WO2021033426A1

WO2021033426A1 - Heat source unit and freezing apparatus

Info

Publication number: WO2021033426A1
Application number: PCT/JP2020/025197
Authority: WO
Inventors: 覚阪江; 東近藤
Original assignee: ダイキン工業株式会社
Priority date: 2019-08-21
Filing date: 2020-06-26
Publication date: 2021-02-25
Also published as: EP3995756A1; ES2966337T3; JP2021032440A; CN114270108A; CN114270108B; EP3995756A4; JP6844667B2; EP3995756B1

Abstract

According to the present invention, an oil recovery operation comprises a first operation of reducing the opening degree of a heat source expansion valve (28) and a second operation of increasing the opening degree of the heat source expansion valve (28) after the first operation. A controller (80) is configured to execute the second operation when a first condition is satisfied during the first operation. The first condition includes at least a condition in which a difference ΔP between the pressure of a refrigerant on the downstream side of the heat source expansion valve (28) in a liquid pipe (43) and the pressure of a suction refrigerant of a compression element (C) is smaller than a predetermined value.

Description

Heat source unit and refrigeration equipment

This disclosure relates to a heat source unit and a refrigerating device.

In the refrigerating apparatus described in Patent Document 1, an oil recovery operation is performed in which the oil accumulated in the heat exchanger used is returned to the compressor. Specifically, in the oil recovery operation, first, the opening degree of the first expansion valve of the liquid pipe is reduced. Then, the flow rate and pressure of the refrigerant flowing through the utilization heat exchanger decrease, and the suction superheat degree increases. Along with this, the opening degree of the utilization expansion valve gradually increases. When a predetermined first time t1 elapses after reducing the opening degree of the first expansion valve, the opening degree of the first expansion valve is increased. As a result, the flow rate of the refrigerant flowing through the utilization heat exchanger increases. This refrigerant is compatible with the refrigerating machine oil in the heat exchanger used and is recovered in the compressor together with the refrigerating machine oil.

JP-A-2018-84376

In the refrigeration apparatus described in Patent Document 1, when the predetermined first time t1 elapses after reducing the opening degree of the first expansion valve, it is considered that the opening degree of the utilization expansion valve has increased, and the opening of the first expansion valve is opened. The degree is increased. However, it is not possible to accurately determine that the opening degree of the expansion valve used has increased by the determination by such a timer.

An object of the present disclosure is to improve the accuracy of determining that the opening degree of the utilization expansion valve has increased in the first operation of reducing the opening degree of the heat source expansion valve in the oil recovery operation.

The first embodiment has a compression element (C), a liquid pipe (43), a heat source expansion valve (28) connected to the liquid pipe (43), and a heat source heat exchanger (25), and utilizes heat exchange. By connecting to a utilization unit (70) having a vessel (73) and a utilization expansion valve (72), the heat source heat exchanger (25) becomes a radiator and the utilization heat exchanger (73) becomes an evaporator. A heat source unit including a refrigerant circuit (10) that performs a refrigeration cycle, and the heat source unit (20) so as to execute an oil recovery operation for recovering oil from the utilization heat exchanger (73) during the refrigeration cycle. ) Is further provided, and the oil recovery operation includes a first operation of reducing the opening degree of the heat source expansion valve (28), and after the first operation, the heat source expansion valve (28). ) Is included, and the controller (80) is configured to execute the second operation when the first condition is satisfied during the first operation, and the first condition is included. At least includes a condition in which the difference ΔP between the pressure of the refrigerant on the downstream side of the heat source expansion valve (28) in the liquid pipe (43) and the pressure of the suction refrigerant of the compression element (C) is smaller than a predetermined value. There is.

In the first aspect, in the first operation, the difference ΔP between the pressure of the refrigerant on the downstream side of the heat source expansion valve (28) in the liquid pipe (43) and the pressure of the suction refrigerant of the compression element (C) is greater than a predetermined value. By setting the first condition to be small, it is possible to improve the accuracy of determining that the opening degree of the utilization expansion valve has increased.

In the second aspect, in the first aspect, the first condition includes a condition in which the degree of inhalation superheat is greater than the first value.

In the second aspect, in the first operation, by setting a large suction superheat degree as the first condition, it is possible to improve the accuracy of determining that the opening degree of the utilization expansion valve (72) has increased.

In the third aspect, in the first or second aspect, when the second condition is satisfied during the second operation, the controller (80) sets the opening degree of the heat source expansion valve (28) to the first. It is configured to execute the third operation which is the opening degree immediately before the start of the operation, and the second condition includes a condition where the suction superheat degree is smaller than the second value.

In the third aspect, in the second operation, the accuracy of determining that the oil has been recovered in the compression element (C) can be improved by setting the suction superheat degree to be smaller than the second value as the second condition.

In the fourth aspect, in any one of the first to third aspects, the controller (80) opens the heat source expansion valve (28) when the second condition is satisfied during the second operation. Is configured to execute the third operation with the opening degree immediately before the start of the first operation, and the second condition is that of the refrigerant on the downstream side of the heat source expansion valve (28) in the liquid pipe (43). Includes the condition that the pressure becomes higher than the predetermined value.

In the fourth aspect, in the second operation, the oil is recovered in the compression element (C) under the second condition that the pressure of the refrigerant on the downstream side of the heat source expansion valve (28) is higher than a predetermined value. The accuracy of the judgment can be improved.

In the fifth aspect, in any one of the first to fourth aspects, the speed at which the opening degree of the heat source expansion valve (28) is increased during the second operation is increased during the first operation. It is faster than the speed of reducing the opening of 28).

In the fifth aspect, in the second operation, under the condition that the opening degree of the utilization expansion valve (72) is large, the oil accumulated in the utilization heat exchanger (73) is quickly compressed together with the refrigerant (21,22,23). ) Can be returned.

A sixth aspect comprises the heat source unit (20) according to any one of the first to fifth aspects, and a utilization unit (70) having a utilization heat exchanger (73) and a utilization expansion valve (72). By connecting the heat source unit (20) and the utilization unit (70), a refrigeration cycle using the heat source heat exchanger (25) as a radiator and the utilization heat exchanger (73) as an evaporator can be performed. It is a refrigerating apparatus in which the refrigerant circuit (10) is configured.

A seventh aspect is a refrigerating apparatus according to the sixth aspect, wherein the utilization expansion valve (72) is a temperature automatic expansion valve.

