EP3486578A1

EP3486578A1 - Refrigeration device

Info

Publication number: EP3486578A1
Application number: EP17836720.7A
Authority: EP
Inventors: Azuma Kondou
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2016-08-04
Filing date: 2017-07-14
Publication date: 2019-05-22
Anticipated expiration: 2037-07-14
Also published as: CN109564034A; JP2018021723A; WO2018025614A1; EP3486578A4; CN109564034B; EP3486578B1; JP6323508B2

Abstract

A refrigeration apparatus (10) includes a utilization-side unit (12) and a heat source-side unit (11) connected together through a pair of connection pipes (14, 15). When the utilization-side unit (12) is switched from a cooling state to a suspended state, a controller (90) closes a heat source-side expansion valve (38), and then stops a compressor (31a-31c) and closes a utilization-side solenoid valve (62). This can avoid a liquid hammer phenomenon that occurs upon opening the utilization-side solenoid valve (62) of the utilization-side unit (12).

Description

TECHNICAL FIELD

The present invention relates to a refrigeration apparatus that circulates a refrigerant through a refrigerant circuit to perform a refrigeration cycle.

BACKGROUND ART

A refrigerant circuit of a refrigeration apparatus that performs a refrigeration cycle may be provided with a solenoid valve to control the flow of a refrigerant. A general solenoid valve interrupts the passage of electric current through a solenoid for switching between an open state and a closed state.
The refrigerant circuit of the refrigeration apparatus includes a pipe through which a high-pressure liquid refrigerant flows. The pipe may be provided with a solenoid valve. When closed, the solenoid valve blocks the flow of the high-pressure liquid refrigerant. If the solenoid valve opens when there is a large differential pressure between both sides of the solenoid valve, a substantially incompressible liquid refrigerant having a relatively high density suddenly flows downstream of the solenoid valve, resulting in a liquid hammer phenomenon. This may break a pipe, an expansion valve, or any other component.
Patent Document 1 discloses that, in order to prevent a liquid hammer phenomenon that occurs when the solenoid valve opens, a pipe through which a liquid refrigerant flows is heated with an electric heater. Specifically, heating the pipe with the electric heater allows part of the refrigerant in the pipe to evaporate, thereby producing a compressible gas refrigerant in the pipe. This reduces the degree of the sudden increase in the internal pressure of the pipe upon opening the solenoid valve.

CITATION LIST

PATENT DOCUMENT

[Patent Document 1] Japanese Unexamined Patent Publication No. H11-325654

SUMMARY OF THE INVENTION

TECHNICAL PROBLEM

The refrigeration apparatus of Patent Document 1 described above needs to include the electric heater for heating the pipe in order to prevent the liquid hammer phenomenon caused upon opening the solenoid valve. This increases the number of parts of the refrigeration apparatus, resulting in an increase in the manufacturing cost. While the solenoid valve is closed, the electric heater needs to keep heating the pipe. This may increase power consumption of the refrigeration apparatus, resulting in the increase in the running cost of the refrigeration apparatus.
In view of the foregoing background, it is therefore an object of the present invention to curb the increases in the manufacturing and running costs of a refrigeration apparatus, and reduce the possibility of a liquid hammer phenomenon that occurs upon opening a solenoid valve.

SOLUTION TO THE PROBLEM

A first aspect of the present disclosure is directed to a refrigeration apparatus which includes a refrigerant circuit (20) in which a heat source-side unit (11) and a utilization-side unit (12) are connected together through a liquid-side connection pipe (14) and a gas-side connection pipe (15), the refrigeration apparatus allowing a refrigerant to circulate through the refrigerant circuit (20) to perform a refrigeration cycle. The heat source-side unit (11) includes a compressor (31a-31c), a heat source-side heat exchanger (33), and a heat source-side expansion valve (38) provided for a pipe (53c) sending the refrigerant condensed in the heat source-side heat exchanger (33) to the liquid-side connection pipe (14), the utilization-side unit (12) includes a utilization-side heat exchanger (61), a utilization-side expansion valve (63), and a utilization-side solenoid valve (62), which are arranged in series. The utilization-side unit (12) is switchable between a cooling state where the utilization-side solenoid valve (62) opens to allow the utilization-side heat exchanger (61) to function as an evaporator, and a suspended state where the utilization-side solenoid valve (62) is closed to block the refrigerant from flowing through the utilization-side heat exchanger (61). The refrigeration apparatus further includes a controller (90) configured to close the heat source-side expansion valve (38) when the utilization-side unit (12) is switched from the cooling state to the suspended state, and then stop the compressor (31a-31c) and close the utilization-side solenoid valve (62).
In the first aspect, the heat source-side unit (11) and a plurality of utilization-side units (12) are provided for the refrigerant circuit (20). The refrigerant condensed in the heat source-side heat exchanger (33) of the heat source-side unit (11) flows into the utilization-side units (12) through the liquid-side connection pipe (14). The refrigerant supplied through the liquid-side connection pipe (14) to the utilization-side units (12) expands when passing through the associated utilization-side expansion valve (63), and then flows into the associated utilization-side heat exchanger (61) to evaporate. In the utilization-side heat exchanger (61), the refrigerant cools a target to be cooled, such as air. The refrigerant evaporated in the utilization-side heat exchanger (61) of the utilization-side unit (12) flows into the heat source-side unit (11) through the gas-side connection pipe (15), and thereafter, is sucked into the compressor (31a-31c) to be compressed.
In the first aspect, when the utilization-side unit (12) is switched from a cooling state to a suspended state, the controller (90) performs a predetermined operation. The operation of this controller (90) will be described below. The controller (90) first closes the heat source-side expansion valve (38). At this time, since the compressor (31a-31c) is operating, the pressure of the refrigerant in the liquid-side connection pipe (14) gradually decreases. The controller (90) then stops the compressor (31a-31c) and closes the utilization-side solenoid valve (62). Therefore, when the utilization-side solenoid valve (62) is closed, the density of the refrigerant present toward the inlet side of the utilization-side solenoid valve (62) is lowered as compared with the case where the utilization-side unit (12) is in the cooling state.
According to a second aspect of the present disclosure, when the utilization-side unit (12) is switched from the cooling state to the suspended state, the controller (90) is configured to perform a preparatory operation before closing the heat source-side expansion valve (38), the preparatory operation reducing a degree of opening of the heat source-side expansion valve (38) so that a refrigerant flowing through the liquid-side connection pipe (14) is brought into a gas-liquid two-phase state.
When the utilization-side unit (12) is switched from the cooling state to the suspended state, the controller (90) of the second aspect closes the heat source-side expansion valve (38) after performing the preparatory operation. In the preparatory operation, the controller (90) reduces the degree of opening of the heat source-side expansion valve (38) so that the refrigerant flowing through the liquid-side connection pipe (14) turns to be a gas-liquid two-phase refrigerant. Therefore, when the heat source-side expansion valve (38) is closed and then the utilization-side solenoid valve (62) is closed, both of the liquid refrigerant and the gas refrigerant are present in the liquid-side connection pipe (14).
According to a third aspect of the present disclosure, the heat source-side unit (11) includes: a liquid-side pressure sensor (87) which measures a pressure of the refrigerant sent from the heat source-side expansion valve (38) to the liquid-side connection pipe (14); and a liquid-side temperature sensor (82) which measures a temperature of the refrigerant sent from the heat source-side expansion valve (38) to the liquid-side connection pipe (14), and the controller (90) is configured to perform, as the preparatory operation, an operation of reducing the degree of opening of the heat source-side expansion valve (38) so that the pressure measured by the liquid-side pressure sensor (87) becomes lower than a saturation pressure of the refrigerant at the temperature measured by the liquid-side temperature sensor (82).
In the third aspect, the controller (90) performs the preparatory operation using the pressure measured by the liquid-side pressure sensor (87) and the temperature measured by the liquid-side temperature sensor (82). When the controller (90) performs the preparatory operation and the pressure measured by the liquid-side pressure sensor (87) becomes lower than the saturation pressure of the refrigerant at the temperature measured by the liquid-side temperature sensor (82), the refrigerant flowing through the liquid-side connection pipe (14) is in a gas-liquid two-phase state.

