JP2002357374A - Refrigerating equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To efficiently exert the heating capacity of an air conditioning heat exchanger and the cooling capacity of a refrigerating heat exchanger or the like. SOLUTION: A heat recovery operation conducts the circulation wherein a refrigerant discharged from a compressor (2B) is condensed in the air conditioning heat exchanger (41), passes through an expansion valve (46), evaporates in the refrigerating heat exchanger (45) and a freezing heat exchanger (51) and returns to the compressor (2B). A capacity excess operation for heating conducts the circulation wherein part of the refrigerant discharged from the compressor (2B) is condensed in the air conditioning heat exchanger (41), while the other refrigerant condenses in an outdoor heat exchanger (4), and all the condensed liquid refrigerants pass through the expansion valve (46), evaporate in the refrigerating heat exchanger (45) and the freezing heat exchanger (51) and returns to the compressor (2B). The capacity excess operation for heating conducts the circulation wherein the refrigerant discharged from the compressor (2B) is condensed in the air conditioning heat exchanger (41), part of the condensed liquid refrigerant passes through the expansion valve (46) and evaporates in the refrigerating heat exchanger (45) and the freezing heat exchanger (51), while the other liquid refrigerant passes through an expansion valve (26) and evaporates in the outdoor heat exchanger (4), and an evaporated gas refrigerant returns to the compressor (2B).

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

[0001] The present invention relates to a refrigeration apparatus,
In particular, the present invention relates to a refrigeration system including an air conditioning heat exchanger and a cooling heat exchanger.

[0002]

2. Description of the Related Art Hitherto, a refrigerating apparatus for performing a refrigerating cycle has been known, and is widely used as an air conditioner for cooling and heating a room or a refrigerator for storing foods and the like.
Some refrigeration systems perform both air conditioning and refrigeration, as disclosed in WO98 / 45651. This type of refrigerating apparatus includes, for example, a plurality of use side heat exchangers such as an air conditioning heat exchanger and a refrigeration heat exchanger, and is installed in a convenience store or the like. This refrigeration apparatus can perform both air conditioning in a store and cooling of a showcase or the like by installing only one refrigeration apparatus.

[0003]

In the conventional refrigeration system described above, since the air conditioning heat exchanger performs only the cooling operation, it is conceivable that the air conditioning heat exchanger performs the heating operation.
However, there is a problem that energy-saving operation with little waste cannot be performed simply by performing the heating operation of the air-conditioning heat exchanger. In particular, the cooling capacity of a refrigeration heat exchanger or the like must always maintain a predetermined value because it is necessary to maintain the quality of the product. Therefore, it is necessary to satisfy the cooling requirement of the refrigeration heat exchanger and the like, and to be able to exhibit the heating capacity of the air conditioning heat exchanger.

[0004] The present invention has been made in view of the above points, and has as its object to efficiently exhibit the heating capacity of an air conditioning heat exchanger and the cooling capacity of a cooling heat exchanger.

[0005]

Specifically, as shown in FIG. 1, the first invention comprises a compressor (2B), a heat source side heat exchanger (4), and an expansion mechanism (26, 46,...). ), An air conditioning heat exchanger (41) that air-conditions the room, and a cooling heat exchanger (4
5) is connected to form a refrigerant circuit (1E) in which the refrigerant circulates. In the refrigerant circuit (1E), the refrigerant discharged from the compressor (2B) condenses in the air-conditioning heat exchanger (41), evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26). Heating operation in which the refrigerant returns to the compressor (2B) and the refrigerant discharged from the compressor (2B) condenses in the air-conditioning heat exchanger (41) and passes through the expansion mechanism (46) to the cooling heat exchanger (45). ), A heat recovery operation in which the refrigerant evaporates and returns to the compressor (2B), and the refrigerant discharged from the compressor (2B) condenses in the heat source side heat exchanger (4) and passes through the expansion mechanism (46). Cooling heat exchanger (4
It is configured to at least selectively perform the refrigeration operation of performing the circulation that evaporates in 5) and returns to the compressor (2B).