FIG. 1 is a piping system diagram of the refrigerating device according to the embodiment. FIG. 2 is a diagram corresponding to FIG. 1 showing the flow of the refrigerant in the cold operation. FIG. 3 is a diagram corresponding to FIG. 1 showing the flow of the refrigerant in the defrost operation. FIG. 4 is a flowchart of the oil return operation.

Hereinafter, this embodiment will be described with reference to the drawings. It should be noted that the following embodiments are essentially preferred examples and are not intended to limit the scope of the present invention, its applications, or its uses.

<overall structure>
The refrigerating apparatus (1) according to the first embodiment cools the air to be cooled. The cooling target of this example is the air inside a refrigerator, a freezer, a showcase, or the like.

As shown in FIG. 1, the refrigerating device (1) includes an outdoor unit (20) installed outdoors and a cooling unit (70) for cooling the air inside the refrigerator. The number of cooling units (70) is not limited to two, and may be one or three or more. The outdoor unit (20) and the two cooling units (70) are connected to each other via a liquid communication pipe (14) and a gas communication pipe (13). As a result, the refrigerant circuit (10) is configured in the refrigerating device (1). In the refrigerant circuit (10), a vapor compression refrigeration cycle is performed by circulating the filled refrigerant.

<Overview of outdoor unit>
The outdoor unit (20) is a heat source unit. The outdoor unit (20) is installed outdoors. The outdoor unit (20) has a heat source circuit (20a) and an outdoor fan (F1). The heat source circuit (20a) has three compressors (21,22,23), a four-way switching valve (24), an outdoor heat exchanger (25), and a receiver (receiver), which are the compression elements (C) as the main components. It has a 26), supercooled heat exchanger (27), and an outdoor expansion valve (28).

The heat source circuit (20a) is provided with a gas shutoff valve (11) and a liquid shutoff valve (12). A gas connecting pipe (13) is connected to the gas shutoff valve (11). A liquid communication pipe (14) is connected to the liquid shutoff valve (12).

<Compression element and its peripheral structure>
The compression element (C) of this example is composed of three compressors (21,22,23). In the heat source circuit (20a), three compressors (21,22,23) are connected in parallel. The three compressors (21,22,23) are composed of a first compressor (21), a second compressor (22), and a third compressor (23). Each compressor (21,22,23) is composed of, for example, a scroll compressor. The first compressor (21) is a variable capacitance type. Power is supplied to the electric motor of the first compressor (21) via an inverter circuit. The second compressor (22) and the third compressor (23) are of a fixed capacitance type.

The first discharge pipe (31) is connected to the discharge portion of the first compressor (21). A first suction pipe (34) is connected to the suction portion of the first compressor (21). A second discharge pipe (32) is connected to the discharge portion of the second compressor (22). A second suction pipe (35) is connected to the suction portion of the second compressor (22). A third discharge pipe (33) is connected to the discharge pipe (33) of the third compressor (23). A third suction pipe (36) is connected to the suction portion of the third compressor (23).

The inflow end of the main discharge pipe (37) is connected to each outflow end of the first discharge pipe (31), the second discharge pipe (32), and the third discharge pipe (33). The outflow end of the main suction pipe (38) is connected to each inflow end of the first suction pipe (34), the second suction pipe (35), and the third suction pipe (36).

The first check valve (CV1) is connected to the first discharge pipe (31). A second check valve (CV2) is connected to the second discharge pipe (32). A third check valve (CV3) is connected to the third discharge pipe (33). The first check valve (CV1), the second check valve (CV2), and the third check valve (CV3) are from the discharge part of each compressor (21,22,23) to the main discharge pipe (37). Allows the flow of refrigerant and prohibits the reverse flow of refrigerant.

An oil separator (39) is provided in the main discharge pipe (37). The oil separator (39) separates the oil from the refrigerant compressed by the compression element (C). The inflow end of the oil return pipe (39a) is connected to the oil separator (39). The outflow end of the oil return pipe (39a) is connected to the injection circuit (I). An oil return valve (39b), which is an electric valve, is connected to the oil return pipe (39a). The oil separated by the oil separator (39) is returned to the compression chamber (intermediate pressure section) of each compressor (21,22,23) via the oil return pipe (39a) and the injection circuit (I).

<Four-way switching valve>
The four-way switching valve (24) has a first port (P1), a second port (P2), a third port (P3), and a fourth port (P4). The first port (P1) is connected to the outflow end of the main discharge pipe (37). The second port (P2) is connected to the inflow end of the main suction pipe (38). The third port (P3) is connected to the gas end of the outdoor heat exchanger (25). The fourth port (P4) is connected to the gas shutoff valve (11).

The four-way switching valve (24) switches between the first state (the state shown by the solid line in FIG. 1) and the second state (the state shown by the broken line in FIG. 1). The four-way switching valve (24) in the first state communicates the first port (P1) and the third port (P3), and communicates the second port (P2) and the fourth port (P4). The four-way switching valve (24) in the second state communicates the first port (P1) and the fourth port (P4), and communicates the second port (P2) and the third port (P3).

<Outdoor heat exchanger and its peripheral structure>
The outdoor heat exchanger (25) is a heat source heat exchanger. The outdoor heat exchanger (25) is a fin-and-tube heat exchanger. The outdoor fan (F1) is located near the outdoor heat exchanger (25). The outdoor fan (F1) carries the outdoor air that passes through the outdoor heat exchanger (25). In the outdoor heat exchanger (25), the outdoor air conveyed by the outdoor fan (F1) exchanges heat with the refrigerant.

<Receiver, supercooled heat exchanger, and its peripheral structure>
The receiver (26) stores the refrigerant. The receiver (26) is a vertically long closed container.

The supercooled heat exchanger (27) has a first flow path (27a) and a second flow path (27b). The supercooling heat exchanger (27) exchanges heat between the refrigerant flowing through the first flow path (27a) and the refrigerant flowing through the second flow path (27b).

The first pipe (41) is connected between the liquid end of the outdoor heat exchanger (25) and the top of the receiver (26). A fourth check valve (CV4) is connected to the first pipe (41). The fourth check valve (CV4) allows the flow of refrigerant from the outdoor heat exchanger (25) side to the receiver (26) side and prohibits the reverse flow of refrigerant.

