will be described with reference to the relationship between the ratio of the mixed components and the temperature. FIG. 20 is a graph showing the relationship between the ratio of the mixed components and the temperature. The vertical axis represents the temperature, the horizontal axis represents the ratio between the high-boiling component and the low-boiling component, and g1 represents a high-pressure saturated gas.
L1 indicates a state of a high-pressure liquid, g2 indicates a state of a medium-pressure saturated gas, and L2 indicates a state of a medium-pressure liquid. Assuming that the refrigerant circuit is initially filled with the refrigerant having the composition A, the state of the refrigerant in the high-pressure receiver 42 is separated into a gas refrigerant having a composition of G _H and a liquid refrigerant having a composition of L _H. Further, gas refrigerant having a composition of this G _H is at an intermediate pressure receiver within 79, is separated into a liquid refrigerant having the composition L _M. Therefore, in the intermediate-pressure receiver 79, a refrigerant rich in components having a lower boiling point than the composition of the filled refrigerant can be stored.

In order to make the refrigerant flowing in the main refrigerant circuit rich in low boiling point components, the opening and closing mechanism 76
Is opened, and the refrigerant inside the intermediate pressure receiver 79 is evaporated by the high-temperature heat source. When the opening / closing mechanism 76 is closed after the evaporation, the excess refrigerant rich in high-boiling components is accumulated in the low-pressure receiver, so that the composition of the refrigerant circulating in the main circuit can be rich in low-boiling components.

The high-temperature heat source 78 of this embodiment includes an electric heater, a gas discharged from the compressor 31 and a high-pressure refrigerant liquid, and the low-temperature heat source 77 uses cold water and a low-temperature and low-pressure two-phase refrigerant. can do.

This refrigeration / air-conditioning apparatus is provided with an intermediate pressure receiver 7.
By controlling the temperature and pressure in the refrigerant 9, the composition of the refrigerant accumulated at the intermediate pressure is changed, and the composition of the refrigerant circulating in the refrigerant circuit is changed.

Embodiment 15 FIG. Hereinafter, a fifteenth embodiment of the present invention will be described with reference to FIG. In the figure, 31 is a compressor, 40 is a four-way valve, 32 is a heat source side heat exchanger, 41 is a sub-throttle device, 83 is a high-pressure composition adjuster, 33 is a main throttle device, 3
Reference numeral 4 denotes a load-side heat exchanger, and reference numeral 35 denotes a low-pressure receiver, which are sequentially connected by a refrigerant pipe to form a main circuit of the refrigerant.
Reference numeral 84 denotes an intermediate pressure composition adjuster.
Is connected to a high-pressure upper composition adjuster through a third expansion device via a refrigerant pipe 117. Reference numeral 82 denotes a third expansion device, which is installed on the refrigerant pipe 118, and has one end connected to the upper part of the intermediate-pressure composition regulator 84 and the other end connected to the suction pipe of the low-pressure receiver 35. Reference numerals 116a and 116b denote low-temperature heat sources connected to the upper portions of the intermediate-pressure composition regulator 84 and the high-pressure composition regulator 83, respectively, and the temperature can be appropriately adjusted. 81 is a high-temperature heat source installed in the intermediate-pressure composition adjuster 84.

The cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat-source-side heat exchanger 32 enters the high-pressure composition adjuster 83 after being slightly throttled by the sub-throttle device 41. The gas-liquid is separated by the high-pressure composition adjuster 83,
The liquid refrigerant is decompressed to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 and cools, and also evaporates and vaporizes to form a four-way valve 40. And returns to the compressor 31 through the low-pressure receiver 35.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant dissipates heat to the surroundings in the load side heat exchanger 34 to heat it, condenses itself, and is slightly throttled by the main throttle device 33.
to go into. Gas-liquid is separated by the high-pressure composition controller 83, the liquid refrigerant is reduced in pressure to a low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant is cooled by the heat source side heat exchanger 32 from the surroundings. After being robbed and vaporized, it returns to the compressor 31 through the four-way valve 40 and the low-pressure receiver.

To change the composition of the refrigerant flowing in the refrigerant circuit, the opening / closing mechanism 76 is opened, and a gas refrigerant rich in low-boiling components is supplied from the upper part of the high-pressure composition controller 83 to the refrigerant pipe 11.
7 flows to the intermediate pressure composition regulator 84. At this time, the gas refrigerant rich in low-boiling components exchanges heat with the low-temperature heat source 116b before reaching the upper part of the high-pressure composition controller 83, and the refrigerant rich in high-boiling components is condensed and liquefied. The gas refrigerant falls to the lower part, and the gas refrigerant rich in low-boiling components, which has been rectified to some extent, remains in the upper part of the high-pressure composition controller 83. The gas refrigerant rich in the low boiling point component is guided to the lower part of the intermediate pressure composition regulator 84, and further, when ascending inside the intermediate pressure composition regulator 84, exchanges heat with the low temperature heat source 116a to condense and liquefy. It is stored in the lower part of the regulator 80. The uncondensed gas is guided to the suction side of the low-pressure receiver 35 via the third throttle device 82 and the opening / closing mechanism 76. As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

In order to make the refrigerant flowing through the main refrigerant circuit rich in low boiling point components, the opening and closing mechanism 76
Is opened, and the refrigerant inside the intermediate-pressure composition controller is evaporated by the high-temperature heat source 81. After the evaporation, when the opening / closing mechanism 76 is closed,
Excess refrigerant rich in high-boiling components accumulates in the low-pressure receiver,
Therefore, the composition of the refrigerant circulating in the main circuit can be rich in low-boiling components.

The high-temperature heat source 81 of this embodiment includes an electric heater, a compressor discharge gas, and a high-pressure refrigerant liquid, and the low-temperature heat sources 116a and 116b use cold water and low-temperature and low-pressure two-phase refrigerant. Can be used.

This refrigeration / air-conditioning apparatus is provided with a high-pressure receiver 42
In, the liquid refrigerant rich in high-boiling point refrigerant and the gas refrigerant rich in low-boiling point refrigerant are divided in advance, rectified by the rectifying heat source unit in the intermediate pressure composition regulator, and a high boiling point refrigerant or a low boiling point refrigerant is selected. As a result, the composition of the refrigerant flowing through the main circuit can be adjusted.

19 and 21, the low-voltage receiver 35
Stores a high-boiling component refrigerant. Further, the low-pressure receiver 35 stores liquid when the load is heavy. Also, high-pressure receiver 4
2 performs gas-liquid separation. The intermediate-pressure receiver 79 stores the low-boiling-point component refrigerant and stores the liquid when the load is light. As can be seen in the phase diagram of FIG.
The composition of the refrigerant gas and the liquid in the chamber is different, and the composition of the refrigerant gas 1
2. Low boiling point component becomes rich. Therefore, the composition can be adjusted by taking the low-boiling-point-rich gas into the intermediate-pressure receiver 79 and condensing it. As shown in FIGS. 19 and 21, by providing the intermediate pressure receiver 79, a refrigerant having a certain composition can be reliably confined in the intermediate pressure receiver 79, so that a transient phenomenon (such as defrost) occurs after the composition adjustment, Even if a change occurs in the refrigerant amount distribution in the circuit, the composition is unlikely to change. The reason for providing the low-temperature heat source is as follows. 1. Increase the speed of condensation It is to condense even low-boiling components that are difficult to condense.