Further, the second invention comprises a compressor (2B), a heat source side heat exchanger (4), an expansion mechanism (26, 46...), And an air conditioning heat exchanger (41) for air-conditioning a room. A refrigerant circuit (1E) is connected to a cooling heat exchanger (45) for cooling the inside of the refrigerator and circulates refrigerant. And the refrigerant circuit (1E)
The refrigerant discharged from the compressor (2B) condenses in the air-conditioning heat exchanger (41), evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26), and returns to the compressor (2B). In the heating operation in which circulation is performed, part of the refrigerant discharged from the compressor (2B) is condensed in the air-conditioning heat exchanger (41), and other refrigerant is condensed in the heat source side heat exchanger (4). All the liquid refrigerant is expanded by the expansion mechanism (4
6) After passing through the cooling heat exchanger (45) and evaporating, the compressor (2B)
Excessive capacity heating operation to circulate back to the refrigerant, and the refrigerant discharged from the compressor (2B) condenses in the heat source side heat exchanger (4) and passes through the expansion mechanism (46) to the cooling heat exchanger (45). It is configured to at least selectively perform a refrigeration operation for performing circulation that evaporates and returns to the compressor (2B).

A third aspect of the present invention relates to a compressor (2B), a heat source side heat exchanger (4), an expansion mechanism (26, 46...), And an air conditioning heat exchanger (41) for air-conditioning a room. A refrigerant circuit (1E) is connected to a cooling heat exchanger (45) for cooling the inside of the refrigerator and circulates refrigerant. And the refrigerant circuit (1E)
The refrigerant discharged from the compressor (2B) condenses in the air-conditioning heat exchanger (41), evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26), and returns to the compressor (2B). In the heating operation for circulation, the refrigerant discharged from the compressor (2B) is condensed in the air-conditioning heat exchanger (41), and a part of the condensed liquid refrigerant passes through the expansion mechanism (46). ), The other liquid refrigerant evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26), and the gas refrigerant evaporates back to the compressor (2B). The refrigerant discharged from the compressor (2B) condenses in the heat source side heat exchanger (4), and the expansion mechanism (46)
And a refrigeration operation of circulating through the cooling heat exchanger (45) and returning to the compressor (2B).

In a fourth aspect based on the first or second aspect, in the refrigerant circuit (1E), the refrigerant discharged from the compressor (2B) is condensed and condensed in the air conditioning heat exchanger (41). Part of the liquid refrigerant evaporates in the cooling heat exchanger (45) via the expansion mechanism (46), and other liquid refrigerant evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26) and evaporates. Insufficient heating operation for circulating the gas refrigerant back to the compressor (2B) is configured to be selectable.

In a fifth aspect based on the second or third aspect, the refrigerant circuit (1E) is characterized in that the refrigerant discharged from the compressor (2B) is condensed in the air conditioning heat exchanger (41), and the expansion mechanism is provided. (46)
And a heat recovery operation of circulating through the cooling heat exchanger (45) and returning to the compressor (2B).

In a sixth aspect based on the first aspect, in the refrigerant circuit (1E), a part of the refrigerant discharged from the compressor (2B) is condensed in the air-conditioning heat exchanger (41), and Is condensed in the heat source side heat exchanger (4), and all the condensed liquid refrigerant evaporates in the cooling heat exchanger (45) via the expansion mechanism (46) and returns to the compressor (2B) for heating. Overcapacity operation of
The refrigerant discharged from the compressor (2B) is condensed in the air-conditioning heat exchanger (41), and part of the condensed liquid refrigerant evaporates in the cooling heat exchanger (45) via the expansion mechanism (46), and is condensed in other liquids. The refrigerant is evaporated in the heat source side heat exchanger (4) via the expansion mechanism (26), and the heating gas lacking operation for circulating the evaporated gas refrigerant back to the compressor (2B) is selectable. .