A second pipe (42) is connected between the bottom of the receiver (26) and one end of the first flow path (27a) of the supercooled heat exchanger (27). A third pipe (43) is connected between the other end of the first flow path (27a) and the liquid shutoff valve (12). The third pipe (43) constitutes a part of the liquid pipe. A fifth check valve (CV5) is connected to the third pipe (43). The fifth check valve (CV5) allows the flow of refrigerant from the other end side of the first flow path (27a) to the liquid closing valve (12) side, and prohibits the reverse flow of refrigerant.

An outdoor expansion valve (28) is connected to the third pipe (43) between the other end of the first flow path (27a) and the fifth check valve (CV5). The outdoor expansion valve (28) is a heat source expansion valve. The outdoor expansion valve (28) is a pressure reducing mechanism for reducing the pressure of the refrigerant. The outdoor expansion valve (28) is composed of an electronic expansion valve.

The fourth pipe (44) is connected to the third pipe (43). One end of the fourth pipe (44) is connected between the fifth check valve (CV5) and the liquid shutoff valve (12) in the third pipe (43). The other end of the fourth pipe (44) is connected between the fourth check valve (CV4) and the receiver (26) in the first pipe (41). A sixth check valve (CV6) is connected to the fourth pipe (44). The sixth check valve (CV6) allows the flow of refrigerant from the third pipe (43) side to the first pipe (41) side, and prohibits the reverse flow of refrigerant.

The fifth pipe (45) is connected to the third pipe (43). One end of the fifth pipe (45) is connected between the outdoor expansion valve (28) and the fifth check valve (CV5) in the third pipe (43). The other end of the fifth pipe (45) is connected between the fourth check valve (CV4) in the first pipe (41) and the outdoor heat exchanger (25). A seventh check valve (CV7) is connected to the fifth pipe (45). The seventh check valve (CV7) allows the flow of refrigerant from the third pipe (43) side to the first pipe (41) side, and prohibits the reverse flow of refrigerant.

<Injection circuit>
The heat source circuit (20a) includes an injection circuit (I). The injection circuit (I) introduces the intermediate pressure refrigerant into the intermediate pressure portion of the compression element (C). The injection circuit (I) includes one branch pipe (51), one relay pipe (52), and three injection pipes (53,54,55).

The inflow end of the branch pipe (51) is connected between the first flow path (27a) and the outdoor expansion valve (28) in the third pipe (43). The outflow end of the branch pipe (51) is connected to the inflow end of the second flow path (27b). An injection valve (59) is connected to the branch pipe (51). The injection valve (59) is composed of an electronic expansion valve.

The inflow end of the relay pipe (52) is connected to the outflow end of the second flow path (27b). The outflow end of the oil return pipe (39a) is connected to the relay pipe (52). The inflow ends of the first injection pipe (53), the second injection pipe (54), and the third injection pipe (55) are connected to the outflow portion of the relay pipe (52).

The outflow end of the first injection pipe (53) communicates with the compression chamber of the first compressor (21). The outflow end of the second injection pipe (54) communicates with the compression chamber of the second compressor (22). The outflow end of the third injection pipe (55) communicates with the compression chamber of the third compressor (23).

The first electric valve (56) is connected to the first injection pipe (53). A second electric valve (57) is connected to the second injection pipe (54). A third electric valve (58) is connected to the third injection pipe (55). Each electric valve (56,57,58) is a flow control valve. Each motorized valve (56,57,58) regulates the flow rate of refrigerant in the corresponding injection tube (53,54,55).

<Sensor of heat source unit>
The heat source unit (20) is provided with a plurality of sensors for detecting the physical quantity of the refrigerant in the heat source circuit (20a). The plurality of sensors include a first discharge temperature sensor (61), a second discharge temperature sensor (62), a third discharge temperature sensor (63), a high pressure pressure sensor (64), a suction temperature sensor (65), and a low pressure pressure sensor ( 67), has at least a liquid side pressure sensor (68), and an intermediate pressure sensor (69).

The first discharge temperature sensor (61) detects the temperature (Td1) of the refrigerant in the first discharge pipe (31). The second discharge temperature sensor (62) detects the temperature (Td2) of the refrigerant in the second discharge pipe (32). The third discharge temperature sensor (63) detects the temperature (Td3) of the refrigerant in the third discharge pipe (33). The high-pressure pressure sensor (64) detects the discharge pressure of the compression element (C) (high-pressure pressure (HP) of the refrigerant circuit (10)). The suction temperature sensor (65) detects the temperature of the suction refrigerant of the compression element (C). The low pressure pressure sensor (67) detects the suction pressure of the compression element (C) (low pressure (LP) of the refrigerant circuit (10)). The liquid side pressure sensor (68) detects the pressure (liquid pressure (Ps)) of the liquid refrigerant in the third pipe (43). The intermediate pressure sensor (69) detects the pressure (MP) of the refrigerant in the relay pipe (52) of the injection circuit (I).

The low-pressure pressure sensor (67) and the suction temperature sensor (66) constitute a suction superheat detection unit for detecting the suction superheat (SSH) of the compression element (C). Specifically, the controller (80) determines the suction superheat degree (80) by the difference between the saturation temperature corresponding to the low pressure (LP) detected by the low pressure pressure sensor (67) and the temperature detected by the suction temperature sensor (66). SSH) is requested.

The high-pressure pressure sensor (64) and the three discharge temperature sensors (61,62,63) constitute a discharge superheat detection unit for detecting the discharge superheat (DSH) of the compression element (C). Specifically, the controller (80) has a saturation temperature corresponding to the high pressure (HP) detected by the high pressure sensor (64) and a temperature detected by each discharge temperature sensor (61,62,63) (for example, these). The discharge superheat degree (DSH) is calculated from the difference from the average temperature).

<Colding unit>
The cooling unit (70) is a utilization unit. Each cooling unit (70) has a utilization circuit (70a) and an internal fan (F2), respectively.

The utilization circuit (70a) is connected in parallel to the liquid communication pipe (14) and the gas communication pipe (13). Each utilization circuit (70a) has an on-off valve (71), an internal expansion valve (72), and an internal heat exchanger (73) in this order from the liquid end portion to the gas end portion.

The on-off valve (71) is an electromagnetic on-off valve that opens and closes the utilization circuit (70a). The on-off valve (71) is opened during normal operation.

The internal expansion valve (72) is a utilization expansion valve. The internal expansion valve (72) is a temperature-sensitive automatic expansion valve. The opening degree of the internal expansion valve (72) is adjusted according to the degree of superheat of the refrigerant flowing out of the utilization heat exchanger (73) serving as an evaporator. This degree of superheat corresponds to the degree of suction superheat (SSH) of the refrigerant sucked into the compression element (C).