Embodiment 16 FIG. Hereinafter, a sixteenth embodiment of the present invention will be described with reference to FIG. In the figure, 31 is a compressor, 40 is a four-way valve, 32 is a heat source side heat exchanger, 41 is a sub-throttle device, 42 is a high-pressure receiver, 33 is a main throttle device, 34
Denotes a load-side heat exchanger, and 35 denotes a low-pressure receiver, which are sequentially connected by a refrigerant pipe to form a refrigerant main circuit. 8
Reference numeral 4 denotes an intermediate pressure composition adjuster. The intermediate pressure composition adjuster 84 is connected to the upper part of the high-pressure receiver 42 via an opening / closing mechanism 85 via an opening / closing mechanism 85 and connected to the refrigerant pipe 120 via an opening / closing mechanism 86. The lower part of the high-pressure receiver 42 is connected to the lower part of the intermediate pressure composition adjuster 84. Reference numeral 82 denotes a third expansion device, which is installed on the refrigerant pipe 121, and has one end connected to the upper part of the intermediate-pressure composition regulator 84 and the other end connected to the suction pipe of the low-pressure receiver 35. 116a is a low-temperature heat source connected to the upper part of the intermediate pressure composition adjuster 84, and 81 is a low temperature heat source
4, and the temperature can be adjusted appropriately.

The cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.

Next, the heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31.

In the case of changing the composition of the refrigerant flowing in the refrigerant circuit, first, a method of storing a gas refrigerant rich in low-boiling components in the intermediate-pressure composition regulator 84 will be described. The opening / closing mechanisms 76 and 86 are opened, and a gas refrigerant rich in low-boiling components flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 120 to the lower part of the intermediate-pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is guided to the suction side of the low-pressure receiver 35 via the third throttle device 82 and the opening / closing mechanism 76. As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method of storing a refrigerant rich in a high boiling point component in the intermediate pressure composition controller 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4. When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates and becomes a gas refrigerant rich in low-boiling components and rises.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

The high-temperature heat source 81 of this embodiment includes an electric heater, a compressor discharge gas, and a high-pressure refrigerant liquid, and the low-temperature heat sources 116a and 116b use cold water and low-temperature and low-pressure two-phase refrigerant. can do.

Embodiment 17 FIG. Hereinafter, a seventeenth embodiment of the present invention will be described with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor 200 for detecting the temperature at the center of the load side heat exchanger 34; A temperature sensor 201 for measuring a pipe temperature between the exchanger 34 and the main throttle device 33,
A temperature sensor 202 for measuring a pipe temperature between the load-side heat exchanger 34 and the four-way valve 40, and control for calculating the opening of the main throttle device 33 and the sub-throttle device 41 based on information from the temperature sensor and adjusting the opening. The vessel 203 is added.

Next, the cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.
Here, the opening degree of the main throttle device 33 is determined by the temperature sensors 201 and 2.
02 is controlled so as to be constant.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31. Here, the opening degree of the sub-throttle device 41 is controlled so that the difference between the temperature sensors 200 and 201 is constant.

In the case where the composition of the refrigerant flowing in the refrigerant circuit is changed, first, a method of storing a refrigerant rich in low-boiling components in the intermediate-pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method for storing a refrigerant rich in a high boiling point component in the intermediate pressure composition controller 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4. When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates and becomes a gas refrigerant rich in low-boiling components and rises.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

The high-temperature heat source 81 of this embodiment includes an electric heater, a compressor discharge gas, and a high-pressure refrigerant liquid, and the low-temperature heat sources 116a and 116b use cold water and low-temperature and low-pressure two-phase refrigerant. can do.

Embodiment 18 FIG. Hereinafter, an eighteenth embodiment of the present invention will be described with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor 200 for detecting the temperature at the center of the load side heat exchanger 34; A temperature sensor 201 for measuring a pipe temperature between the exchanger 34 and the main throttle device 33,
A temperature sensor 202 for measuring a pipe temperature between the load-side heat exchanger 34 and the four-way valve 40; a refrigerant circuit 122 from the lower part of the high-pressure receiver to the low-pressure receiver 35 through the saturation temperature detecting throttle device 87; Temperature sensor 2 for detecting the temperature of the pipe between the expansion device 87 and the low-pressure receiver 35
03 and the information from the temperature sensor, the opening of the main throttle device 33 and the sub-throttle device 41 is calculated, and a controller 203 for adjusting the opening is added.

Next, the cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.
Here, the opening degree of the main throttle device 33 is determined by the temperature sensors 202 and 2.
03 is controlled to be constant.

Next, the heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31. Here, the opening degree of the sub-throttle device 41 is controlled so that the difference between the temperature sensors 200 and 201 is constant.

In the case where the composition of the refrigerant flowing in the refrigerant circuit is changed, first, a method of storing a refrigerant rich in low boiling point components in the intermediate pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method of storing a refrigerant rich in high-boiling components in the intermediate-pressure composition controller 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4. When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates and becomes a gas refrigerant rich in low-boiling components and rises.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

The high-temperature heat source 81 of this embodiment includes an electric heater, a compressor discharge gas, and a high-pressure refrigerant liquid, and the low-temperature heat sources 116a and 116b use cold water and low-temperature and low-pressure two-phase refrigerant. can do.

Embodiment 19 FIG. Hereinafter, a nineteenth embodiment of the present invention will be described with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor 201 for measuring a pipe temperature between the load side heat exchanger 34 and the main expansion device 33 is provided. , A temperature sensor 202 and a pressure sensor 204 for measuring a pipe temperature and a pressure between the load side heat exchanger 34 and the four-way valve 40, and a low-pressure receiver 35
Means 216 for detecting the amount of surplus refrigerant inside, and calculating the composition of the refrigerant circulating in the refrigerant circuit from the information on the amount of surplus refrigerant, and the main throttle device 33 from the information on the pressure sensor, the temperature sensor and the circulating composition. And a controller 203 for calculating the opening of the sub-throttle device 41 and adjusting the opening is added.

Next, the cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.

The opening of the main throttle device 33 is controlled as follows. First, by detecting the liquid level in the low-pressure receiver 35, the amount of surplus refrigerant generated in the low-pressure receiver 35 is recognized, and the composition of the refrigerant flowing in the refrigerant circuit (hereinafter, referred to as circulation composition) is determined based on the surplus refrigerant amount. Predict. The relationship between saturation temperature and pressure is derived from the predicted circulation composition. As a result, the opening degree of the main throttle device 33 is determined so that the difference between the evaporation temperature derived from the pressure sensor 204 and the temperature measured by the temperature sensor 202 is constant.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The gas returns to the compressor 31 through the four-way valve 40 and the low-pressure receiver. Here, the opening degree of the sub-throttle device 41 is controlled so that the difference between the temperature sensors 200 and 201 is constant.