According to a seventh aspect of the present invention, in any one of the first to third aspects, the refrigerant circuit (1E) includes a plurality of compressors (2B, 2C...), And the refrigerant circuit (1E) The refrigerant recovery operation for recovering the excess refrigerant into the compressor (2B ...) is selectable.

In an eighth aspect based on any one of the first to third aspects, a floor heating heat exchanger (36) is provided in the refrigerant circuit (1E) in series with the air conditioning heat exchanger (41). The configuration is provided.

That is, in the first aspect, the operation is performed by switching between the heating operation, the heat recovery operation, and the freezing operation. In this heat recovery operation, efficient operation is performed without exhausting heat from the heat source side heat exchanger (4).

Further, in the second invention, the operation is performed by switching between the heating operation, the excess heating operation and the freezing operation. In this excess capacity operation, the heat of condensation is released from the heat source side heat exchanger (4), and the excess operation of the air conditioning heat exchanger (41) and the reduction in the capacity of the cooling heat exchanger (45) are suppressed.

Further, in the third invention, the operation is performed by switching between the heating operation, the insufficient heating insufficient operation, and the refrigeration operation. In this insufficient capacity operation, evaporation heat is released from the heat source side heat exchanger (4), and the capacity reduction of the air conditioning heat exchanger (41) and the excessive operation of the cooling heat exchanger (45) are suppressed.

Further, in the fourth to sixth inventions, claims 1 to 5 are provided.
In the invention of claim 3, at least one of the heat recovery operation, the excess capacity operation, and the insufficient excess operation is selected and switched to perform the operation.

Further, in the seventh invention, surplus refrigerant in the heat exchanger and the pipes is collected in the compressor (2B ...).

Further, in the eighth invention, the floor heating is performed by flowing the refrigerant to the floor heating heat exchanger (36).

[0019]

Therefore, according to the present invention, since the heating operation and the heat recovery operation are selectively performed, the operation corresponding to the operation conditions can be performed. As a result,
Energy-saving operation with less waste can be performed.

In particular, since the excess or insufficient heating capacity of the air conditioning heat exchanger (41) can be adjusted by the heat source side heat exchanger (4), the cooling capacity of the cooling heat exchanger (45) is reduced. It can always be kept at a predetermined value. As a result, the quality of a product such as a refrigerator can be reliably maintained.

In other words, when performing the heat recovery operation, since the heat is not exhausted from the heat source side heat exchanger (4), an efficient operation can be performed.

When the heating capacity is excessively operated, heat of condensation is released from the heat source side heat exchanger (4), resulting in excessive operation of the air conditioning heat exchanger (41) and reduced capacity of the cooling heat exchanger (45). Can be suppressed.

In the heating capacity shortage operation, the heat source side heat exchanger (4) releases the heat of evaporation, and the air conditioning heat exchanger (4).
It is possible to suppress the decrease in the capacity of 1) and the excessive operation of the cooling heat exchanger (45).

Further, according to the seventh aspect of the present invention, the surplus refrigerant under various operating conditions is recovered, so that the liquid back at the next start-up is prevented, the start-up can be performed smoothly, and the refrigerant charge amount can be improved. Can be reduced.

[0025]

Embodiment 1 Hereinafter, Embodiment 1 of the present invention will be described in detail with reference to the drawings.

As shown in FIG. 1, a refrigeration apparatus (1) according to the present embodiment is provided in a convenience store, and performs cooling of a showcase in a refrigerator and cooling and heating of a store in a room. is there.

The refrigerating apparatus (1) is provided with an outdoor unit (1).
A), an indoor unit (1B), a refrigeration unit (1C), and a refrigeration unit (1D), and a refrigerant circuit (1E) for performing a vapor compression refrigeration cycle. The refrigerant circuit (1E) is configured to switch between a cooling cycle and a heating cycle.