ADVANTAGES OF THE INVENTION

In the first aspect, when the utilization-side unit (12) is switched from the cooling state to the suspended state, the controller (90) performs a predetermined operation. Therefore, when the utilization-side solenoid valve (62) is closed, the density of the refrigerant present toward the inlet side of the utilization-side solenoid valve (62) is lowered as compared with the case where the utilization-side unit (12) is in the cooling state.
The lower the density of the refrigerant present toward the inlet side of the utilization-side solenoid valve (62) in the closed state is, the more the possibility of the adverse effect caused by the liquid hammer phenomenon upon opening the utilization-side solenoid valve (62) decreases. On the other hand, according to the first aspect, the density of the refrigerant present toward the inlet side of the utilization-side solenoid valve (62) can be reduced in advance with the pressure of the refrigerant in the liquid-side connection pipe (14) reduced before the utilization-side solenoid valve (62) is closed. Thus, this aspect can reduce the density of the refrigerant present toward the inlet side of the utilization-side solenoid valve (62) in the closed state, thereby reducing the risk of a liquid hammer phenomenon that occurs upon opening the utilization-side solenoid valve (62).
When the utilization-side unit (12) is switched from the cooling state to the suspended state, the controller (90) according to the second aspect closes the heat source-side expansion valve (38) after performing the preparatory operation. Therefore, when the utilization-side solenoid valve (62) is closed after the heat source-side expansion valve (38) is closed, a gas refrigerant having compressibility is present in the liquid-side connection pipe (14). In the presence of the gas refrigerant in the liquid-side connection pipe (14), a change in the volume of the gas refrigerant reduces a pressure variation at the time of opening the utilization-side solenoid valve (62). Hence, in this aspect, the gas refrigerant present in the liquid-side connection pipe (14) can further reduce the risk of a liquid hammer phenomenon that occurs upon opening the utilization-side solenoid valve (62).
According to the third aspect, the controller (90) performs the preparatory operation using the values measured by the liquid-side pressure sensor (87) and the liquid-side temperature sensor (82), so that the refrigerant flowing through the liquid-side connection pipe (14) can be reliably brought into the gas-liquid two-phase state.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a refrigerant circuit diagram showing a schematic configuration for a refrigeration apparatus according to a first embodiment.
FIG. 2 is a refrigerant circuit diagram showing a refrigeration apparatus in a normal mode.
FIG. 3 is a block diagram showing a configuration for a main controller.
FIG. 4 is a flowchart showing an operation performed by a liquid hammer avoidance control section of the main controller.
FIG. 5 is a refrigerant circuit diagram showing a schematic configuration for a refrigeration apparatus according to a second embodiment.

DESCRIPTION OF EMBODIMENTS

Embodiments of the present invention will be described in detail with reference to the drawings. Note that the following embodiments and variations are merely beneficial examples in nature, and are not intended to limit the scope, applications, or use of the invention.

«First Embodiment»

A first embodiment will be described. A refrigeration apparatus (10) according to this embodiment is used to cool an internal space in a refrigerator.
As shown in FIG. 1, the refrigeration apparatus (10) includes a single heat source-side unit (11) and a single utilization-side unit (12). The heat source-side unit (11) is a so-called outdoor unit, and is installed outdoors. The utilization-side unit (12) is a so-called unit cooler, and is installed in the internal space of the refrigerator.
The heat source-side unit (11) is provided with a heat source-side circuit (21), a heat source-side fan (22), and a main controller (90). Meanwhile, the utilization-side unit (12) is provided with a utilization-side circuit (23), a utilization-side fan (24), a drain pan (25), and a utilization-side controller (99).
The refrigeration apparatus (10) includes a refrigerant circuit (20) in which the heat source-side circuit (21) of the heat source-side unit (11) and the utilization-side circuit (23) of the utilization-side unit (12) are connected together through a liquid-side connection pipe (14) and a gas-side connection pipe (15). The refrigerant circuit (20) allows a refrigerant to circulate therethrough to perform a vapor compression refrigeration cycle.
The heat source-side circuit (21) has a liquid-side end and a gas-side end respectively provided with a liquid-side shutoff valve (VI) and a gas-side shutoff valve (V2). The liquid-side connection pipe (14) provides connection between the liquid-side shutoff valve (VI) of the heat source-side circuit (21) and the liquid-side end of the utilization-side circuit (23). The gas-side connection pipe (15) provides connection between the gas-side shutoff valve (V2) of the heat source-side circuit (21) and the gas-side end of the utilization-side circuit (23).

-Heat Source-Side Circuit-

The heat source-side circuit (21) includes first through third compressors (31a, 31b, 31c), a four-way switching valve (32), a heat source-side heat exchanger (33), a subcooling heat exchanger (34), a subcooling expansion valve (35), first through third intermediate expansion valves (36a, 36b, 36c), a receiver (37), a heat source-side expansion valve (38), first through third check valves (CV1-CV3), and an oil separator (41). The heat source-side circuit (21) is provided with a discharge refrigerant pipe (51), a suction refrigerant pipe (52), a heat source-side liquid refrigerant pipe (53), an injection pipe (54), a first connection pipe (55), a second connection pipe (56), and an oil return pipe (57). Note that the number of the compressors (31a-31c) of the heat source-side unit (11) is merely an example.