More specifically, as shown in FIG. 1, the internal expansion valve (72) has an expansion valve main body (72a), a temperature sensitive tube (72b), and a capillary tube (72c). The expansion valve body (72a) is connected between the on-off valve (71) of the utilization circuit (70a) and the internal heat exchanger (73). The temperature sensitive cylinder (72b) is arranged so as to come into contact with the piping at the gas end of the utilization heat exchanger (73). The expansion valve body (72a) and the temperature sensitive cylinder (72b) are connected via a capillary tube (72c). When the degree of superheat of the refrigerant flowing out of the internal heat exchanger (73) serving as an evaporator changes, the pressure of the working fluid sealed inside the temperature sensitive cylinder (72b) and the capillary tube (72c) changes. The diaphragm of the expansion valve main body (72a) is displaced according to this change in internal pressure, and the opening degree of the internal expansion valve (72) is adjusted.

The internal heat exchanger (73) is a utilization heat exchanger. The internal heat exchanger (73) is a fin-and-tube heat exchanger. The internal fan (F2) is arranged in the vicinity of the internal heat exchanger (73). The internal fan (F2) conveys the internal air passing through the internal heat exchanger (73). In the internal heat exchanger (73), the internal air conveyed by the internal fan (F2) exchanges heat with the refrigerant.

<controller>
The outdoor unit (20) includes a controller (80). The controller (80) includes a microcomputer mounted on a control board and a memory device (specifically, a semiconductor memory) for storing software for operating the microcomputer.

The controller (80) controls each device of the outdoor unit (21,22,23) based on the operation command and the detection signal of each sensor. The controller (80) controls each device so as to switch between the cold operation, the defrost operation, and the oil return operation. The cooling operation is an operation in which the air inside the refrigerator is cooled by the cooling unit (70). The defrost operation is an operation of melting the frost on the surface of the internal heat exchanger (73). The oil return operation is an operation of recovering the oil (refrigerator oil) accumulated in the internal heat exchanger (73) to the compressor (21,22,23).

In the oil return operation, the controller (80) controls the outdoor unit (20) to execute the first operation, the second operation, and the third operation. The first operation is an operation of reducing the opening degree of the outdoor expansion valve (28). The second operation is an operation of increasing the opening degree of the outdoor expansion valve (28). The third operation is an operation of returning the opening degree of the outdoor expansion valve (28) to the opening degree immediately before the start of the first operation.

The controller (80) makes a determination to execute the second operation during the first operation. This determination is made based on the first condition (details will be described later). The controller (80) determines to execute the third operation during the second operation. This determination is made based on the second condition (details will be described later).

-Driving operation-
The operation operation of the refrigerating apparatus (1) according to the embodiment will be described.

<Cold operation>
In the cold operation, each compressor (21,22,23), an outdoor fan (F1), and an internal fan (F2) are operated. The four-way switching valve (24) is set to the first state, and the outdoor expansion valve (28) is fully opened. The on-off valve (71) is opened. The opening degree of each internal expansion valve (72) is adjusted as appropriate. Specifically, the opening degree of each internal expansion valve (72) is adjusted so as to maintain the degree of superheat of the refrigerant flowing out of the internal heat exchanger (73) at a predetermined value. The opening degrees of the injection valve (59), the first electric valve (56), the second electric valve (57), and the third electric valve (58) are appropriately adjusted.

In the cold operation, the first refrigeration cycle is performed in which the outdoor heat exchanger (25) is used as a radiator or condenser and the internal heat exchanger (73) is used as an evaporator.

As shown in FIG. 2, in the cold operation, the refrigerant compressed by each compressor (21,22,23) flows through the outdoor heat exchanger (25). In the outdoor heat exchanger (25), the refrigerant dissipates heat to the outdoor air. The refrigerant radiated by the outdoor heat exchanger (25) passes through the first pipe (41), the receiver (26), and the second pipe (42), and passes through the first flow path (27a) of the supercooled heat exchanger (27). ) Flow.

When the injection valve (59) is opened, a part of the refrigerant in the third pipe (43) flows through the branch pipe (51). The refrigerant in the branch pipe (51) is decompressed by the injection valve (59) and then flows through the second flow path (27b) of the supercooling heat exchanger (27). In the supercooling heat exchanger (27), the refrigerant in the second flow path (27b) and the refrigerant in the first flow path (27a) exchange heat. The refrigerant in the second flow path (27b) absorbs heat from the refrigerant in the first flow path (27a) and evaporates. As a result, the refrigerant in the first flow path (27a) is cooled, and the degree of supercooling of this refrigerant increases.

The refrigerant flowing through the second flow path (27b) is introduced from each injection pipe (53,54,55) to the compression chamber of each compressor (21,22,23) via the relay pipe (52). To.

The refrigerant cooled in the first flow path (27a) flows through the third pipe (43) and the liquid communication pipe (14), and is sent to each cooling unit (70).

In each cooling unit (70), the refrigerant is decompressed by the internal expansion valve (72) and then flows through the internal heat exchanger (73). In the internal heat exchanger (73), the refrigerant absorbs heat from the internal air and evaporates. As a result, the air inside the refrigerator is cooled.

The refrigerant evaporated in each heat exchanger (73) flows through the gas connecting pipe (13) and is sent to the outdoor unit (20). This refrigerant flows through the main suction pipe (38) and is sucked into each compressor (21, 22, 23).

<Defrost operation>
In the defrost operation, each compressor (21,22,23), an outdoor fan (F1), and an internal fan (F2) are operated. The four-way switching valve (24) is set to the second state, and the internal expansion valve (72) is fully opened. The on-off valve (71) is opened. The opening degree of the outdoor expansion valve (28) is adjusted. As shown in FIG. 3, in the defrost operation, the refrigerant may flow through the injection circuit (I) as in the cold operation. It is not necessary to fully close the injection valve (59) and allow the refrigerant to flow through the injection circuit (I).

In the defrost operation, a second refrigeration cycle is performed in which the internal heat exchanger (73) is used as a radiator or condenser and the outdoor heat exchanger (25) is used as an evaporator.