The indoor unit (1B) is configured to switch between a cooling operation and a heating operation, and is installed at, for example, a sales floor. In addition, the refrigeration unit (1C)
Is installed in a refrigerated showcase to cool the air inside the showcase. The refrigeration unit (1D) is installed in a refrigeration showcase and cools air in the refrigerator of the showcase.

<Outdoor unit> The above outdoor unit (1A)
Comprises a non-inverter compressor (2A), a first inverter compressor (2B), a second inverter compressor (2C), a first four-way switching valve (3A) and a second four-way switching valve (3B). ) And an outdoor heat exchanger (4) which is a heat source side heat exchanger.

Each of the compressors (2A, 2B, 2C) is, for example,
It is composed of a hermetic high-pressure dome type scroll compressor. The non-inverter compressor (2A) is of a constant capacity type in which the motor is always driven at a constant rotation speed. The first inverter compressor (2B) and the second inverter compressor (2C) are configured such that the electric motor is inverter-controlled and the capacity can be varied stepwise or continuously.

As a feature of the present invention, the non-inverter compressor (2A), the first inverter compressor (2B), and the second inverter compressor (2C) are composed of a first system compression mechanism (2D) and a second system. Of the compression mechanism (2E). That is, the non-inverter compressor (2A) and the first inverter compressor (2B) constitute a first system compression mechanism (2D), and the second inverter compressor (2C) is a second system compression mechanism (2C). 2E) and the non-inverter compressor (2A)
In some cases, a system compression mechanism (2D) is configured, and the first inverter compressor (2B) and the second inverter compressor (2C) configure a second system compression mechanism (2E). In short, the present invention is configured by the first system compressor and the second system compressor.

The non-inverter compressor (2A), the first inverter compressor (2B), and the second inverter compressor (2C)
Each discharge pipe (5a, 5b, 5c) is one high pressure gas pipe (8)
And the high-pressure gas pipe (8) is connected to the first four-way switching valve (3
A) is connected to one port. The discharge pipe (5a) of the non-inverter compressor (2A) and the discharge pipe (5c) of the second inverter compressor (2C) are provided with check valves (7).

The gas side end of the outdoor heat exchanger (4)
The outdoor gas pipe (9) is connected to one port of the first four-way switching valve (3A). One end of a liquid pipe (10), which is a liquid line, is connected to a liquid side end of the outdoor heat exchanger (4). In the middle of the liquid pipe (10), a receiver (14)
The other end of the liquid pipe (10) is connected to the first connecting liquid pipe (11).
And a second communication liquid pipe (12).

The outdoor heat exchanger (4) is, for example,
This is a cross-fin type fin-and-tube heat exchanger in which an outdoor fan (4F), which is a heat source fan, is disposed in close proximity.

The non-inverter compressor (2A) and the first
Each suction pipe (6a, 6b) of the inverter compressor (2B) is connected to a low-pressure gas pipe (15). The suction pipe (6c) of the second inverter compressor (2C) is connected to one port of the second four-way switching valve (3B).

A communication gas pipe (17) is connected to one port of the first four-way switching valve (3A). One port of the first four-way switching valve (3A) is connected to one port of the second four-way switching valve (3B) by a connection pipe (18). One port of the second four-way switching valve (3B) is connected to a discharge pipe (5c) of a second inverter compressor (2C) by an auxiliary gas pipe (19). One port of the second four-way switching valve (3B) is configured as a closed port that is closed. That is, the second four-way switching valve (3B) may be a three-way switching valve.

The first four-way switching valve (3A) is connected to a high-pressure gas pipe (8) and an outdoor gas pipe (9) and a connection pipe (18) and a communication gas pipe (17). One state (see the solid line in FIG. 1) and a second state (FIG. 1) in which the high-pressure gas pipe (8) communicates with the communication gas pipe (17) and the connection pipe (18) communicates with the outdoor gas pipe (9). (See one broken line).