The first through third compressors (31a, 31b, 31c) are all hermetic scroll compressors. Each compressor (31a-31c) has a suction port, an intermediate port, and a discharge port. The compressor (31a-31c) compresses a refrigerant sucked therein through the suction port, and discharges the compressed refrigerant through the discharge port. The intermediate port of the compressor (31a-31c) is used to introduce a refrigerant into a compression chamber in the course of compression.
The first compressor (31a) has a variable capacity. An electric motor of the first compressor (31a) is supplied with power from an inverter outside the drawing. Changing the output frequency of the inverter triggers a change in the rotational speed of the first compressor (31a). This causes the operating capacity of the first compressor (31a) to vary. On the other hand, the second and third compressors (31b) and (31c) each have a fixed capacity. The second and third compressors (31b) and (31c) rotate at a constant rotational speed.

<Four-Way Switching Valve>

The four-way switching valve (32) is switchable between a first state (indicated by the solid curves shown in FIG. 1) and a second state (indicated by the dashed curves shown in FIG. 1). In the first state, a first port communicates with a third port, and a second port communicates with a fourth port. In the second state, the first port communicates with the fourth port, and the second port communicates with the third port.
The first port of the four-way switching valve (32) is connected to the discharge ports of the compressors (31a-31c) through the discharge refrigerant pipe (51), and the second port thereof is connected to the suction ports of the compressors (31a-31c) through the suction refrigerant pipe (52). The third port of the four-way switching valve (32) is connected to the gas-side end of the heat source-side heat exchanger (33), and the fourth port thereof is connected to the gas-side shutoff valve (V2).

The discharge refrigerant pipe (51) includes the same number of (three in this embodiment) discharge pipes (51a, 51b, 51c) as the compressors (31a-31c), and a single discharge collection pipe (51d). One end of the first discharge pipe (51a) is connected to the discharge port of the first compressor (31a), one end of the second discharge pipe (51b) is connected to the discharge port of the second compressor (31b), and one end of the third discharge pipe (51c) is connected to the discharge port of the third compressor (31c). The other end of each discharge pipe (51a, 51b, 51c) is connected to one end of the discharge collection pipe (51d). The other end of the discharge collection pipe (51d) is connected to the first port of the four-way switching valve (32).
The suction refrigerant pipe (52) includes the same number of (three in this embodiment) suction pipes (52a, 52b, 52c) as the compressors (31a-31c), and a single main suction pipe (52d). One end of the first suction pipe (52a) is connected to the suction port of the first compressor (31a), one end of the second suction pipe (52b) is connected to the suction port of the second compressor (31b), and one end of the third suction pipe (52c) is connected to the suction port of the third compressor (31c). The other end of each suction pipe (52a, 52b, 52c) is connected to one end of the main suction pipe (52d). The other end of the main suction pipe (52d) is connected to the second port of the four-way switching valve (32).

The heat source-side heat exchanger (33) is a cross-fin, fin-and-tube heat exchanger, and exchanges heat between a refrigerant and outdoor air. The heat source-side heat exchanger (33) has a liquid-side end connected to the heat source-side liquid refrigerant pipe (53), and a gas-side end connected to the third port of the four-way switching valve (32). The heat source-side fan (22) for supplying the outdoor air to the heat source-side heat exchanger (33) is disposed near the heat source-side heat exchanger (33).

The subcooling heat exchanger (34) is a so-called plate-type heat exchanger. The subcooling heat exchanger (34) has a plurality of first flow paths (34a) and a plurality of second flow paths (34b). The subcooling heat exchanger (34) exchanges heat between a refrigerant flowing through the first flow paths (34a) and a refrigerant flowing through the second flow paths (34b).

The heat source-side liquid refrigerant pipe (53) has one end connected to the heat source-side heat exchanger (33), and the other end connected to the liquid-side shutoff valve (VI). The heat source-side liquid refrigerant pipe (53) includes three heat source-side liquid pipes (53a, 53b, 53c). The first heat source-side liquid pipe (53a) provides connection between the liquid-side end of the heat source-side heat exchanger (33) and the inlet of the receiver (37). The second heat source-side liquid pipe (53b) provides connection between the outlet of the receiver (37) and the inlets of the first flow paths (34a) of the subcooling heat exchanger (34). The third heat source-side liquid pipe (53c) provides connection between the outlets of the first flow paths (34a) of the subcooling heat exchanger (34) and the liquid-side shutoff valve (VI).
The first heat source-side liquid pipe (53a) is provided with a first check valve (CV1). The first check valve (CV1) allows the refrigerant to flow from the heat source-side heat exchanger (33) toward the receiver (37), and blocks the refrigerant from flowing in the reverse direction.
The third heat source-side liquid pipe (53c) is provided with the heat source-side expansion valve (38) and a second check valve (CV2) arranged in this order from the subcooling heat exchanger (34) toward the liquid-side shutoff valve (VI). The heat source-side expansion valve (38) is an electric expansion valve having a variable degree of opening. The second check valve (CV2) allows the refrigerant to flow from the subcooling heat exchanger (34) toward the liquid-side shutoff valve (VI), and blocks the refrigerant from flowing in the reverse direction.

The injection pipe (54) includes two main injection pipes (54m, 54n), and three injection branch pipes (54a, 54b, 54c).
The first main injection pipe (54m) has one end connected to a portion of the third heat source-side liquid pipe (53c) between the subcooling heat exchanger (34) and the heat source-side expansion valve (38), and the other end connected the inlets of the second flow paths (34b) of the subcooling heat exchanger (34). The first main injection pipe (54m) constitutes a subcooling pipe. The first main injection pipe (54m) is provided with the subcooling expansion valve (35). One end of the second main injection pipe (54n) is connected to the outlets of the second flow paths (34b) of the subcooling heat exchanger (34). The other end of the second main injection pipe (54n) is connected to one end of each injection branch pipe (54a, 54b, 54c).
The other ends of the first, second, and third injection branch pipes (54a), (54b), and (54c) are respectively connected to the intermediate ports of the first, second, and third compressors (31a), (31b), and (31c). The injection branch pipes (54a-54c) are respectively provided with the intermediate expansion valves (36a, 36b, 36c). Each intermediate expansion valve (36a-36c) is an electric expansion valve having a variable degree of opening.

One end of the first connection pipe (55) is connected to a portion of the third heat source-side liquid pipe (53c) between the second check valve (CV2) and the liquid-side shutoff valve (VI), and the other end thereof is connected to a portion of the first heat source-side liquid pipe (53a) between the first check valve (CV1) and the receiver (37). The first connection pipe (55) is provided with a third check valve (CV3). The third check valve (CV3) allows the refrigerant to flow from the one end toward the other end of the first connection pipe (55), and blocks the refrigerant from flowing in the reverse direction.
One end of the second connection pipe (56) is connected to a portion of the third heat source-side liquid pipe (53c) between the heat source-side expansion valve (38) and the second check valve (CV2), and the other end thereof is connected to a portion of the first heat source-side liquid pipe (53a) between the heat source-side heat exchanger (33) and the first check valve (CV1). The second connection pipe (56) is provided with a fourth check valve (CV4). The fourth check valve (CV4) allows the refrigerant to flow from the one end toward the other end of the second connection pipe (56), and blocks the refrigerant from flowing in the reverse direction.