The opening of the main throttle device 33 is controlled as follows. First, by detecting the liquid level in the low-pressure receiver 35, the amount of excess refrigerant generated in the low-pressure receiver is recognized, and the circulation composition is predicted from the amount of excess refrigerant. The relationship between saturation temperature and pressure is derived from the predicted circulation composition. As a result,
So that the difference between the condensation temperature derived from the pressure sensor 204 and the temperature measured by the temperature sensor 201 is constant.
The opening of the sub-throttle device 41 is determined.

In the case where the composition of the refrigerant flowing in the refrigerant circuit is changed, first, a method of storing a refrigerant rich in low boiling point components in the intermediate pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method for storing a refrigerant rich in a high boiling point component in the intermediate pressure composition controller 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4. When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates and becomes a gas refrigerant rich in low-boiling components and rises.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

The high-temperature heat source 81 of this embodiment includes an electric heater, a compressor discharge gas, and a high-pressure refrigerant liquid, and the low-temperature heat sources 116a and 116b use cold water and low-temperature and low-pressure two-phase refrigerant. can do. In the above description, the method of detecting the surplus refrigerant in the low-pressure receiver 35 can be predicted, for example, based on the amount of refrigerant required for cooling and heating.

Embodiment 20 FIG. Hereinafter, a twentieth embodiment of the present invention will be described with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor for measuring a pipe temperature and a pressure between the load side heat exchanger 34 and the main expansion device 33. 201 and a pressure sensor 204; a temperature sensor 202 for measuring a pipe temperature between the load side heat exchanger 34 and the four-way valve 40; a temperature sensor 205 for measuring a pipe temperature and pressure between the high-pressure receiver 42 and the main throttle device 33; The composition of the refrigerant circulating in the refrigerant circuit is calculated from the pressure sensor 206 and the information on the pressure and the temperature, and the opening of the main throttle device 33 and the sub-throttle device 41 is calculated from the pressure sensor, the temperature sensor and the information on the circulating composition. A controller 203 for calculating the degree and adjusting the opening is added.

Next, the cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.

Here, the opening of the main throttle device 33 is controlled as follows. First, a circulation composition is assumed, and the temperature sensors 201 and 205 and the pressure sensor 2 are used by using the circulation composition.
The enthalpy of the refrigerant before and after the main throttle device is calculated from 04 and 206. The assumption of the circulation composition is repeated until the enthalpies become equal to determine the circulation composition. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition is recognized, and the main throttle is set so that the difference between the evaporation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 202 is constant. The opening of the device 33 is controlled.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31.

Here, the opening of the sub-throttle device 41 is controlled as follows. First, a circulation composition is assumed, and using this circulation composition, the temperature sensors 201 and 202 and the pressure sensor 2 are used.
The enthalpy of the refrigerant before and after the main throttle device is calculated from 04 and 206. The assumption of the circulation composition is repeated until the enthalpies become equal to determine the circulation composition. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition is recognized, and the sub-throttler is set so that the difference between the condensation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 201 is constant. The opening of the device 41 is controlled.

In the case of changing the composition of the refrigerant flowing in the refrigerant circuit, first, a method of storing the refrigerant having a low boiling point component in the intermediate pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method for storing a refrigerant rich in high-boiling components in the intermediate-pressure composition controller 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4. When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates and becomes a gas refrigerant rich in low-boiling components and rises.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

Here, the circulating composition is predicted by the above-described method for estimating the circulating composition, the above-described composition adjustment is performed according to the magnitude of the load, and the time of the composition adjustment is controlled.

Embodiment 21 FIG. Hereinafter, the twenty-first embodiment of the present invention will be described with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor for measuring a pipe temperature and a pressure between the load side heat exchanger 34 and the main expansion device 33. 201 and a pressure sensor 204; a temperature sensor 202 for measuring a pipe temperature between the load side heat exchanger 34 and the four-way valve 40; a temperature sensor 205 for measuring a pipe temperature and pressure between the high-pressure receiver 42 and the main throttle device 33; The composition of the refrigerant circulating in the refrigerant circuit is calculated from the pressure sensor 206 and the information on the pressure and the temperature, and the opening of the main throttle device 33 and the sub-throttle device 41 is calculated from the pressure sensor, the temperature sensor and the information on the circulating composition. A controller 203 for calculating the degree and adjusting the opening is added.

[0164] The cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.

The opening of the main throttle device 33 is controlled as follows. First, the main throttle device 33 and the load side heat exchanger 3
Suppose the dryness of the refrigerant between 4 is 0.2. The circulation composition is estimated by the temperature sensor 201 and the pressure sensor 204. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition is recognized, and the main throttle is set so that the difference between the evaporation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 202 is constant. The opening of the device 33 is controlled.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31.

Here, the opening of the sub-throttle device 41 is controlled as follows. First, a circulation composition is assumed, and using this circulation composition, the temperature sensors 201 and 202 and the pressure sensor 2 are used.
The enthalpy of the refrigerant before and after the main throttle device is calculated from 04 and 206. The assumption of the circulation composition is repeated until the enthalpies become equal to determine the circulation composition. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition is recognized, and the sub-throttler is set so that the difference between the condensation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 201 is constant. The opening of the device 41 is controlled.

When the composition of the refrigerant flowing in the refrigerant circuit is changed, first, a method of storing the refrigerant rich in low boiling point components in the intermediate pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method for storing a refrigerant rich in a high boiling point component in the intermediate pressure composition controller 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4. When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates and becomes a gas refrigerant rich in low-boiling components and rises.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

Here, the circulating composition is predicted by the above-described method for estimating the circulating composition, the above-described composition adjustment is performed according to the magnitude of the load, and the time of the composition adjustment is controlled.

Embodiment 22 FIG. Hereinafter, a twenty-second embodiment of the present invention will be described with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor for measuring a pipe temperature and a pressure between the load side heat exchanger 34 and the main expansion device 33. 201 and a pressure sensor 204; a temperature sensor 202 for measuring a pipe temperature between the load side heat exchanger 34 and the four-way valve 40; a temperature sensor 205 for measuring a pipe temperature and pressure between the high-pressure receiver 42 and the main throttle device 33; The composition of the refrigerant circulating in the refrigerant circuit is calculated from the pressure sensor 206 and the information on the pressure and the temperature, and the opening of the main throttle device 33 and the sub-throttle device 41 is calculated from the pressure sensor, the temperature sensor and the information on the circulating composition. A controller 203 for calculating the degree and adjusting the opening is added.

[0172] The cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.

Here, the opening of the main throttle device 33 is controlled as follows. First, the main throttle device 33 and the load side heat exchanger 3
Suppose the dryness of the refrigerant between 4 is 0.2. The circulation composition is estimated by the temperature sensor 201 and the pressure sensor 204. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition is recognized, and the main throttle is set so that the difference between the evaporation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 202 is constant. The opening of the device 33 is controlled.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31.

Here, the opening of the main throttle device 33 is controlled as follows. First, the main diaphragm device 33 and the high-pressure receiver 42
It is assumed that the dryness of the refrigerant during the period is zero. Temperature sensor 205
And the pressure sensor 206 to estimate the circulation composition.
Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition is recognized, and the main throttle is set so that the difference between the evaporation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 201 is constant. The opening of the device 33 is controlled.