As shown in FIG. 3, in the defrost operation, the refrigerant compressed by each compressor (21,22,23) passes through the gas connecting pipe (13) and is sent to each cooling unit (70). In each cooling unit (70), the refrigerant flows through the internal heat exchanger (73). In the internal heat exchanger (73), the refrigerant melts the frost on the surface. The refrigerant radiated by each internal heat exchanger (73) flows through the liquid communication pipe (14) and is sent to the outdoor unit (20).

The refrigerant of the outdoor unit (20) is the fourth pipe (44), the receiver (26), the second pipe (42), the first flow path (27a) of the supercooled heat exchanger (27), and the third pipe (43). ) Flow in order. The refrigerant flowing out to the third pipe (43) is depressurized by the outdoor expansion valve (28), and then flows through the fifth pipe (45) and the outdoor heat exchanger (25) in this order. In the outdoor heat exchanger (25), the refrigerant absorbs heat from the outdoor air and evaporates. The refrigerant evaporated in the outdoor heat exchanger (25) flows through the main suction pipe (38) and is sucked into each compressor (21,22,23).

<Oil recovery operation>
Next, the oil recovery operation will be described in detail. The oil return operation is executed when a predetermined condition is satisfied during the above-mentioned cold operation. In the oil return operation, each compressor (21,22,23), an outdoor fan (F1), and an internal fan (F2) are operated. The four-way switching valve (24) is set to the first state. The on-off valve (71) is opened. The opening degree of each internal expansion valve (72) is adjusted as appropriate. Specifically, the opening degree of each internal expansion valve (72) is adjusted so as to maintain the degree of superheat of the refrigerant flowing out of the internal heat exchanger (73) at a predetermined value. The opening degrees of the injection valve (59), the first electric valve (56), the second electric valve (57), and the third electric valve (58) are appropriately adjusted.

The oil recovery operation described below is an example of recovering the oil of all the internal heat exchangers (73) at the same time.

As shown in FIG. 4, when a command to execute the oil recovery operation is input to the controller (80), in step ST1, the storage unit of the controller (80) changes the current opening degree (pls1) of the outdoor expansion valve (28). ) Is memorized. This current opening degree (Pls1) is, for example, the maximum opening degree of the outdoor expansion valve (28). Then, in step ST2, the first operation is executed.

In the first operation, the opening degree of the outdoor expansion valve (28) gradually decreases. Specifically, in the first operation, the opening degree of the outdoor expansion valve (28) is gradually reduced every predetermined time ΔT1. Here, the opening degree (pulse) of the next outdoor expansion valve (28) after the elapse of ΔT1 is EV1, and the opening degree (pulse) of the current outdoor expansion valve (28) is EV1'. In the first operation, the opening degree of the outdoor expansion valve (28) is reduced so that EV1 = α × EV1'for each ΔT1. Here, ΔT1 is set to, for example, 15 seconds. α is set to 0.75. In other words, in the first operation, the opening degree (pulse) of the outdoor expansion valve (28) decreases by 25% every 15 seconds. The first operation is continuously performed until the first condition of step ST3 is satisfied.

In the first operation, when the opening degree of the outdoor expansion valve (28) becomes small, the refrigerant is depressurized by the outdoor expansion valve (28). Therefore, the flow rate and pressure of the refrigerant flowing through the utilization heat exchanger (73) are reduced. As a result, the degree of superheat of the refrigerant flowing out of each internal heat exchanger (73) increases, and the opening degree of each internal expansion valve (72) increases.

In step ST3, it is determined whether or not the first condition for executing the second operation is satisfied during the first operation. The first condition includes the following conditions a) to e). In this example, when any one of the conditions a) to e) is satisfied, the process proceeds from step ST4 to step S6, and the second operation is executed.

A) The difference ΔP (= Ps-LP) between the hydraulic pressure (Ps) detected by the liquid side pressure sensor (68) and the low pressure pressure (LP) detected by the low pressure pressure sensor (67) is smaller than the predetermined value. Here, this predetermined value is set to, for example, several hundred KPa.

B) The degree of inhalation superheat (SSH) is larger than the predetermined value (first value). Here, the first value is set to, for example, several tens of degrees Celsius.

C) Low pressure (LP) is smaller than the specified value. Here, this predetermined value is set to several tens of KPa.

D) High pressure (HP) is greater than the specified value. Here, this predetermined value is set to several hundred MPa.

E) A predetermined time t1 has elapsed since the first operation was executed. Here, t1 is set to, for example, a few minutes.

The above a) is a condition for determining that the opening degree of the internal expansion valve (72) has been sufficiently increased by the first operation. The hydraulic pressure (Ps) of the refrigerant on the downstream side of the outdoor expansion valve (28) corresponds to the pressure on the inflow side of the internal expansion valve (72). The low pressure (LP) corresponds to the pressure on the outflow side of the internal expansion valve (72). Therefore, ΔP corresponds to the pressure at which the refrigerant is depressurized by the internal expansion valve (72). Therefore, on condition that ΔP is smaller than a predetermined value, it is possible to accurately determine that the opening degree of the internal expansion valve (72) is large.

In addition, the condition a) uses only the pressure of the refrigerant as an index for judgment. The pressure of the refrigerant is highly responsive compared to the temperature of the refrigerant. Therefore, by setting a) as the first condition, it can be quickly determined that the opening degree of the internal expansion valve (72) is large.

The above b) is a condition for determining that the opening degree of the internal expansion valve (72) has been sufficiently increased by the first operation. As described above, when the degree of superheat of the refrigerant flowing out of each internal heat exchanger (73) increases due to the first operation, the opening degree of each internal expansion valve (72) increases. Nevertheless, when the suction superheat degree (SSH) is larger than the first value, it can be estimated that the opening degree of the internal expansion valve (72) is sufficiently large or is in a fully open state. Therefore, on condition that the suction superheat degree (SSH) is larger than the first value, it is possible to accurately determine that the opening degree of the internal expansion valve (72) is large.

The above c) is a condition set from the viewpoint of protection of the refrigerating apparatus (1). When the first operation is executed and the opening degree of the outdoor expansion valve (28) is reduced, the low pressure pressure (LP) may become excessively low. Therefore, in the first operation, when the low pressure pressure (LP) becomes lower than the predetermined value, the process proceeds to steps ST4 to ST6, and the second operation is executed. As a result, the opening degree of the outdoor expansion valve (28) is increased, and a decrease in low pressure (LP) can be suppressed.