The oil separator (41) is provided for the discharge collection pipe (51d) of the discharge refrigerant pipe (51). A gas refrigerant containing refrigerating machine oil in the form of mist is discharged from the compressors (31a-31c). The oil separator (41) separates the refrigerating machine oil from the refrigerant discharged from the compressors (31a-31c).
The oil return pipe (57) is used to return the refrigerating machine oil from the oil separator (41) to the compressors (31a-31c). The oil return pipe (57) has one end connected to the oil separator (41), and the other end connected to the second main injection pipe (54n). The oil return pipe (57) is provided with a capillary tube (42).

The heat source-side circuit (21) is provided with a plurality of temperature sensors (81a, 81b, 81c, 82) and a plurality of pressure sensors (85, 86, 87).
The discharge pipes (51a, 51b, 51c) of the discharge refrigerant pipe (51) are respectively provided with first through third discharge refrigerant temperature sensors (81a, 81b, 81c). The first discharge refrigerant temperature sensor (81a) is attached to the first discharge pipe (51a) to measure the temperature of the refrigerant discharged from the first compressor (31a). The second discharge refrigerant temperature sensor (81b) is attached to the second discharge pipe (51b) to measure the temperature of the refrigerant discharged from the second compressor (31b). The third discharge refrigerant temperature sensor (81c) is attached to the third discharge pipe (51c) to measure the temperature of the refrigerant discharged from the third compressor (31c).
The heat source-side liquid refrigerant pipe (53) is provided with a liquid refrigerant temperature sensor (82). The liquid refrigerant temperature sensor (82) is attached to the third heat source-side liquid pipe (53c) to measure the temperature of the refrigerant flowing through the third heat source-side liquid pipe (53c). The liquid refrigerant temperature sensor (82) is a liquid-side temperature sensor.
A discharge pressure sensor (85) is connected to the discharge collection pipe (51d) of the discharge refrigerant pipe (51) to measure the pressure of the refrigerant discharged from the compressors (31a-31c). A suction pressure sensor (86) is connected to the main suction pipe (52d) of the suction refrigerant pipe (52) to measure the pressure of the refrigerant yet to be sucked into the compressors (31a-31c). A liquid refrigerant pressure sensor (87) is connected to the third heat source-side liquid pipe (53c) of the heat source-side liquid refrigerant pipe (53) to measure the pressure of the refrigerant flowing through the third heat source-side liquid pipe (53c). The liquid refrigerant pressure sensor (87) is a liquid-side pressure sensor.

-Utilization-Side Circuit-

The utilization-side circuit (23) includes a utilization-side heat exchanger (61), a drain pan heater (71b), a utilization-side solenoid valve (62), and a utilization-side expansion valve (63). The utilization-side circuit (23) is provided with a utilization-side liquid refrigerant pipe (71) and a utilization-side gas refrigerant pipe (72).

<Utilization-Side Heat Exchanger>

The utilization-side heat exchanger (61) is a cross-fin, fin-and-tube heat exchanger, and exchanges heat between the refrigerant and the indoor air. The utilization-side fan (24) for supplying the indoor air to the utilization-side heat exchanger (61) is disposed near the utilization-side heat exchanger (61).

The drain pan heater (71b) is configured as a pipe of the drain pan (25) disposed below the utilization-side heat exchanger (61). The drain pan heater (71b) is used to heat the drain pan (25) to prevent drain water from being frozen.

<Utilization-Side Liquid Refrigerant Pipe, Utilization-Side Gas Refrigerant Pipe>

The utilization-side liquid refrigerant pipe (71) includes a first utilization-side liquid pipe (71a) and a second utilization-side liquid pipe (71c). One end of the first utilization-side liquid pipe (71a) is connected to the liquid-side connection pipe (14), and the other end thereof is connected to one end of the drain pan heater (71b). The one end of the first utilization-side liquid pipe (71a) constitutes the liquid-side end of the utilization-side circuit (23). The second utilization-side liquid pipe (71c) has one end connected to the other end of the drain pan heater (71b), and the other end connected to the liquid-side end of the utilization-side heat exchanger (61).
One end of the utilization-side gas refrigerant pipe (72) is connected to the gas-side end of the utilization-side heat exchanger (61), and the other end thereof is connected to the gas-side connection pipe (15). The other end of the utilization-side gas refrigerant pipe (72) constitutes the gas-side end of the utilization-side circuit (23).

<Utilization-Side Solenoid Valve, Utilization-Side Expansion Valve>

The utilization-side solenoid valve (62) and the utilization-side expansion valve (63) are provided for the second utilization-side liquid pipe (71c) of the utilization-side liquid refrigerant pipe (71). The utilization-side expansion valve (63) is disposed at a portion of the second utilization-side liquid pipe (71c) between the utilization-side solenoid valve (62) and the utilization-side heat exchanger (61).
The utilization-side solenoid valve (62) interrupts the passage of electric current through a solenoid for switching between an open state and a closed state. While the utilization-side solenoid valve (62) is in the open state, the utilization-side unit (12) is in a cooling state where the utilization-side heat exchanger (61) functions as an evaporator to cool the indoor air. While the utilization-side solenoid valve (62) is in the closed state, the utilization-side unit (12) is in a suspended state where the flow of the refrigerant through the utilization-side heat exchanger (61) is blocked.
The utilization-side expansion valve (63) is an externally equalized thermostatic expansion valve. A sensing bulb (63a) of the utilization-side expansion valve (63) is provided near one end of the utilization-side gas refrigerant pipe (72) (near the end toward the utilization-side heat exchanger (61)). An equalizer (63b) of the utilization-side expansion valve (63) is connected to a portion of the utilization-side gas refrigerant pipe (72) near one end thereof.

-Main Controller-

As shown in FIG. 2, the main controller (90) of the heat source-side unit (11) includes a compressor control section (91), an intermediate expansion valve control section (92), a subcooling expansion valve control section (93), and a liquid hammer avoidance control section (94). The main controller (90) receives values input from the temperature sensors (81a, 81b, 81c, 82) and the pressure sensors (85, 86, 87) provided for the heat source-side unit (11). The main controller (90) receives a thermo-off signal from the utilization-side controller (99) of the utilization-side unit (12). A control operation performed by the main controller (90) will be described later.