In the case of changing the composition of the refrigerant flowing in the refrigerant circuit, first, a method of storing the refrigerant having a low boiling point component in the intermediate pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method of storing a refrigerant rich in a high boiling point component in the intermediate pressure composition regulator 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4. When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates and becomes a gas refrigerant rich in low-boiling components and rises.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

Here, the circulating composition is predicted by the above-described method for estimating the circulating composition, the above-described composition adjustment is performed according to the magnitude of the load, and the time of the composition adjustment is controlled.

Embodiment 23 FIG. Hereinafter, a twenty-third embodiment of the present invention will be described with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor for measuring a pipe temperature and a pressure between the load side heat exchanger 34 and the main expansion device 33. 201 and a pressure sensor 204; a temperature sensor 202 for measuring a pipe temperature between the load side heat exchanger 34 and the four-way valve 40; and a temperature sensor 207 and a pressure sensor 208 on the suction side of the low-pressure receiver 35.
And the composition of the refrigerant circulating in the refrigerant circuit is calculated from the information on the pressure and the temperature, and the opening degree of the main throttle device 33 and the sub-throttle device 41 is calculated from the information of the pressure sensor, the temperature sensor and the circulating composition. Then, a controller 203 for adjusting the opening is added.

Next, the cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.

Here, the opening of the main throttle device 33 is controlled as follows. First, it is assumed that the dryness of the refrigerant in the suction of the low-pressure receiver 35 is in the range of 0.9 to 1.0. The circulation composition is estimated by the temperature sensor 207 and the pressure sensor 208. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition is recognized, and the main throttle is set so that the difference between the evaporation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 202 is constant. The opening of the device 33 is controlled.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31.

Here, the opening degree of the sub-throttle device 41 is controlled as follows. First, it is assumed that the dryness of the refrigerant in the suction of the low-pressure receiver 35 is in the range of 0.9 to 1.0. next,
Recognizing the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition, the condensing temperature predicted from the measurement value of the pressure sensor 204, and the auxiliary throttle device 41 Control the opening.

In changing the composition of the refrigerant flowing in the refrigerant circuit, first, a method of storing a refrigerant rich in low boiling point components in the intermediate pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method of storing a refrigerant rich in a high boiling point component in the intermediate pressure composition controller 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4. When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates and becomes a gas refrigerant rich in low-boiling components and rises.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

Here, the circulating composition is predicted by the method for estimating the circulating composition described above, and the above-described composition adjustment is performed depending on the magnitude of the load, and the time of the composition adjustment is controlled.

Embodiment 24 FIG. Embodiment 24 of the present invention will be described below with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor for measuring a pipe temperature and a pressure between the load side heat exchanger 34 and the main expansion device 33. 201 and a pressure sensor 204; a temperature sensor 202 for measuring a pipe temperature between the load side heat exchanger 34 and the four-way valve 40; a temperature sensor 209 and a pressure sensor 210 for detecting the saturation temperature and pressure of the refrigerant inside the high-pressure receiver 42; Calculate the composition of the refrigerant circulating in the refrigerant circuit from the pressure and temperature information, and
An opening of the main throttle device 33 and the sub-throttle device 41 is calculated from the information of the pressure sensor, the temperature sensor and the circulating composition, and a controller 203 for adjusting the opening is added.

The cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.

Here, the opening of the main throttle device 33 is controlled as follows. First, since the liquid level of the refrigerant exists inside the high-pressure receiver 42 and is in a saturated state, the circulation composition can be estimated by the temperature sensor 209 and the pressure sensor 210. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the predicted circulation composition is recognized, and the pressure sensor 204
Of the evaporation temperature predicted from the measured value of
The opening degree of the main throttle device 33 is controlled so that the difference between the measured values of the constants is constant.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31.

Here, the opening of the sub-throttle device 41 is controlled as follows. First, since the liquid level of the refrigerant exists inside the high-pressure receiver 42 and is in a saturated state, the circulation composition can be estimated by the temperature sensor 209 and the pressure sensor 210. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the predicted circulation composition is recognized, and the pressure sensor 204
Evaporation temperature predicted from the measured value of
The opening degree of the main throttle device 33 is controlled so that the difference between the measured values of the constants is constant.

In changing the composition of the refrigerant flowing in the refrigerant circuit, first, a method of storing a refrigerant rich in low boiling point components in the intermediate pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method for storing a refrigerant rich in a high boiling point component in the intermediate pressure composition regulator 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4 When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates, and rises as a gas refrigerant rich in low boiling point components.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

Here, the circulating composition is predicted by the above-described method for estimating the circulating composition, the above-described composition adjustment is performed according to the magnitude of the load, and the time of the composition adjustment is controlled. Also,
Here, the method of predicting the circulation composition by measuring the pressure and the temperature in the high-pressure receiver 42 has been described. However, the method of predicting the circulation composition by measuring the pressure and the temperature in the low-pressure receiver 35 is also described in the present embodiment. Including in the form.

Embodiment 25 FIG. Hereinafter, a twenty-fifth embodiment of the present invention will be described with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor for measuring a pipe temperature and a pressure between the load side heat exchanger 34 and the main expansion device 33. 201, a pressure sensor 204, a temperature sensor 202 for measuring a pipe temperature between the load side heat exchanger 34 and the four-way valve 40, a branch from the compressor 31 discharge side, a third expansion device 90 and a refrigerant heat exchanger 92. Refrigerant pipe 123 connected to the suction side of the low-pressure receiver 35 via the refrigerant pipe 123;
Between 0 and the suction of the low-pressure receiver 35, a temperature sensor 211 for measuring the pipe temperature, a pressure sensor 212 for measuring the compressor discharge pressure, and the composition of the refrigerant circulating in the refrigerant circuit is calculated from the pressure and temperature information. In addition, a controller 203 for calculating the opening of the main throttle device 33 and the sub-throttle device 41 from the information of the pressure sensor, the temperature sensor and the circulating composition and adjusting the opening is added.

Next, the cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.

Here, the opening degree of the main throttle device 33 is controlled as follows. First, the degree of dryness of the refrigerant inside the refrigerant pipe 123 is 0.1 to 0.1 in the vicinity of the measurement unit of the temperature sensor 211.
Assuming a range of 0.5, the circulation composition can be estimated by the temperature sensor 211 and the pressure sensor 212. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the predicted circulation composition is recognized, and the difference between the evaporation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 202 is constant. The opening degree of the main throttle device 33 is controlled.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31.

Here, the opening of the sub-throttle device 41 is controlled as follows. First, the degree of dryness of the refrigerant inside the refrigerant pipe 123 is 0.1 to
Assuming a range of 0.5, the circulation composition can be estimated by the temperature sensor 211 and the pressure sensor 212. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the predicted circulation composition is recognized, and the difference between the evaporation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 201 is constant. The opening degree of the sub-throttle device 41 is controlled.

In the case of changing the composition of the refrigerant flowing in the refrigerant circuit, first, a method of storing the refrigerant rich in low boiling point components in the intermediate pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method for storing a refrigerant rich in a high boiling point component in the intermediate pressure composition regulator 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4. When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates and becomes a gas refrigerant rich in low-boiling components and rises.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

Here, the circulating composition is predicted by the above-described method for estimating the circulating composition, the above-described composition adjustment is performed according to the magnitude of the load, and the time of the composition adjustment is controlled.