In the second four-way switching valve (3B), the auxiliary gas pipe (19) communicates with the closing port and the connecting pipe (1
8) and the suction pipe (6c) of the second inverter compressor (2C) in the first state (see the solid line in FIG. 1), and the auxiliary gas pipe (1
It is configured to switch to a second state (see the broken line in FIG. 1) in which the connection pipe (18) and the connection pipe (18) communicate with each other and the connection pipe (18) and the closing port communicate with each other.

The discharge pipes (5a, 5b, 5c), the high-pressure gas pipe (8), and the outdoor gas pipe (9) constitute a high-pressure gas line (1L) during a cooling operation. On the other hand, the low pressure gas pipe (15) and the suction pipes (6a, 6a,
6b) constitutes the first low-pressure gas line (1M). In addition, the connecting gas pipe (17) and the second system compression mechanism (2E)
Constitutes the second low-pressure gas line (1N) during the cooling operation.

The first communication liquid pipe (11), the second communication liquid pipe (12), the communication gas pipe (17) and the low-pressure gas pipe (15) extend from the outdoor unit (1A) to the outside, and A closing valve (20) is provided in each of the units (1A). Further, a check valve (7) is provided in the outdoor unit (1A) at the branch end of the second communication liquid pipe (12), and the receiver (1) is provided.
It is configured such that the refrigerant flows from 4) toward the closing valve (20).

A communication pipe (21) as an auxiliary line is connected between the low-pressure gas pipe (15) and the suction pipe (6c) of the second inverter compressor (2C). The communication pipe (21)
The suction sides of the non-inverter compressor (2A), the first inverter compressor (2B), and the second inverter compressor (2C) can communicate with each other. The communication pipe (21) is connected to the main pipe (2
2) and a first sub pipe (23) and a second sub pipe (24) branched from the main pipe (22). And the main pipe (2
2) is connected to the suction pipe (6c) of the second inverter compressor (2C). The first sub pipe (23) and the second sub pipe (2
4) is connected to the low pressure gas pipe (15).

The first sub pipe (23) and the second sub pipe (24)
Is provided with a solenoid valve (7a, 7b) and a check valve (7) as opening / closing mechanisms, respectively. That is, the first sub-tube (2
3) is a non-inverter compressor (2A) of the first system compression mechanism (2D) or a second inverter compressor (2C) from the first inverter compressor (2B) to the second system compression mechanism (2E).
It is configured such that the refrigerant flows toward. The second sub pipe (24) is a second system compression mechanism (2E),
Inverter compressor (2C) to first system compression mechanism (2D)
The refrigerant flows toward the non-inverter compressor (2A) or the first inverter compressor (2B).

An auxiliary liquid pipe (25) for bypassing the receiver (14) is connected to the liquid pipe (10). The auxiliary liquid pipe (25) is provided with an outdoor expansion valve (26) as an expansion mechanism, through which a refrigerant mainly flows during heating. The above liquid tube (1
A check valve (7) that allows only the refrigerant flow toward the receiver (14) is provided between the outdoor heat exchanger (4) and the receiver (14) in (0). The check valve (7) is connected to the connection of the auxiliary liquid pipe (25) in the liquid pipe (10) and the receiver (1).
4) Located between and.

A liquid injection pipe (27) is connected between the auxiliary liquid pipe (25) and the low-pressure gas pipe (15). The liquid injection pipe (27) is provided with an electromagnetic valve (7c). In addition, the receiver (1
4) The upper part and the discharge pipe of the non-inverter compressor (2A) (5
A degassing pipe (28) is connected between a) and a).
The gas vent pipe (28) is connected to the discharge pipe (5) from the receiver (14).
A check valve (7) is provided which allows only the refrigerant flow towards a).

The high-pressure gas pipe (8) is provided with an oil separator (30). The oil separator (3
0) is connected to one end of an oil return pipe (31). The oil return pipe (31) is provided with a solenoid valve (7d), and the other end is connected to the suction pipe (6a) of the non-inverter compressor (2A). Dome of the above non-inverter compressor (2A) and second
A first oil equalizing pipe (32) is connected between the suction pipe (6c) of the inverter compressor (2C). The first oil level pipe (32)
Is provided with a check valve (7) that allows oil flow from the non-inverter compressor (2A) to the second inverter compressor (2C) and a solenoid valve (7e).