-Utilization-Side Controller-

The utilization-side unit (12) is provided with a suction air temperature sensor (26). The suction air temperature sensor (26) measures the temperature of indoor air that has not passed through the utilization-side heat exchanger (61) yet. The utilization-side controller (99) receives a value measured by the suction air temperature sensor (26). The utilization-side controller (99) opens and closes the utilization-side solenoid valve (62) in accordance with the value measured by the suction air temperature sensor (26). The utilization-side controller (99) outputs the thermo-off signal if the utilization-side solenoid valve (62) is to be closed. An operation performed by the utilization-side controller (99) will be described later.

-Operation of Refrigeration Apparatus-

The refrigeration apparatus (10) operates in a selected one of a normal mode for cooling an internal space or a defrosting mode for melting frost formed on the utilization-side heat exchanger (61). Here, the normal mode will be described in detail, but the defrosting mode will not be described.
In the defrosting mode, the four-way switching valve (32) is set to the second state, the utilization-side heat exchanger (61) functions as a condenser, and the heat source-side heat exchanger (33) functions as an evaporator. In the defrosting mode, the utilization-side fan (24) stops.

The operation of the refrigeration apparatus (10) in the normal mode will be described with reference to FIG. 2. The refrigerant circuit (20) operating in the normal mode allows the refrigerant to circulate to perform a refrigeration cycle, in which the heat source-side heat exchanger (33) functions as a condenser, and the utilization-side heat exchanger (61) functions as an evaporator.
The operation in the normal mode in which both of the utilization-side units (12) are in the cooling state and all the compressors (31a-31c) are operating will now be exemplified.
As shown in FIG. 2, the four-way switching valve (32) is set to the first state in the normal mode. The main controller (90) controls the subcooling expansion valve (35), the intermediate expansion valves (36a, 36b, 36c), and the heat source-side expansion valve (38). An operation of the main controller (90) will be described later. In the case shown in FIG. 2, the utilization-side solenoid valves (62) of the utilization-side units (12) are set to the open state.
The refrigerant discharged from the compressors (31a-31c) passes through the oil separator (41) in the discharge refrigerant pipe (51), then flows into the heat source-side heat exchanger (33) through the four-way switching valve (32), and dissipates heat to the outdoor air in the heat source-side heat exchanger (33) to condense. The refrigerant (high-pressure refrigerant) flowing out of the heat source-side heat exchanger (33) sequentially passes through the first heat source-side liquid pipe (53a), the receiver (37), and the second heat source-side liquid pipe (53b) in this order, flows into the first flow paths (34a) of the subcooling heat exchanger (34), and is cooled by the refrigerant flowing through the second flow paths (34b) of the subcooling heat exchanger (34). Part of the subcooled liquid refrigerant that has flowed from the first flow paths (34a) of the subcooling heat exchanger (34) into the third heat source-side liquid pipe (53c) flows into the first main injection pipe (54m). The remaining part sequentially passes through the heat source-side expansion valve (38) and the liquid-side shutoff valve (VI) in this order, and then flows into the liquid-side connection pipe (14).
The refrigerant that has flowed into the liquid-side connection pipe (14) is introduced in the utilization-side circuit (23) of the utilization-side unit (12). In the utilization-side circuit (23), the refrigerant that has flowed into the first utilization-side liquid pipe (71a) passes through the drain pan heater (71b), and then flows into the utilization-side solenoid valve (62) through the second utilization-side liquid pipe (71c). The refrigerant that has passed through the utilization-side solenoid valve (62) expands when passing through the utilization-side expansion valve (63), and turns to be a gas-liquid two-phase refrigerant, which then flows into the utilization-side heat exchanger (61). The refrigerant that has flowed into the utilization-side heat exchanger (61) absorbs heat from the indoor air to evaporate. As a result, the indoor air is cooled. The utilization-side unit (12) sends the indoor air cooled in the utilization-side heat exchanger (61) back to the internal space.
The refrigerant that has evaporated in the utilization-side heat exchanger (61) flows into the gas-side connection pipe (15) through the utilization-side gas refrigerant pipe (72). Flows of the refrigerant from the utilization-side circuits (23) enter and merge together in the gas-side connection pipe (15). Then, the merged refrigerant flows into the heat source-side circuit (21), sequentially passes through the gas-side shutoff valve (V2) and the four-way switching valve (32) in this order, and thereafter, is sucked into the compressors (31a-31c) through the suction refrigerant pipe (52).
Meanwhile, the refrigerant that has flowed into the first main injection pipe (54m) expands when passing through the subcooling expansion valve (35), and turns to be a gas-liquid two-phase refrigerant, which then flows into the second flow paths (34b) of the subcooling heat exchanger (34), and absorbs heat from the refrigerant (high-pressure refrigerant) flowing through the first flow paths (34a) of the subcooling heat exchanger (34) to evaporate. The refrigerant that has flowed into the second main injection pipe (54n) through the second flow paths (34b) of the subcooling heat exchanger (34) is introduced into the intermediate ports of the compressors (31a-31c).

-Operation of Utilization-Side Controller-

As described above, the utilization-side controller (99) in the utilization-side unit (12) opens and closes the utilization-side solenoid valve (62) in accordance with the value measured by the suction air temperature sensor (26). The operation of this utilization-side controller (99) will be described.
The utilization-side controller (99) controls the utilization-side solenoid valve (62) such that a value Tr measured by the suction air temperature sensor (26) is in the range of the set internal temperature Tr_set ± 1°C (i.e., Tr_set - 1 ≤ Tr ≤ Tr_set + 1).
Suppose that the utilization-side solenoid valve (62) is open. While the utilization-side solenoid valve (62) is open, the utilization-side unit (12) is in the cooling state. Specifically, the refrigerant flows into the utilization-side heat exchanger (61) to evaporate. As a result, the indoor air is cooled in the utilization-side heat exchanger (61). While the utilization-side solenoid valve (62) is open, the temperature of the indoor air (i.e., the value Tr measured by the suction air temperature sensor (26)) gradually decreases. If the value Tr measured by the suction air temperature sensor (26) falls below Tr_set - 1 (i.e., Tr < Tr_set - 1 is met), the utilization-side controller (99) switches the utilization-side solenoid valve (62) from the open state to the closed state. Switching the utilization-side solenoid valve (62) from the open state to the closed state, the utilization-side controller (99) outputs, to the main controller (90), the thermo-off signal indicating that the utilization-side unit (12) has been suspended.
While the utilization-side solenoid valve (62) is closed, the utilization-side unit (12) is in the suspended state. Specifically, the flow of a refrigerant through the utilization-side heat exchanger (61) is blocked, and the indoor air is not cooled in the utilization-side heat exchanger (61). While the utilization-side solenoid valve (62) is closed, the temperature of the indoor air (i.e., the value Tr measured by the suction air temperature sensor (26)) gradually increases. If the value Tr measured by the suction air temperature sensor (26) exceeds Tr_set + 1 (i.e., Tr_set + 1 < Tr is met), the utilization-side controller (99) switches the utilization-side solenoid valve (62) from the closed state to the open state.
Note that the utilization-side controller (99) is configured to be capable of receiving a valve open command output from the main controller (90). The valve open command will be described in detail later. Upon receipt of the valve open command, the utilization-side controller (99) keeps the utilization-side solenoid valve (62) open until the valve open command is canceled. In other words, during a period from when the valve open command is received to when the valve open command is canceled, the utilization-side controller (99) keeps the utilization-side solenoid valve (62) open even if the value Tr measured by the suction air temperature sensor (26) falls below Tr_set - 1.