Embodiment 26 FIG. Hereinafter, a twenty-sixth embodiment of the present invention will be described with reference to FIG. In the figure, the same parts as those of the sixteenth embodiment are denoted by the same reference numerals, and the description is omitted. In the components of the sixteenth embodiment in FIG. 22, the main expansion device 33 and the auxiliary expansion device 41 are electronic expansion valves, and a temperature sensor for measuring a pipe temperature and a pressure between the load side heat exchanger 34 and the main expansion device 33. 201 and a pressure sensor 204; a temperature sensor 202 for measuring a pipe temperature between the load-side heat exchanger 34 and the four-way valve 40; and a branch from the bottom of the high-pressure receiver 42 to the low-pressure receiver 35 via the third expansion device 91. A connected refrigerant pipe 124 and a temperature sensor 2 that measures the pipe temperature and pressure between the third expansion device 91 and the low-pressure receiver 35 on the refrigerant pipe 124.
13 and the pressure sensor 214 and the composition of the refrigerant circulating in the refrigerant circuit from the information on the pressure and the temperature. The main throttle device 33 and the sub-throttle device 41 are obtained from the pressure sensor, the temperature sensor and the information on the circulating composition. , And a controller 203 for adjusting the opening is added.

The cooling operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the heat source side heat exchanger 32 through the four-way valve 40. The refrigerant condensed in the heat source side heat exchanger 32 is slightly throttled by the sub-throttle device 41 and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to a low pressure by the main expansion device 33, and the low-temperature two-phase refrigerant takes heat from the surroundings in the load-side heat exchanger 34 to cool the air. And evaporates and evaporates itself.
Returning to the compressor 31 through the 0 and the low pressure receiver 35.

Here, the opening of the main throttle device 33 is controlled as follows. First, in the refrigerant pipe 124, the dryness of the refrigerant downstream of the third expansion device 91 is assumed to be in the range of 0.1 to 0.5. Temperature sensor 213 and pressure sensor 21
4 to estimate the circulating composition. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition is recognized, and the main throttle is set so that the difference between the evaporation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 202 is constant. The opening of the device 33 is controlled.

The heating operation will be described. Opening / closing mechanism 76
Is closed and the compressor 31 is driven. The high-temperature and high-pressure gas refrigerant discharged from the compressor 31 enters the load-side heat exchanger 34 through the four-way valve 40. The high-temperature and high-pressure gas refrigerant radiates heat to the surroundings in the load-side heat exchanger 34 and heats it. The refrigerant condenses, is slightly throttled by the main throttle device 33, and then enters the high-pressure receiver 42. Gas-liquid is separated by the high-pressure receiver 42, the liquid refrigerant is reduced in pressure to the low pressure by the sub-throttle device 41, and the low-temperature two-phase refrigerant takes heat from the surroundings in the heat source side heat exchanger 32 and evaporates. The vaporized gas passes through the four-way valve 40 and the low-pressure receiver 35, and returns to the compressor 31.

Here, the opening degree of the sub-throttle device 41 is controlled as follows. First, in the refrigerant pipe 124, the dryness of the refrigerant downstream of the third expansion device 91 is assumed to be in the range of 0.1 to 0.5. Temperature sensor 213 and pressure sensor 21
4 to estimate the circulating composition. Next, the relationship between the saturation temperature and the saturation pressure of the refrigerant in the circulation composition is recognized, and the main throttle is set so that the difference between the evaporation temperature predicted from the measurement value of the pressure sensor 204 and the measurement value of the temperature sensor 201 is constant. The opening of the device 33 is controlled.

In the case where the composition of the refrigerant flowing in the refrigerant circuit is changed, first, a method of storing a refrigerant rich in low boiling point components in the intermediate pressure composition regulator 84 will be described. Open the opening and closing mechanisms 76 and 86, and from the upper part of the high-pressure receiver 42,
A gas refrigerant rich in low boiling point components flows through the refrigerant pipe 120 and is guided to a lower part of the intermediate pressure composition regulator 84. When ascending inside the intermediate-pressure composition adjuster 84, it exchanges heat with the low-temperature heat source 116 a to be condensed and liquefied, and is stored below the intermediate-pressure composition adjuster 84. The uncondensed gas is supplied to the third throttle device 82 and the opening / closing mechanism 7.
6, it is guided to the suction side of the low-pressure receiver 35.
As a result, the intermediate-pressure receiver 79 stores the liquid refrigerant rich in low-boiling components and can make the composition of the refrigerant circulating in the main circuit rich in high-boiling components.

A method of storing a refrigerant rich in a high boiling point component in the intermediate pressure composition controller 84 will be described. The opening and closing mechanisms 76 and 85 are opened, and a liquid refrigerant slightly rich in a high boiling point component flows from the upper part of the high-pressure receiver 42 through the refrigerant pipe 119 and is guided to the upper part of the intermediate pressure composition regulator 84. Intermediate pressure composition adjuster 8
4 When the liquid refrigerant descends from the upper part to the lower part by the action of gravity, it exchanges heat with the high-temperature heat source 116a, and a part of the liquid refrigerant evaporates, and rises as a gas refrigerant rich in low boiling point components.
The gas refrigerant rich in the low-boiling component is guided to the suction of the low-pressure receiver 35 through the refrigerant pipe 121. The liquid refrigerant stored in the lower part of the intermediate-pressure composition regulator 84 is rich in high-boiling components. As a result, the composition of the refrigerant circulating in the main circuit can be made rich in high-boiling components.

Here, the circulating composition is predicted by the above-described method for estimating the circulating composition, the above-described composition adjustment is performed according to the magnitude of the load, and the time of the composition adjustment is controlled.

Twenty-seventh Embodiment Hereinafter, a twenty-seventh embodiment of the present invention will be described with reference to FIG. In the figure, 31 is a compressor, 32 is a heat source side heat exchanger, 42 is a high pressure receiver, 94
Is a heating heat exchanger, 96 is a heating throttle device, 98 is a cooling throttle device, 95 is a cooling heat exchanger, and 35 is a low-pressure receiver, which are sequentially connected to form a refrigerant main circuit. The refrigerant pipe 125 branches from the high-pressure receiver, bypasses the heating heat exchanger 94 and the heating expansion device 96, and connects to a piping between the heating expansion device 96 and the cooling expansion device 98. Above, a bypass throttle device 97 for controlling the bypass refrigerant flow rate is provided. Further, a pressure sensor 222 and a temperature sensor 223 for measuring the pressure and temperature of the refrigerant inside the high-pressure receiver 42,
A temperature sensor 217 for measuring the temperature of the refrigerant between the heating heat exchanger 94 and the heating throttle device 96, and a pressure sensor 218 for measuring the pressure and the temperature between the heating heat exchanger 95 and the low-pressure receiver 35. And a temperature sensor 219, a ratio of the cooling and heating capacities, a measurement value of the pressure sensor 222, and a measurement value of the temperature sensor 223 to estimate a circulation composition, and control the opening degree of the heating throttle device 96. Controller 220 that estimates the circulation composition from the ratio of the cooling and heating capacities, the measurement value of the pressure sensor 222 and the measurement value of the temperature sensor 223, and controls the opening of the cooling expansion device 98.
And a configuration including:

The operation will be described. The high-temperature and high-pressure refrigerant gas discharged from the compressor 31 is condensed to a certain degree of dryness in the heat-source-side heat exchanger 32 and enters the high-pressure receiver 42 as a gas-liquid two-phase flow. The refrigerant in the gas-liquid two-phase state is separated by the high-pressure receiver 42 into gas and liquid. Among them, the gas is guided to the heating heat exchanger 94 and emits heat to the surroundings for heating. At the same time, the gas itself is condensed and liquefied, and is slightly throttled by the heating throttle device 96. Further, the liquid inside the high-pressure receiver 42 passes through the refrigerant pipe 125 and is slightly throttled by the bypass throttle device 97, and then merges with the refrigerant that has exited the heating throttle device 96. The combined liquid refrigerant is decompressed to a low pressure by the cooling expansion device 98, and the cooling heat exchanger 95
At the same time, heat is taken from the surroundings and cooling is performed.