The above d) is a condition set from the viewpoint of protection of the refrigerating apparatus (1). When the first operation is executed and the opening degree of the outdoor expansion valve (28) is reduced, the high pressure (HP) may become excessively high. Therefore, in the first operation, when the high pressure pressure (HP) becomes higher than the predetermined value, the process proceeds to steps ST4 to ST6, and the second operation is executed.

The above e) is a condition for determining that the opening degree of the internal expansion valve (72) has been sufficiently increased by the first operation. In the first operation, the opening degree of the internal expansion valve (72) increases with the passage of time. Therefore, by setting d) on which the predetermined time t1 elapses as the first condition, it can be determined that the opening degree of the internal expansion valve (72) is large. The predetermined time t1 is set sufficiently long so that the conditions a) and b) above are satisfied first. The condition e) can be said to be a protective condition for shifting to the second operation even when the conditions a) to d) are not satisfied when, for example, a sensor failure or false detection occurs.

In step ST3, when any of the above conditions a) to e) is satisfied, the process proceeds to step ST4, and when the predetermined time t2 elapses, the process proceeds to step ST5. t2 is about several seconds. Note that step S4 may be omitted and the process may be shifted from step ST3 to step ST5. In step ST5, the hydraulic pressure (Ps1) detected by the liquid side pressure sensor (68) is stored in the storage unit of the controller (80). Then, the process proceeds to step ST6, and the second operation is executed.

In the second operation, the opening of the outdoor expansion valve (28) gradually increases. Specifically, in the second operation, the opening degree of the outdoor expansion valve (28) is gradually increased every predetermined time ΔT2. Here, the opening degree (pulse) of the next outdoor expansion valve (28) after ΔT2 has elapsed is defined as EV2, and the opening degree (pulse) of the current outdoor expansion valve (28) is defined as EV2'. In the second operation, the opening degree of the outdoor expansion valve (28) is increased so that EV2 = β × EV2'for each ΔT2. Here, ΔT2 is set to, for example, 10 seconds. β is set to 1.5. In other words, in the second operation, the opening degree (pulse) of the outdoor expansion valve (28) increases by 50% every 10 seconds. The second operation is continuously performed until the second condition of step ST7 is satisfied.

As described above, in the present embodiment, the speed at which the opening degree of the outdoor expansion valve (28) is increased during the second operation is faster than the speed at which the opening degree of the outdoor expansion valve (28) is decreased during the first operation.

In the second operation, as the opening degree of the outdoor expansion valve (28) increases, the flow rate and pressure of the refrigerant flowing through the internal heat exchanger (73) increase. Here, the second operation is executed after the condition that the opening degree of the internal expansion valve (72) is increased is satisfied in step ST3, except when the conditions c) and d) are satisfied. .. Therefore, a sufficient flow rate of the refrigerant flowing through the internal heat exchanger (73) can be secured. The oil accumulated in the internal heat exchanger (73) is dissolved in the liquid refrigerant or the gas-liquid two-phase refrigerant and then sucked into the compressor (21,22,23). As a result, the oil accumulated in the internal heat exchanger (73) can be quickly recovered.

As described above, the speed at which the opening degree of the outdoor expansion valve (28) is increased during the second operation is faster than the speed at which the opening degree of the outdoor expansion valve (28) is decreased during the first operation. Therefore, in a situation where the opening degree of the internal expansion valve (72) is large, the refrigerant can be quickly sent to the internal heat exchanger (73), and the oil in the internal heat exchanger (73) can be quickly sent. It can be collected in a compressor (21,22,23).

The second operation is continuously executed until the second condition is satisfied in the next step ST7.

In step ST7, it is determined whether or not the second condition for executing the third operation is satisfied during the second operation. The second condition includes the following conditions f) to i). In this example, when any one of the conditions from f) to i) is satisfied, the process proceeds to steps ST8 and ST9, and the third operation is executed.

F) The current hydraulic pressure (Ps) is larger than the specified value. Strictly speaking, the current hydraulic pressure (Ps) is larger than the hydraulic pressure (Ps1) × A immediately before the start of the second operation stored in step ST5. Here, the coefficient A is set to, for example, 2.0.

G) Inhalation superheat (SSH) is smaller than the second value. Strictly speaking, the state in which the inhalation superheat degree (SSH) is smaller than the second value continues for t3 for a predetermined time. Here, the second value is set to, for example, about several ° C to 10 ° C, and t3 is set to about several tens of seconds.

H) Discharge superheat degree (DSH) is smaller than the specified value. Strictly speaking, the state in which the discharge superheat degree (DSH) is smaller than the predetermined value is continuous for t4 for a predetermined time. Here, this predetermined value is set to, for example, about several tens of degrees, and t4 is set to about several tens of seconds.

I) t5 has passed since the second operation was executed. Here, t5 is set to about several minutes. t5 is shorter than t1 under the condition e) above.

The above f) is a condition for determining that the oil in the internal heat exchanger (73) has been recovered by the compressor (21,22,23) by the second operation. When the pressure (hydraulic pressure (Ps)) on the downstream side of the outdoor expansion valve (28) is larger than a predetermined value, it indicates that the opening degree of the outdoor expansion valve (28) is large. Strictly speaking, the fact that the hydraulic pressure (Ps) is larger than the hydraulic pressure (Ps1) × A (A = 2.0) immediately before the start of the second operation means that the opening of the outdoor expansion valve (28) is due to the second operation. Indicates that is large enough. Therefore, when the condition of f) is satisfied, sufficient liquid refrigerant is sent to the internal heat exchanger (73), and the oil of the internal heat exchanger (73) is sent to the compressor (21,22,23). It can be estimated that it was recovered. Therefore, on condition that the hydraulic pressure (Ps) is larger than the predetermined value (hydraulic pressure (Ps1) × A), the oil in the internal heat exchanger (73) is transferred to the compressor (21,22,23). It can be accurately determined that it has been recovered.

In addition, the condition of f) uses only the pressure of the refrigerant as an index. The pressure of the refrigerant is highly responsive compared to the temperature of the refrigerant. Therefore, by setting f) as the second condition, it can be quickly determined that the oil in the internal heat exchanger (73) has been recovered by the compressor (21,22,23).