One end of a second oil equalizing pipe (33) is connected to the dome of the first inverter compressor (2B). The other end of the second oil equalizing pipe (33) is connected between the check valve (7) and the solenoid valve (7e) of the first oil equalizing pipe (32). Also,
A third oil equalizing pipe (34) is connected between the dome of the second inverter compressor (2C) and the low-pressure gas pipe (15). The third oil equalizing pipe (34) is provided with a solenoid valve (7f).

A floor heating circuit (35) is connected to the liquid pipe (10). The floor heating circuit (35) includes a floor heating heat exchanger (36), a first pipe (37), and a second pipe (38). One end of the first pipe (37) is connected between the check valve (7) and the closing valve (20) in the first communication liquid pipe (11), and the other end is a floor heating heat exchanger (36). It is connected to the. One end of the second pipe (38) is connected between the check valve (7) and the receiver (14) in the liquid pipe (10), and the other end is connected to the floor heating heat exchanger (36). I have. The floor heating heat exchanger (36) is arranged at a cash register (a cash payment place) where a clerk works for a long time in a convenience store.

The first pipe (37) and the second pipe (38)
, A closing valve (20) is provided, and the first pipe (37) is provided with a check valve (7) that allows only the refrigerant flow toward the floor heating heat exchanger (36). . When the floor heating heat exchanger (36) is not provided, the first pipe (37) and the second pipe (38) are directly connected.

<Indoor unit> The above indoor unit (1B)
Has an indoor heat exchanger (41) as a use side heat exchanger and an indoor expansion valve (42) as an expansion mechanism. The gas side of the indoor heat exchanger (41) is connected to a communication gas pipe (17). On the other hand, the liquid side of the indoor heat exchanger (41) is connected to a second communication liquid pipe (12) via an indoor expansion valve (42). The indoor heat exchanger (41) is, for example, a cross-fin type fin-and-tube heat exchanger, and an indoor fan (43), which is a use-side fan, is disposed close to the indoor heat exchanger (41).

<Refrigeration unit> The above refrigeration unit (1C)
Has a refrigeration heat exchanger (45) as a cooling heat exchanger and a refrigeration expansion valve (46) as an expansion mechanism. The liquid side of the refrigeration heat exchanger (45) is connected to the solenoid valve (7) and the refrigeration expansion valve (4
The first communication liquid pipe (11) is connected via 6). On the other hand, a low-pressure gas pipe (15) is connected to the gas side of the refrigeration heat exchanger (45).

The refrigeration heat exchanger (45) communicates with the suction side of the first system compression mechanism (2D), while the indoor heat exchanger (41) operates during the cooling operation by the second inverter compressor (2C). )
To the suction side. Therefore, the refrigerant pressure (evaporation pressure) of the refrigeration heat exchanger (45) is changed to the indoor heat exchanger (41).
Refrigerant pressure (evaporation pressure). As a result, the refrigerant evaporation temperature of the refrigeration heat exchanger (45) is, for example, −10.
° C, and the refrigerant evaporation temperature of the indoor heat exchanger (41) is, for example, + 5 ° C, and the refrigerant circuit (1E) forms a circuit of different temperature evaporation.

The refrigeration expansion valve (46) is a temperature-sensitive expansion valve, and a temperature-sensitive cylinder is attached to the gas side of the refrigeration heat exchanger (45). The refrigerating heat exchanger (45) is, for example, a cross-fin type fin-and-tube heat exchanger, and a refrigerating fan (47), which is a cooling fan, is disposed in close proximity.