Here, in order to estimate the circulation composition, first,
The dryness of the refrigerant accumulated in the high-pressure receiver 42 is calculated from the ratio between the cooling and heating capacities. The circulation composition is estimated from the calculated dryness and the measured values of the pressure sensor 222 and the temperature sensor 223. When controlling the heating throttle device 96, the saturation temperature for the pressure sensor 222 is calculated, and the heating throttle device is controlled so that the difference between the saturation temperature and the temperature detected by the temperature sensor 217 is constant. The opening of the device 96 is determined. Furthermore, when controlling the cooling throttle device 98, the saturation temperature for the pressure sensor 218 is calculated, and the cooling throttle is controlled so that the difference between the saturation temperature and the temperature detected by the temperature sensor 219 becomes constant. The opening of the device 98 is determined.

[0214]

As described above, the present invention has the above-mentioned structure, and by controlling the composition of the refrigerant circulating in the refrigerant circuit, the high pressure and the low pressure of the refrigeration cycle are controlled, so that the refrigerant is always stable and efficient. Driving can be performed.

According to the present invention, the liquid refrigerant rich in high-boiling components existing on the compressor suction side is evaporated, and a rapid rise in high pressure can be suppressed.

The present invention evaporates the liquid refrigerant rich in high-boiling components stored in the evaporator, and shortens the time required for the refrigerant circuit to have a constant composition in the refrigerant circuit and to attain a stable operation state.

According to the present invention, the opening and closing mechanism can be opened and closed with high accuracy.
Efficient operation can be performed.

According to the present invention, a decrease in pressure at the suction of the compressor is prevented, and the startup time of heating is shortened.

According to the present invention, while suppressing an increase in high pressure,
The time required until the composition of the refrigerant becomes constant and a stable operation state is obtained is reduced.

The present invention prevents the liquid from flowing back to the compressor while achieving the purpose of changing the composition of the refrigerant flowing in the refrigerant circuit at low cost.

According to the present invention, the composition change of the refrigerant can be suppressed and stable refrigeration cycle control can be performed.

According to the present invention, the composition of the refrigerant can be changed and efficient operation can be performed.

According to the present invention, the composition of the refrigerant is adjusted by controlling the amount of the liquid refrigerant in the plurality of receivers by changing the pressure by the expansion device, so that the composition can be easily adjusted.

According to the present invention, the refrigerant is moved through the bypass pipe by utilizing the pressure difference inside the receiver, and the refrigerant can be moved quickly and the composition can be adjusted smoothly.

According to the present invention, since the refrigerant is moved in a liquid state between a plurality of receivers, the refrigerant is moved more quickly, the composition is smoothly adjusted, and the refrigeration cycle is controlled stably.

According to the present invention, since the amount of the liquid refrigerant accumulated in each receiver is controlled to be constant by the bypass pipe, the composition can be easily adjusted.

According to the present invention, the time required for changing the composition of the refrigerant can be reduced, efficient operation can be performed, and high and low pressures of the refrigeration cycle can be controlled.

According to the present invention, the composition of the refrigerant is adjusted by opening and closing the opening / closing mechanism according to the ambient temperature conditions, so that the composition of the refrigerant can be adjusted according to the air-conditioning load and the like.

According to the present invention, the liquid level inside the receiver is detected, and if the detected liquid level is not the target liquid level, the bypass is opened and the liquid level is adjusted. It can be carried out.

According to the present invention, it is possible to shorten the time required for changing the composition of the refrigerant, perform an efficient operation, and control the high and low pressures of the refrigeration cycle while preventing the refrigerant liquid from flowing back to the compressor. Can be.

According to the present invention, the discharge pressure of the compressor can be suppressed while improving the reliability of the flow rate control and maintaining the capability. According to the present invention, different evaporation temperatures can be obtained in a plurality of evaporators.

According to the present invention, when the load is light, heat energy can be stored, and when the load is heavy, operation such as air conditioning can be performed using the heat energy.

According to the present invention, when the load is light, heat energy is stored, and when the load is heavy, the air conditioner or the like is operated by using the heat storage energy, and the degree of supercooling is increased at the inlet of the expansion device to improve the reliability of the expansion device. Improve spirit.

According to the present invention, the composition of the refrigerant accumulated in the intermediate pressure receiver is changed, the range of changing the composition of the refrigerant circulating in the refrigerant circuit is widened, and efficient operation can be performed.

According to the present invention, the composition of the refrigerant accumulated in the intermediate pressure composition regulator is changed, the range of changing the composition of the refrigerant circulating in the refrigerant circuit is widened, the composition is adjusted with high accuracy, and efficient operation is performed. It can be carried out.

[Brief description of the drawings]

FIG. 1 is a refrigerant circuit diagram according to an embodiment of the present invention.

FIG. 2 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 3 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 4 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 5 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 6 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 7 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 8 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 9 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 10 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 11 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 12 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 13 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 14 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 15 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 16 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 17 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 18 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 19 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 20 is a diagram relating to the temperature and the composition of the refrigerant in the present invention.

FIG. 21 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 22 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 23 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 24 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 25 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 26 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 27 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 28 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 29 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 30 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 31 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 32 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 33 is a refrigerant circuit diagram of another embodiment of the present invention.

FIG. 34 is a refrigerant circuit diagram showing a conventional refrigeration / air-conditioning device.