The above g) is a condition for determining that the oil in the internal heat exchanger (73) has been recovered by the compressor (21,22,23) by the second operation. When the suction superheat degree (SSH) is smaller than a predetermined value, it indicates that sufficient liquid refrigerant is being sent to the internal heat exchanger (73). When the suction superheat degree (SSH) is smaller than the predetermined value for t3 consecutive times, the liquid refrigerant is continuously sent to the internal heat exchanger (73), and the oil is sent to the compressor (21,22,23) together with the refrigerant. ) Can be estimated to have been recovered. Therefore, on condition that the suction superheat degree (SSH) is smaller than the predetermined value, strictly speaking, this state is continuous for t3 hours, the oil of the internal heat exchanger (73) is compressed (21,22). , 23) can be accurately determined to have been recovered.

The above h) is a condition set from the viewpoint of protection of the refrigerating apparatus (1). When the second operation is executed and the opening degree of the outdoor expansion valve (28) is increased, there is a possibility that the wet refrigerant is sucked into the compressor (21,22,23). In this case, the oil in the compressor (21,22,23) is diluted, which may lead to poor lubrication of the sliding portion. Therefore, the second operation is terminated on the condition that the discharge superheat degree (DSH) is smaller than a predetermined value, strictly speaking, this state is continuous for t4 hours. This can protect the compressor (21,22,23).

The above i) is a condition for determining that the oil in the internal heat exchanger (73) has been recovered by the compressor (21,22,23) by the second operation. In the second operation, the opening degree of the outdoor expansion valve (28) increases with the passage of time. Therefore, by setting i) on which the predetermined time t5 has elapsed as the second condition, it can be determined that the oil in the internal heat exchanger (73) has been recovered by the compressor (21,22,23). The predetermined time t5 is set sufficiently long so that the above conditions f) and g) are satisfied first. The condition of l) can be said to be a protective condition for terminating the second operation even when the conditions of f) and g) are not satisfied, for example, when a sensor failure or false detection occurs.

In step ST7, when any of the above conditions f) to i) is satisfied, the process proceeds to step ST8, and further determination as to whether or not to retain the second operation is performed. In step ST8, when any of the conditions j) to l) is satisfied, the process proceeds to step ST9. Here, j) is a condition in which the high pressure (HP) is larger than a predetermined value. This predetermined value is set to several MPa. k) is a condition in which the maximum discharge temperature (TdMAX) is smaller than a predetermined value. The maximum discharge temperature (TdMAX) is the maximum value among the discharge refrigerant temperatures (Td1, Td2, Td3) detected by each discharge temperature sensor (61,62,63). This predetermined value is set to, for example, a value of around 100 ° C. i) is a condition in which a predetermined time t6 has elapsed since the transition to step ST8. t6 is set to about several minutes. If the second condition of step ST7 is satisfied, the determination of ST8 may be omitted and the process may proceed to step ST9.

When moving to step ST9, the third operation is executed. In the third operation, the opening degree of the outdoor expansion valve (28) returns to the opening degree (Psl1) immediately before the start of the first operation. This opening degree (Psl1) is the opening degree stored in step ST1. In this example, this opening degree (Psl1) is the maximum opening degree of the outdoor expansion valve (28). Then, the oil recovery operation is completed, and the above-mentioned cold operation is performed.

-Effect of embodiment-
In the above embodiment, the compression element (C), the liquid pipe (43) (third pipe), the heat source expansion valve (28) (outdoor expansion valve) connected to the liquid pipe (43), and the heat source heat exchanger ( 25) Utilization unit (70) (cooling unit) having (outdoor heat exchanger) and utilization heat exchanger (73) (internal heat exchanger) and utilization expansion valve (72) (internal expansion valve) ), It is a heat source unit that constitutes a refrigerant circuit (10) that performs a refrigeration cycle using the heat source heat exchanger (25) as a radiator and the utilization heat exchanger (73) as an evaporator. Further, a controller (80) (controller) for controlling the heat source unit (20) is further provided so as to execute an oil recovery operation for recovering the oil of the utilization heat exchanger (73) during the refrigeration cycle. The oil recovery operation includes a first operation of reducing the opening degree of the heat source expansion valve (28) and a second operation of increasing the opening degree of the heat source expansion valve (28) after the first operation. The controller (80) is configured to execute the second operation when the first condition is satisfied during the first operation, and the first condition is the heat source expansion valve (the heat source expansion valve (43) in the liquid pipe (43). At least the condition that the difference ΔP between the pressure of the refrigerant on the downstream side of 28) and the pressure of the suction refrigerant of the compression element (C) is smaller than a predetermined value is included.

In this embodiment, the first condition is that the difference ΔP between the hydraulic pressure (Ps) and the low pressure pressure (Ps) is smaller than a predetermined value, so that the opening degree of the internal expansion valve (72) is large. It can be judged accurately.

In addition, since this condition uses only pressure as an index, it is more responsive than the case where temperature is used as an index. Therefore, it can be quickly determined that the opening degree of the internal expansion valve (72) is large.

In addition, ΔP can be obtained by using the low pressure pressure sensor (67) and the liquid side pressure sensor (68) of the heat source unit (20). Therefore, it can be determined that the first condition is satisfied regardless of the specifications of the cooling unit (70). The same judgment can be made even if the cooling unit (70) is replaced.

In the above embodiment, the first condition includes a condition in which the inhalation superheat degree (SSH) is larger than the first value.

In this embodiment, since the first condition is that the suction superheat degree (SSH) is larger than the first value, it can be accurately determined that the opening degree of the internal expansion valve (72) is large.

In addition, the suction superheat degree (SSH) can be obtained by using the suction temperature sensor (66) and the low pressure pressure sensor (67) of the heat source unit (20). Therefore, it can be determined that the first condition is satisfied regardless of the specifications of the cooling unit (70). The same judgment can be made even if the cooling unit (70) is replaced.

In the above embodiment, when the second condition is satisfied during the second operation of the controller (80), the opening degree of the heat source expansion valve (28) is set to the opening degree immediately before the start of the first operation. The second condition is configured to execute three operations, and the second condition includes a condition in which the suction superheat degree (SSH) is smaller than the second value.

In this embodiment, the second condition is that the suction superheat degree (SSH) is smaller than the second value, so that the oil in the internal heat exchanger (73) is recovered by the compressor (21,22,23). Can be judged accurately.

In the above embodiment, when the second condition is satisfied during the second operation, the controller (80) sets the opening degree of the heat source expansion valve (28) to the opening degree immediately before the start of the first operation. The second condition is configured to execute the three operations, and includes a condition in which the pressure of the refrigerant on the downstream side of the heat source expansion valve (28) in the liquid pipe (43) becomes higher than a predetermined value.