-Operation of Main Controller-

As described above, the main controller (90) includes the compressor control section (91), the intermediate expansion valve control section (92), the subcooling expansion valve control section (93), and the liquid hammer avoidance control section (94). Operations performed by the compressor control section (91), the intermediate expansion valve control section (92), the subcooling expansion valve control section (93), and the liquid hammer avoidance control section (94) will be described. The main controller (90) operates the four-way switching valve (32) for the switching between the normal mode and the defrosting mode, and controls the rotational speed of the heat source-side fan (22).

The compressor control section (91) adjusts the operating capacity of the first compressor (31a), and switches the second and third compressors (31b) and (31c) between an on state and an off state, such that the value measured by the suction pressure sensor (86) reaches a predetermined target pressure.
If the cooling capacity of the utilization-side unit (12) is low with respect to a load required to cool the indoor air, the evaporating pressure of the refrigerant in the utilization-side heat exchanger (61) (i.e., the low pressure of the refrigeration cycle) increases. The low pressure of the refrigeration cycle is substantially equal to the value measured by the suction pressure sensor (86). Thus, if the value measured by the suction pressure sensor (86) exceeds the target pressure, the compressor control section (91) performs an operation to increase the operating capacities of the compressors (31a-31c). In other words, in this case, the compressor control unit (91) performs an operation of increasing the output frequency of the inverter and increasing the operating capacity of the first compressor (31a), and an operation of starting one of the second and third compressors (31b) and (31c) which is stopped.
On the other hand, if the cooling capacity of the utilization-side unit (12) is high with respect to the load required to cool the indoor air, the evaporating pressure of a refrigerant in the utilization-side heat exchanger (61) (i.e., the low pressure of the refrigeration cycle) decreases. Thus, if the value measured by the suction pressure sensor (86) falls below the target pressure, the compressor control section (91) performs an operation to reduce the operating capacities of the compressors (31a-31c). Specifically, in this case, the compressor control section (91) performs an operation of gradually reducing the output frequency of the inverter to reduce the operating capacity of the first compressor (31a), and an operation of suspending one of the second and third compressors (31b) and (31c) which is operating.

The intermediate expansion valve control section (92) adjusts the degrees of opening of the intermediate expansion valves (36a-36c). The intermediate expansion valve control section (92) adjusts the degree of opening of the first intermediate expansion valve (36a) in accordance with the values measured by the first discharge refrigerant temperature sensor (81a) and the discharge pressure sensor (85), adjusts the degree of opening of the second intermediate expansion valve (36b) in accordance with the values measured by the second discharge refrigerant temperature sensor (81b) and the discharge pressure sensor (85), and adjusts the degree of opening of the third intermediate expansion valve (36c) in accordance with the values measured by the third discharge refrigerant temperature sensor (81c) and the discharge pressure sensor (85).
An operation in which the intermediate expansion valve control section (92) adjusts the degree of opening of the first intermediate expansion valve (36a) will be described below. The intermediate expansion valve control section (92) adjusts the degrees of opening of the second and third intermediate expansion valves (36b) and (36c) in the same way.
If the value measured by the first discharge refrigerant temperature sensor (81a) exceeds a predetermined upper limit temperature, the intermediate expansion valve control section (92) performs an operation of increasing the degree of opening of the first intermediate expansion valve (36a) to reduce the value measured by the first discharge refrigerant temperature sensor (81a).
On the other hand, if the value measured by the first discharge refrigerant temperature sensor (81a) falls below the predetermined upper limit temperature, the intermediate expansion valve control section (92) adjusts the degree of opening of the first intermediate expansion valve (36a) such that the superheat of the refrigerant discharged from the first compressor (31a) reaches a predetermined target discharge superheat. Specifically, the intermediate expansion valve control section (92) calculates the superheat of the refrigerant discharged from the first compressor (31a) using the values measured by the first discharge refrigerant temperature sensor (81a) and the discharge pressure sensor (85). If the calculated superheat exceeds the target discharge superheat, the intermediate expansion valve control section (92) increases the degree of opening of the first intermediate expansion valve (36a). If the calculated superheat falls below the target discharge superheat, the intermediate expansion valve control section (92) reduces the degree of opening of the first intermediate expansion valve (36a).
If one or more of the compressors (31a-31c) respectively associated with the intermediate expansion valves (36a-36c) are operating, the intermediate expansion valve control section (92) adjusts the degree of opening of the associated intermediate expansion valve(s) (36a-36c). If one or more of the compressors (31a-31c) respectively associated with the intermediate expansion valves (36a-36c) are suspending, the intermediate expansion valve control section (92) keeps the associated intermediate expansion valve(s) (36a-36c) fully closed. Specifically, the intermediate expansion valve control section (92) adjusts the degree of opening of the second intermediate expansion valve (36b) while the second compressor (31b) is operating, and keeps the second intermediate expansion valve (36b) fully closed while the second compressor (31b) is suspending. Further, the intermediate expansion valve control section (92) adjusts the degree of opening of the third intermediate expansion valve (36c) while the third compressor (31c) is operating, and keeps the second intermediate expansion valve (36b) fully closed while the second compressor (31b) is suspending.

The subcooling expansion valve control section (93) adjusts the degree of opening of the subcooling expansion valve (35) in accordance with the temperature of the liquid refrigerant sent from the heat source-side unit (11) to the liquid-side connection pipe (14) during the operation in the normal mode. The temperature of the liquid refrigerant sent from the heat source-side unit (11) to the liquid-side connection pipe (14) during the operation in the normal mode is substantially equal to the value measured by the liquid refrigerant temperature sensor (82). Thus, the subcooling expansion valve control section (93) adjusts the degree of opening of the subcooling expansion valve (35) such that the value measured by the liquid refrigerant temperature sensor (82) reaches a predetermined target liquid refrigerant temperature (e.g., 20°C). If an operation is performed in the normal mode and the heat source-side expansion valve (38) is fully open, the degree of subcooling of the liquid refrigerant sent from the heat source-side unit (11) to the liquid-side connection pipe (14) is generally about 0°C to 20°C.
Specifically, if the value measured by the liquid refrigerant temperature sensor (82) exceeds the target liquid refrigerant temperature, the subcooling expansion valve control section (93) reduces the degree of opening of the subcooling expansion valve (35), and reduces the temperature of the refrigerant sent from the subcooling expansion valve (35) to the second flow paths (34b) of the subcooling heat exchanger (34). On the other hand, if the value measured by the liquid refrigerant temperature sensor (82) falls below the target liquid refrigerant temperature, the subcooling expansion valve control section (93) increases the degree of opening of the subcooling expansion valve (35), and increases the temperature of the refrigerant sent from the subcooling expansion valve (35) to the second flow paths (34b) of the subcooling heat exchanger (34).