[Explanation of symbols]

1 compressor, 2 heat source side heat exchanger, 3 main throttle device, 4
Main throttle device, 5 auxiliary throttle device, 6 load side heat exchanger,
8 Refrigerant storage tower, 9 Cooling source, 10 Heating source, 11 Tower reservoir, 12 Tower reservoir, 13 Open / close valve, 14 Open / close valve, 15 Open / close valve, 16 Open / close valve, 31 Compressor, 3
2 heat source side heat exchanger, 33 expansion device, 34 load side heat exchanger, 35 low pressure receiver, 36 opening and closing mechanism, 37
Opening and closing mechanism, 38 opening and closing mechanism, 39 opening and closing mechanism, 40
Four-way valve, 41 Sub-throttle device, 42 High-pressure receiver, 43
Opening / closing mechanism, 44 opening / closing mechanism, 45 opening / closing mechanism, 46 opening / closing mechanism, 47 opening / closing mechanism, 48 opening / closing mechanism, 49 expansion device, 50 supercooling heat exchanger, 51 expansion device, 52
Load side heat exchanger, 53 refrigerant-refrigerant heat exchanger, 54 four-way valve, 55 heat storage heat exchanger, 56 heat storage medium, 57
Heat storage tank, 58 refrigerant gas pump, 59 four-way valve for heat storage,
60 opening / closing mechanism, 61 opening / closing mechanism, 62 opening / closing mechanism, 63
Heat storage heat exchanger, 64 Heat storage heat exchanger, 65 opening / closing mechanism, 66 opening / closing mechanism, 67 opening / closing mechanism, 68 opening / closing mechanism, 69 opening / closing mechanism, 70 opening / closing mechanism, 71 opening / closing mechanism, 72 opening / closing mechanism, 73 diaphragm device, 75 Expansion device, 76 opening and closing mechanism, 77 low temperature heat source, 78 high temperature heat source, 79 intermediate pressure receiver, 81 high temperature heat source, 82 expansion device, 83 high pressure composition adjuster, 84 intermediate pressure composition adjustment device, 85 opening and closing mechanism, 86 opening and closing mechanism, 87 Throttle device for detecting saturated temperature, 91 Throttle device, 94 Heat exchanger for heating, 95 Heat exchanger for cooling, 96 Throttle device for heating, 9
7 Throttle device for bypass, 98 Throttle device for cooling, 20
0 temperature sensor, 201 temperature sensor, 202 temperature sensor, 203 controller, 204 pressure sensor, 205
Temperature sensor, 206 pressure sensor, 207 temperature sensor, 208 pressure sensor, 209 temperature sensor, 210
Pressure sensor, 211 temperature sensor, 212 pressure sensor, 213 temperature sensor, 214 pressure sensor, 215
Temperature sensor, 216 refrigerant amount detection means, 217 temperature sensor, 218 pressure sensor, 219 temperature sensor, 2
20 controller, 221 controller, 222 pressure sensor,
223 Temperature sensor.

Continued on the front page (72) Inventor Moriya Miyamoto 6-66, Tehira, Wakayama-shi Mitsubishi Electric Corporation Wakayama Works (72) Inventor Shuichi Tani 6-66, Teda, Wakayama-shi Mitsubishi Electric Corporation Inside Wakayama Works (72) Inventor Tomohiko Kasai 6-5-66 Tehira, Wakayama City Mitsubishi Electric Corporation Inside Wakayama Works (72) Inventor Yoshihiro Sumida 8-1-1 Honcho Tsukaguchi, Amagasaki City Mitsubishi Electric Corporation Central Research Laboratory (72) Inventor, etc. Iijima, etc. 3-181-1, Oka, Shizuoka City Mitsubishi Electric Corporation Living Environment Engineering Management Center

Claims (37)