In this embodiment, the second condition is that the hydraulic pressure (Ps) on the downstream side of the outdoor expansion valve (28) in the third pipe (43) is higher than a predetermined value, so that the opening degree of the outdoor expansion valve (28) is increased. It can be determined that it is sufficiently large, and it can be accurately determined that the oil in the internal heat exchanger (73) has been recovered by the compressor (21,22,23).

In addition, since this condition uses only pressure as an index, it is more responsive than the case where temperature is used as an index. Therefore, it can be quickly determined that the oil has been recovered in the compressor (21,22,23).

In addition, the pressure (Ps) can be obtained by using the low pressure pressure sensor (67) and the liquid side pressure sensor (68) of the heat source unit (20). Therefore, it can be determined that the first condition is satisfied regardless of the specifications of the cooling unit (70). The same judgment can be made even if the cooling unit (70) is replaced.

In particular, in the above embodiment, in order to compare the current hydraulic pressure (Ps) with the hydraulic pressure (Ps1) immediately before the start of the second operation, the opening degree of the outdoor expansion valve (28) is sufficiently large due to the second operation. It can be determined more reliably that it has become.

In the above embodiment, the speed at which the opening degree of the heat source expansion valve (28) is increased during the second operation is faster than the speed at which the opening degree of the heat source expansion valve (28) is decreased during the first operation.

In this embodiment, in the second operation, in a situation where the opening degree of the internal expansion valve (72) is large, in order to quickly increase the opening degree of the outdoor expansion valve (28), the internal heat exchanger (73) is used. Oil can be quickly recovered in the compressor (21,22,23).

In addition, in the first operation, the opening degree of the outdoor expansion valve (28) is gradually reduced. Therefore, it is possible to prevent the high pressure pressure (HP) from becoming excessively high or the low pressure pressure (LP) from becoming excessively low due to the opening degree of the outdoor expansion valve (28) becoming excessively small. it can.

<< Other Embodiments >>
The first condition may include at least the condition a) above, and preferably includes the condition b) above. The second condition preferably includes the condition of f) or the condition of g).

The refrigerating device (1) of the above embodiment is a refrigerating device that cools the air in the refrigerator. However, the freezing device (1) may be an air conditioner that air-conditions the indoor air, or may be a freezing device that simultaneously cools the air inside the refrigerator and air-conditions the indoor air.

The utilization expansion valve (72) is a temperature-sensitive automatic expansion valve. However, the utilization expansion valve (72) may be an expansion valve that adjusts the opening degree based on the degree of superheat of the refrigerant after evaporation, and may be an electronic expansion valve.

The utilization heat exchanger (73) is an air heat exchanger that exchanges heat between air and a refrigerant. However, the utilization heat exchanger (73) may be a heat exchanger that exchanges heat between the refrigerant and a predetermined heat medium (for example, water).

Although the embodiments and modifications have been described above, it will be understood that various modifications of the forms and details are possible without departing from the purpose and scope of the claims. In addition, the above embodiments and modifications may be appropriately combined or replaced as long as they do not impair the functions of the present disclosure. The above-mentioned descriptions of "first", "second", "third" ... Are used to distinguish the words and phrases to which these descriptions are given, and the number and order of the words and phrases are also limited. It's not something to do.

As described above, the present disclosure is useful for heat source units and refrigeration equipment.

10 Refrigerant circuit 20 Outdoor unit (heat source unit)
20a Heat source circuit 25 Outdoor heat exchanger (heat source heat exchanger)
28 Outdoor expansion valve (heat source expansion valve)
43 Third pipe (liquid pipe)
70 Cold installation unit (utilization unit)
72 Internal expansion valve (utilization expansion valve)
73 Internal heat exchanger (utilized heat exchanger)
80 controller (controller)

Claims

It has a compression element (C), a liquid pipe (43), a heat source expansion valve (28) connected to the liquid pipe (43), and a heat source heat exchanger (25).
By connecting to a utilization unit (70) having a utilization heat exchanger (73) and a utilization expansion valve (72), the utilization heat exchanger (25) is used as a radiator and the utilization heat exchanger (73) is evaporated. A heat source unit composed of a refrigerant circuit (10) that performs a refrigeration cycle
A controller (80) for controlling the heat source unit (20) to execute an oil recovery operation for recovering oil from the utilization heat exchanger (73) during the refrigeration cycle is provided.
The oil recovery operation includes a first operation of reducing the opening degree of the heat source expansion valve (28) and a second operation of increasing the opening degree of the heat source expansion valve (28) after the first operation. ,
The controller (80) is configured to execute the second operation when the first condition is satisfied during the first operation.
The first condition is a condition in which the difference ΔP between the pressure of the refrigerant on the downstream side of the heat source expansion valve (28) in the liquid pipe (43) and the pressure of the suction refrigerant of the compression element (C) is smaller than a predetermined value. A heat source unit characterized by containing at least.
In claim 1,
The first condition is a heat source unit characterized in that the suction superheat degree includes a condition larger than the first value.
In claim 1 or 2,
When the second condition is satisfied during the second operation, the controller (80) executes a third operation in which the opening degree of the heat source expansion valve (28) is set to the opening degree immediately before the start of the first operation. Is configured as
The second condition is a heat source unit characterized in that the suction superheat degree is smaller than the second value.
In any one of claims 1 to 3,
When the second condition is satisfied during the second operation, the controller (80) executes a third operation in which the opening degree of the heat source expansion valve (28) is set to the opening degree immediately before the start of the first operation. Is configured as
The second condition is a heat source unit including a condition in which the pressure of the refrigerant on the downstream side of the heat source expansion valve (28) in the liquid pipe (43) becomes higher than a predetermined value.
In any one of claims 1 to 4,
A heat source unit characterized in that the speed at which the opening degree of the heat source expansion valve (28) is increased during the second operation is faster than the speed at which the opening degree of the heat source expansion valve (28) is decreased during the first operation. ..
The heat source unit (20) according to any one of claims 1 to 5, and a utilization unit (70) having a utilization heat exchanger (73) and a utilization expansion valve (72) are provided. ) And the utilization unit (70), a refrigerant circuit (10) that performs a refrigeration cycle using the heat source heat exchanger (25) as a radiator and the utilization heat exchanger (73) as an evaporator. Is composed of a refrigeration system.
In claim 6,
The utilization expansion valve (72) is a refrigeration apparatus characterized by being a temperature automatic expansion valve.