<Refrigeration unit> The above refrigeration unit (1D)
Has a refrigeration heat exchanger (51) as a cooling heat exchanger, a refrigeration expansion valve (52) as an expansion mechanism, and a booster compressor (53) as a refrigeration compressor. The liquid side of the refrigeration heat exchanger (51) is connected to a branch liquid pipe (1) branched from the first communication liquid pipe (11).
3) is connected via the solenoid valve (7h) and the refrigeration expansion valve (52).

The gas side of the refrigerating heat exchanger (51) and the suction side of the booster compressor (53) are connected by a connecting gas pipe (54). A branch gas pipe (16) branched from the low-pressure gas pipe (15) is connected to the discharge side of the booster compressor (53). The branch gas pipe (16) is provided with a check valve (7) and an oil separator (55).
An oil return pipe (57) having a capillary tube (56) between the oil separator (55) and the connecting gas pipe (54)
Is connected.

The booster compressor (53) is connected to the first compression mechanism (2D) so that the refrigerant evaporation temperature of the refrigerating heat exchanger (51) is lower than the refrigerant evaporation temperature of the refrigeration heat exchanger (45). The refrigerant is compressed in two stages between the two stages. The above refrigeration heat exchanger (5
The refrigerant evaporation temperature of 1) is set to, for example, -40C.

The refrigerating expansion valve (52) is a temperature-sensitive expansion valve, and a temperature-sensitive cylinder is mounted on the gas side of the refrigerating heat exchanger (45). The refrigerating heat exchanger (51) is, for example, a cross-fin type fin-and-tube heat exchanger, and a refrigerating fan (58) serving as a cooling fan is arranged close to the refrigerating heat exchanger (51).

The connection gas pipe (54) on the suction side of the booster compressor (53) and the check valve (7) of the branch gas pipe (16) on the discharge side of the booster compressor (53). A bypass pipe (59) having a check valve (7) is connected to the side. The bypass pipe (59) is configured so that the refrigerant flows by bypassing the booster compressor (53) when the booster compressor (53) is stopped due to a failure or the like.

<Control System> The refrigerant circuit (1E) is provided with various sensors and various switches. The high-pressure gas pipe (8) of the outdoor unit (1A) has a high-pressure pressure sensor (61) as pressure detection means for detecting high-pressure refrigerant pressure.
And a discharge temperature sensor (62) as temperature detecting means for detecting the high-pressure refrigerant temperature. The discharge pipe (5c) of the second inverter compressor (2C) is provided with a discharge temperature sensor (63) as temperature detecting means for detecting a high-pressure refrigerant temperature. In addition, the above non-inverter compressor (2A),
Each of the discharge pipes (5a, 5b, 5c) of the first inverter compressor (2B) and the second inverter compressor (2C) is provided with a pressure switch (64) that opens when the high-pressure refrigerant pressure reaches a predetermined value. .

The first inverter compressor (2B) and the second inverter compressor (2B)
Each suction pipe (6b, 6c) of the inverter compressor (2C) has a low-pressure pressure sensor (65, 66) which is a pressure detecting means for detecting a low-pressure refrigerant pressure and a temperature detecting means for detecting a low-pressure refrigerant temperature. An intake temperature sensor (67, 68) is provided.

The outdoor heat exchanger (4) has an outdoor heat exchange sensor (69) as temperature detecting means for detecting an evaporation temperature or a condensation temperature as a refrigerant temperature in the outdoor heat exchanger (4).
Is provided. Further, the outdoor unit (1A) is provided with an outside air temperature sensor (70) which is a temperature detecting means for detecting an outdoor air temperature.

The indoor heat exchanger (41) has an indoor heat exchange sensor (71) which is a temperature detecting means for detecting a condensing temperature or an evaporating temperature which is a refrigerant temperature in the indoor heat exchanger (41).
And a gas temperature sensor (72) as temperature detecting means for detecting the gas refrigerant temperature on the gas side. Further, the indoor unit (1B) is provided with a room temperature sensor (73) as temperature detecting means for detecting the indoor air temperature.