The liquid hammer avoidance control section (94) performs control to avoid a liquid hammer phenomenon. This control to avoid the liquid hammer phenomenon is performed when the utilization-side unit (12) is switched from the cooling state to the suspended state. Here, the liquid hammer avoidance control will be described with reference to the flowchart of FIG. 4.
First, in Step ST1, the liquid hammer avoidance control section (94) determines whether or not the liquid hammer avoidance control section (94) has received a thermo-off signal from the utilization-side unit (12). If the main controller (90) has not received the thermo-off signal, no liquid hammer phenomenon occurs, so that the liquid hammer avoidance control section (94) finishes the liquid hammer avoidance control. On the other hand, when the liquid hammer avoidance control section (94) has received the thermo-off signal, the liquid hammer avoidance control section (94) proceeds to Step ST2.
In Step ST2, the liquid hammer avoidance control section (94) outputs a valve open command to the utilization-side controller (99). This valve open command is a command signal for causing the utilization-side controller (99) to keep the utilization-side solenoid valve (62) open. As described above, upon receipt of the valve open command, the utilization-side controller (99) keeps the utilization-side solenoid valve (62) open until the valve open command is canceled.
Subsequently, the liquid hammer avoidance control section (94) performs a preparatory operation. This preparatory operation is an operation of reducing the degree of opening of the heat source-side expansion valve (38) before closing the heat source-side expansion valve (38) so that the refrigerant flowing through the liquid-side connection pipe (14) turns to be a gas-liquid two-phase refrigerant. In the flowchart of FIG. 4, Steps ST3 to ST5 correspond to the preparatory operation.
In Step ST3, the liquid hammer avoidance control section (94) sets a target pressure Ps_t which is a target value of the refrigerant pressure of the liquid-side connection pipe (14). More specifically, the liquid hammer avoidance control section (94) reads the measurement value TL of the liquid refrigerant temperature sensor (82). The liquid hammer avoidance control section (94) calculates a saturation pressure of the refrigerant at the measurement value TL using the read measurement value TL and the physical property of the refrigerant, and sets the value of the saturation pressure to the target pressure Ps_t.
In subsequent Step ST4, the liquid hammer avoidance control section (94) reduces the degree of opening of the heat source-side expansion valve (38) so that the value Ps measured by the liquid refrigerant pressure sensor (87) reaches the target pressure Ps_t. Note that a reduction amount of the degree of opening of the heat source-side expansion valve (38) in Step ST4 may be a predetermined constant value or a value adjusted in accordance with the value Ps measured by the liquid refrigerant pressure sensor (87) and the target pressure Ps_t.
In subsequent Step ST5, the liquid hammer avoidance control section (94) reads the value Ps measured by the liquid refrigerant pressure sensor (87), and compares the read measurement value Ps with the target pressure Ps_t. If the measured value Ps is higher than or equal to the target pressure Ps_t (Ps ≥ Ps_t), the liquid hammer avoidance control section (94) returns to Step ST4, and further reduces the degree of opening of the heat source-side expansion valve (38). On the other hand, if the measured value Ps is lower than the target pressure Ps_t (Ps < Ps_t), it can be determined that the refrigerant flowing through the liquid-side connection pipe (14) is in the gas-liquid two-phase state. In this case, the liquid hammer avoidance control section (94) proceeds to Step ST6, and fully closes the heat source-side expansion valve (38).
When the heat source-side expansion valve (38) is fully closed, no refrigerant is supplied from the heat source-side circuit (21) to the liquid-side connection pipe (14). At this point in time, the compressors (31a-31c) continue to operate. Therefore, in the refrigerant circuit (20), the refrigerant pressure decreases in the liquid-side connection pipe (14), the utilization-side circuit (23), and the gas-side connection pipe (15).
In subsequent Step ST7, the liquid hammer avoidance control section (94) reads the value LP measured by the suction pressure sensor (86), and compares the read measurement value LP with the lower limit pressure LP_min stored in advance. If the measured value LP is higher than or equal to the lower limit pressure LP min (LP ≥ LP_min), the liquid hammer avoidance control section (94) stands by as it is. On the other hand, if the measured value LP is lower than the lower limit pressure LP_min (LP < LP_min), the liquid hammer avoidance control section (94) proceeds to Step ST8, and stops the compressors (31a-31c).
In subsequent Step ST9, the liquid hammer avoidance control section (94) cancels the valve open command output in Step ST2, and finishes the liquid hammer avoidance control. At this time, the utilization-side controller (99) of the utilization-side unit (12) outputs the thermo-off signal. Thus, the value Tr measured by the suction air temperature sensor (26) already falls below Tr_set - 1. Therefore, when the liquid hammer avoidance control section (94) cancels the valve open command, the utilization-side controller (99) of the utilization-side unit (12) closes the utilization-side solenoid valve (62).

-Advantages of First Embodiment-

In the refrigerating apparatus (10) of this embodiment, when the utilization-side unit (12) is switched from the cooling state to the suspended state, the liquid hammer avoidance control section (94) of the main controller (90) performs the liquid hammer avoidance control. In other words, the liquid hammer avoidance control section (94) fully closes the heat source-side expansion valve (38) upon receiving the thermo-off signal from the utilization-side unit (12), and thereafter, stops the compressors (31a-31c) when the measurement value LP of the suction pressure sensor (86) falls below the lower limit pressure LP_min, and cancels the valve open command.
At a time when the valve open command is canceled and the utilization-side controller (99) closes the utilization-side solenoid valve (62), the refrigerant pressure of the liquid-side connection pipe (14) is sufficiently lowered. Therefore, when the utilization-side solenoid valve (62) is closed, the density of the refrigerant present toward the inlet side of the utilization-side solenoid valve (62) is lowered as compared with the case where the utilization-side unit (12) is in the cooling state. Thus, this embodiment can reduce the density of the refrigerant present toward the inlet side of the utilization-side solenoid valve (62) in the closed state, thereby reducing the risk of a liquid hammer phenomenon that occurs upon opening the utilization-side solenoid valve (62).
Furthermore, when the utilization-side unit (12) is switched from the cooling state to the suspended state, the liquid hammer avoidance control section (94) of this embodiment performs the preparatory operation, and then sets the heat source-side expansion valve (38) in the fully-closed state. In other words, the liquid hammer avoidance control section (94) narrows the opening of the heat source-side expansion valve (38) so that the refrigerant flowing through the liquid-side connection pipe (14) turns to be a gas-liquid two-phase refrigerant, and thereafter, sets the heat source-side expansion valve (38) into a fully closed state.
When the valve open command is canceled and the utilization-side controller (99) closes the utilization-side solenoid valve (62), both of the liquid refrigerant and the gas refrigerant are present in the liquid-side connection pipe (14). In the presence of the gas refrigerant in the liquid-side connection pipe (14), a change in the volume of the gas refrigerant reduces a pressure variation at the time of opening the utilization-side solenoid valve (62). Hence, in this embodiment, the presence of the gas refrigerant in the liquid-side connection pipe (14) makes it possible to further reduce the risk of a liquid hammer phenomenon that occurs upon opening the utilization-side solenoid valve (62).