[Claims] 1. A refrigerant circuit for circulating a refrigerant by sequentially connecting a compressor, a condenser, a throttle device, and an evaporator to form a non-azeotropic mixed refrigerant in which several types of hydrofluorocarbons are mixed with the refrigerant. In the refrigerant circulation system used,
A piping for bypassing each device, an opening / closing mechanism provided in this piping, and opening / closing the opening / closing mechanism to adjust the composition while circulating the refrigerant through each device in the refrigerant circuit. Refrigerant circulation system. 2. The refrigerant circulation system according to claim 1, further comprising a bypass pipe connected from the compressor discharge section to at least one of low-pressure side components of the refrigerant circuit or the low-pressure side pipe to bypass the refrigerant. . 3. A refrigerant circulation system in which a compressor, a condenser, a throttling device, and an evaporator are sequentially connected, and a non-azeotropic mixed refrigerant in which several types of hydrofluorocarbons are mixed into a refrigerant, a low pressure side from a compressor discharge part. A refrigerant circulation system, comprising: a bypass pipe connected to at least one component device or a low-pressure side pipe and bypassing a part of the refrigerant. 4. A part of the refrigerant discharged from the compressor is blown into the refrigerant liquid stagnation portion in the low-pressure side component device or the low-pressure side piping at the time of starting the system.
The refrigerant circulation system according to claim 1. 5. The compressor according to claim 3, wherein the bypass pipe is connected between the compressor discharge part and the evaporator inlet part.
The refrigerant circulation system according to claim 1. 6. The refrigerant circulation system according to claim 1, wherein the opening / closing mechanism is opened at the time of starting. 7. The refrigerant circulation system according to claim 1, wherein the opening / closing mechanism is closed by detecting a predetermined physical quantity. 8. The refrigerant circulation system according to claim 7, wherein the physical quantity is at least one of time, temperature change, pressure change, and liquid level. 9. A compressor, a condenser, a throttle device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are mixed with the refrigerant, and a bypass pipe from an outlet of the condenser to a suction of the compressor. A refrigerant circulation system comprising: 10. A compressor, a condenser, a throttling device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are mixed in the refrigerant, and the evaporator is bypassed from the condenser outlet to bypass the throttling device. A refrigerant circulation system provided with a bypass pipe leading to an inlet. 11. The refrigerant circulation system according to claim 9, wherein an opening / closing mechanism is provided in the bypass pipe, and the opening / closing mechanism is opened at the time of startup. 12. A compressor, a condenser, a throttle device, and an evaporator are connected in sequence, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are mixed in the refrigerant, and a low-pressure side such as between the evaporator and the compressor. A low pressure receiver capable of storing a liquid refrigerant, and a degree of supercooling at a condenser outlet is changed according to a load. 13. A compressor, a condenser, a throttling device, and an evaporator are sequentially connected, a non-azeotropic mixed refrigerant obtained by mixing several kinds of hydrofluorocarbons as a refrigerant, and a high-pressure receiver is provided between the condenser and the throttling device. A refrigerant circulation system, comprising: 14. A compressor, a condenser, a throttle device, and an evaporator, which are sequentially connected, a non-azeotropic mixed refrigerant obtained by mixing several kinds of hydrofluorocarbons with a refrigerant, and a low-pressure refrigerant located between the evaporator and the compressor. A refrigerant circulation system comprising: a receiver; and a high-pressure receiver located between the condenser and the expansion device. 15. The refrigerant circulation system according to claim 13, further comprising pressure changing means for changing the pressure of the refrigerant flowing between the condenser and the high-pressure receiver. 16. A refrigerant circuit for circulating a refrigerant by sequentially connecting each of a compressor, a condenser, a throttle device, and an evaporator to form a non-azeotropic mixed refrigerant in which several types of hydrofluorocarbons are mixed with the refrigerant. In the refrigerant circulation system used, a low-pressure receiver that is provided on the low-pressure side and stores the refrigerant,
A high-pressure receiver provided on the high-pressure side for storing the refrigerant, wherein the liquid refrigerant stored in each of the receivers is moved between the receivers by changing the throttle amount of the expansion device. . 17. The apparatus according to claim 1, further comprising a bypass pipe for bypassing the low-voltage receiver and the high-pressure receiver.
17. The refrigerant circulation system according to 4 or 16. 18. A refrigerant circuit for circulating a refrigerant by sequentially connecting a compressor, a condenser, a throttle device, and an evaporator,
In a refrigerant circulation system using a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are mixed with a refrigerant, a plurality of receivers capable of storing a refrigerant are provided at different refrigerant pressures of the refrigerant circuit, and the respective receivers are connected. A refrigerant circulation system provided with a bypass pipe. 19. The refrigerant circulation system according to claim 17, further comprising an opening / closing mechanism provided on the bypass pipe for adjusting an amount of the refrigerant flowing through the bypass pipe. 20. The refrigerant circulation system according to claim 17, wherein the bypass pipe is connected near the bottom of each receiver to enable refrigerant transfer between the receivers. 21. The refrigerant circulation system according to claim 17, wherein the bypass pipes are connected to different positions in the vertical direction of the plurality of receivers to enable refrigerant transfer between the respective receivers. 22. A refrigerant circuit using a non-azeotropic mixed refrigerant in which several types of hydrofluorocarbons are mixed with a refrigerant by forming a refrigerant circuit for circulating the refrigerant by sequentially connecting a compressor, a condenser, a throttle device, and an evaporator. In the system, a low-pressure receiver that is provided on a low-pressure side of the refrigerant circuit that is the suction side of the compressor and stores the refrigerant, and a high-pressure receiver that is provided on a high-pressure side that is an inlet side of the expansion device of the refrigerant circuit and stores the refrigerant. A refrigerant, comprising: a receiver, a bypass pipe that connects the low-pressure receiver and the high-pressure receiver, and is capable of transferring a refrigerant between the receivers, and an opening / closing mechanism provided in the bypass pipe to open and close a flow path of the bypass pipe. Circulation system. 23. The refrigerant circulation system according to claim 22, wherein opening and closing of the opening / closing mechanism is performed by detecting a load condition or a surrounding environment condition in which the composition of the refrigerant is required. 24. The refrigerant circulation according to claim 23, wherein the state of storage of the liquid refrigerant in at least one of the low-pressure and high-pressure receivers is detected, and a refrigerant circuit opening / closing mechanism is opened / closed to adjust the composition of the refrigerant. system. 25. The refrigerant circulation system according to claim 18, wherein heat exchange can be performed between the bypass pipe and a pipe of the refrigerant circuit. 26. A compressor, a condenser, a throttling device and an evaporator which are sequentially connected, a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are mixed with the refrigerant, and a high-pressure high-pressure refrigerant located between the condenser and the throttling device. A refrigerant circulation system comprising: a receiver; and a bypass pipe that exchanges heat with the high-pressure refrigerant liquid pipe via the expansion device from the high-pressure receiver and then joins with the low-pressure component device or the low-pressure pipe. 27. The refrigerant circulation system according to claim 26, wherein a low-pressure receiver is provided between the evaporator and the compressor, and the low-pressure receiver is connected to the bypass. 28. A system in which a compressor, a condenser, a throttle device, and an evaporator are sequentially connected, and a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are mixed in the refrigerant,
A plurality of combinations of the expansion device and the evaporator are arranged, and the combinations of the expansion device and the evaporator are connected to different positions of the high-pressure side receiver connected to the condenser outlet, and each evaporator has a different state in the high-pressure side receiver. A refrigerant circulation system, characterized in that the refrigerant is allowed to flow. 29. A compressor, a condenser, a throttle device, and an evaporator, which are sequentially connected, a non-azeotropic mixed refrigerant obtained by mixing several kinds of hydrofluorocarbons as a refrigerant, and a high-pressure refrigerant located between the condenser and the throttle device. A receiver, a bypass pipe connected to a low-pressure side component device or a low-pressure side pipe through a second throttle device and a second evaporator from above the high-pressure receiver, and between the high-pressure receiver and the second throttle device. And a heat exchanger for exchanging heat between the piping and the piping between the expansion device and the evaporator. 30. A compressor, a condenser, a throttling device, and an evaporator, which are sequentially connected, a non-azeotropic mixed refrigerant obtained by mixing several kinds of hydrofluorocarbons as a refrigerant, and a high-pressure high-pressure refrigerant located between the condenser and the throttling device. A receiver, a bypass pipe connected to a pipe at an outlet of the evaporator through a second expansion device, a heat exchanger for heat storage, and a refrigerant gas pump from above the high-pressure receiver, and the heat storage tank bypassing the refrigerant gas pump. And a pipe connecting the evaporator outlet, and a heat exchanger for exchanging heat between a pipe between the high-pressure receiver and a second expansion device and a pipe between the expansion device and the evaporator. Refrigerant circulation system. 31. A compressor, a condenser, a throttling device, a heat storage heat exchanger and an evaporator are connected in sequence, and a non-azeotropic mixed refrigerant in which several kinds of hydrofluorocarbons are mixed with a refrigerant is used. A high-pressure receiver located between the high-pressure receiver and a bypass pipe connected to a low-pressure two-phase pipe through a second expansion device and a second heat storage heat exchanger from the upper part of the high-pressure receiver; A heat storage medium that stores heat energy through a heat exchanger and a second heat storage heat exchanger; a heat storage tank that stores the heat storage medium; a pipe between the high-pressure receiver and a second expansion device; the expansion device; A refrigerant circulation system comprising a heat exchanger for exchanging heat between pipes between evaporators. 32. The refrigerant circulation system according to claim 30, wherein a low-pressure receiver is provided between the evaporator and the compressor. 33. A compressor, a condenser, a throttle device, and an evaporator, which are sequentially connected, a non-azeotropic mixed refrigerant obtained by mixing several kinds of hydrofluorocarbons with the refrigerant, and a low-pressure refrigerant located between the evaporator and the compressor. A receiver, a high-pressure receiver located between the condenser and the expansion device, an intermediate pressure receiver, a bypass pipe connecting the high-pressure receiver to the low-pressure side component device or the low-pressure side pipe via the intermediate pressure receiver, and the intermediate pressure Means for controlling the temperature inside the receiver. 34. The refrigerant circulation system according to claim 33, further comprising means for controlling a pressure in the intermediate pressure receiver. 35. The refrigerant circulation system according to claim 33, wherein the means for controlling the temperature in the intermediate receiver can set the temperature in multiple stages. 36. A compressor, a condenser, a throttle device, and an evaporator, which are sequentially connected, a non-azeotropic mixed refrigerant obtained by mixing several types of hydrofluorocarbons as a refrigerant, and a low-pressure refrigerant located between the evaporator and the compressor. A receiver, a high-pressure receiver located between the condenser and the expansion device, an intermediate-pressure composition adjuster containing a rectifying heat source, and a liquid refrigerant pipe that guides the liquid refrigerant from the high-pressure receiver to the intermediate-pressure composition adjuster. A gas refrigerant pipe that guides a gas refrigerant from the high-pressure receiver to the intermediate-pressure composition adjuster; and a bypass pipe that connects the intermediate-pressure composition adjuster to a low-pressure side component device or a low-pressure side pipe. Refrigerant circulation system. 37. A pipe connecting between the high-pressure receiver and the intermediate composition adjuster, and a pipe connecting the intermediate composition adjuster and the low-pressure side component device 2 connecting with the low-pressure side pipe are provided with opening / closing mechanisms, respectively. 37. The refrigerant circulation system according to claim 36.