«Second Embodiment»

A second embodiment will be described. The following description of a refrigeration apparatus (10) of this embodiment will be focused on differences from the refrigeration apparatus (10) of the first embodiment.
As shown in FIG. 5, the refrigeration apparatus (10) of this embodiment includes a plurality of (two in this embodiment) utilization-side units (12A, 12B). Each utilization-side unit (12) is a so-called unit cooler. The two utilization-side units (12A, 12B) shown in FIG. 5 are installed in an interior space of a single refrigerator (i.e., a single space). Note that the number of the utilization-side units (12) is merely an example.
The two utilization-side units (12A, 12B) are arranged in parallel in a refrigerant circuit (20). In other words, in the refrigerant circuit (20) of this embodiment, a liquid-side connection pipe (14) is connected to the liquid-side end of a utilization-side circuit (23) of each of the utilization-side units (12A, 12B), and a gas-side connection pipe (15) is connected to the gas-side end of the utilization-side circuit (23) of each of the utilization-side units (12A, 12B).
In the refrigeration apparatus (10) of this embodiment, only the first utilization-side unit (12A) includes a utilization-side controller (99) and a suction air temperature sensor (26). This utilization-side controller (99) controls a utilization-side solenoid valve (62) of the first utilization-side unit (12A) and a utilization-side solenoid valve (62) of the second utilization-side unit (12B).
In other words, if the value Tr measured by the suction air temperature sensor (26) falls below Tr_set - 1 (i.e., Tr < Tr_set - 1 is met), the utilization-side controller (99) switches the utilization-side solenoid valve (62) of each of the utilization-side units (12A, 12B) from the open state to the closed state. As a result, the two utilization-side units (12A, 12B) are simultaneously switched from the cooling state to the suspended state.
When the value Tr measured by the suction air temperature sensor (26) exceeds Tr_set + 1 (i.e., Tr > Tr_set + 1 is met), the utilization-side controller (99) switches the utilization-side solenoid valve (62) of each of the utilization-side units (12A, 12B) from the closed state to the open state. As a result, the two utilization-side units (12A, 12B) are simultaneously switched from the suspended state to the cooling state.
As with the refrigeration apparatus (10) of the first embodiment, the main controller (90) of the refrigeration apparatus (10) of this embodiment also includes the liquid hammer avoidance control section (94). The liquid hammer avoidance control section (94) performs the liquid hammer avoidance control shown in FIG. 4.

INDUSTRIAL APPLICABILITY

As can be seen from the foregoing description, the present invention is useful for a refrigeration apparatus which allows a refrigerant to circulate through a refrigerant circuit to perform a refrigeration cycle.

DESCRIPTION OF REFERENCE CHARACTERS

10: Refrigeration Apparatus
11: Heat Source-Side Unit
12: Utilization-Side Unit
14: Liquid-Side Connection Pipe
15: Gas-Side Connection Pipe
20: Refrigerant Circuit
31a: First Compressor
31b: Second Compressor
31c: Third Compressor
33: Heat Source-Side Heat Exchanger
34: Subcooling Heat Exchanger
35: Heat Source-Side Expansion Valve
53c: Third Heat Source-Side Liquid Pipe (Pipe)
61: Utilization-Side Heat Exchanger
63: Utilization-Side Expansion Valve
62: Utilization-Side Solenoid Valve
82: Liquid Refrigerant Temperature Sensor (Liquid-Side Temperature Sensor)
87: Liquid Refrigerant Pressure Sensor (Liquid-Side Pressure Sensor)
90: Controller

Claims

A refrigeration apparatus comprising:
a refrigerant circuit (20) in which a heat source-side unit (11) and a utilization-side unit (12) are connected together through a liquid-side connection pipe (14) and a gas-side connection pipe (15),

the refrigeration apparatus allowing a refrigerant to circulate through the refrigerant circuit (20) to perform a refrigeration cycle, wherein

the heat source-side unit (11) includes a compressor (31a-31c), a heat source-side heat exchanger (33), and a heat source-side expansion valve (38) provided for a pipe (53c) sending the refrigerant condensed in the heat source-side heat exchanger (33) to the liquid-side connection pipe (14),

the utilization-side unit (12) includes a utilization-side heat exchanger (61), a utilization-side expansion valve (63), and a utilization-side solenoid valve (62), which are arranged in series, the utilization-side unit (12) being switchable between a cooling state where the utilization-side solenoid valve (62) opens to allow the utilization-side heat exchanger (61) to function as an evaporator, and a suspended state where the utilization-side solenoid valve (62) is closed to block the refrigerant from flowing through the utilization-side heat exchanger (61), and

the refrigeration apparatus further comprises a controller (90) configured to close the heat source-side expansion valve (38) when the utilization-side unit (12) is switched from the cooling state to the suspended state, and then stop the compressor (31a-31c) and close the utilization-side solenoid valve (62).
The refrigeration apparatus of claim 1, wherein
when the utilization-side unit (12) is switched from the cooling state to the suspended state, the controller (90) is configured to perform a preparatory operation before closing the heat source-side expansion valve (38), the preparatory operation reducing a degree of opening of the heat source-side expansion valve (38) so that a refrigerant flowing through the liquid-side connection pipe (14) is brought into a gas-liquid two-phase state.
The refrigeration apparatus of claim 2, wherein
the heat source-side unit (11) includes:
a liquid-side pressure sensor (87) which measures a pressure of the refrigerant sent from the heat source-side expansion valve (38) to the liquid-side connection pipe (14); and

a liquid-side temperature sensor (82) which measures a temperature of the refrigerant sent from the heat source-side expansion valve (38) to the liquid-side connection pipe (14), and

the controller (90) is configured to perform, as the preparatory operation, an operation of reducing the degree of opening of the heat source-side expansion valve (38) so that the pressure measured by the liquid-side pressure sensor (87) becomes lower than a saturation pressure of the refrigerant at the temperature measured by the liquid-side temperature sensor (82).