The refrigeration unit (1C) is provided with a refrigeration temperature sensor (74) as temperature detecting means for detecting the temperature in the refrigerator in the refrigerated showcase. The refrigeration unit (1D) is provided with a refrigeration temperature sensor (75) as temperature detection means for detecting the temperature in the refrigerator inside the freezer showcase.

A liquid temperature sensor (76) which is a temperature detecting means for detecting a refrigerant temperature after flowing through the floor heating heat exchanger (36) is provided in the second pipe (38) of the floor heating circuit (35). Is provided.

The output signals of the various sensors and various switches are input to the controller (80). The controller (80) includes a first inverter compressor (2B) and a second inverter compressor (2B).
It is configured to control the capacity and the like of the inverter compressor (2C).

The controller (80) controls the operation of the refrigerant circuit (1E), and performs a cooling operation, a freezing operation, a first cooling / freezing operation, a second cooling / freezing operation, a heating operation, and a first heating / freezing operation. The system is configured to control by switching between the heating excess operation and the third heating / refrigeration operation.

-Operation- Next, the operation performed by the refrigeration system (1) will be described for each operation.

<Cooling Mode> As shown in FIG. 11, the cooling mode is switched to one of a cooling operation, a freezing operation, a first cooling / freezing operation, and a second cooling / freezing operation.

In the operation in the cooling mode, the following 3
Two decisions are made. That is, in step ST1, the air conditioning thermostat is ON and the low pressure sensor (65,
It is determined whether the condition 1 that the low-pressure refrigerant pressure detected by 66) is higher than 98 kPa is satisfied. Step ST
In 2, it is determined whether or not the condition 2 that the low-pressure refrigerant pressure is lower than 98 kPa is satisfied while the air conditioning thermostat is ON. In step ST3, the air conditioning thermo OF
It is determined whether the condition 3 is satisfied and the condition 3 that the low-pressure refrigerant pressure is higher than 98 kPa is satisfied. Note that the air conditioning thermo ON means a state in which the refrigerant evaporates in the indoor heat exchanger (41) to perform a cooling operation, and the air conditioning thermo OFF means that the indoor expansion valve (42) is closed and the refrigerant is turned off. A state in which the indoor fan (43) does not flow through the indoor heat exchanger (41) and the cooling operation is stopped by driving the indoor fan (43).

When the operation in the cooling mode is started, first, the determination in the step ST1 is performed. If the condition 1 of step ST1 is satisfied, the process proceeds to step ST4, where the first cooling / freezing operation or the second cooling / freezing operation for performing cooling, refrigeration, and freezing is performed, and the process returns. If the condition 1 of step ST1 is not satisfied and the condition 2 of step ST2 is satisfied, the process proceeds to step ST5, performs the cooling operation, and returns. Condition 2 of step ST2
Is not satisfied, and the condition 3 of step ST3 is satisfied, the process proceeds to step ST6, performs the freezing operation, and returns. If condition 3 of step ST3 is not satisfied,
Continue operation and return.

The respective operations of the cooling operation, the freezing operation, the first cooling / freezing operation, and the second cooling / freezing operation will be described.

<Cooling operation> This cooling operation is an operation for cooling only the indoor unit (1B). During this cooling operation, as shown in FIG. 2, the non-inverter compressor (2A) forms a first system compression mechanism (2D), and the first inverter compressor (2B) and the second inverter compressor (2C). ) Constitute the second system compression mechanism (2E). Then, only the first inverter compressor (2B) and the second inverter compressor (2C) as the second system compression mechanism (2E) are driven.

The first four-way switching valve (3A) and the second four-way switching valve (3B) switch to the first state, respectively, as shown by the solid lines in FIG. Further, the solenoid valve (7b) of the second sub pipe (24) of the communication pipe (21) is opened, while the communication pipe (21) is opened.
Solenoid valve (7a) of the first auxiliary pipe (23), outdoor expansion valve (26),
The solenoid valve (7g) of the refrigeration unit (1C) and the solenoid valve (7h) of the refrigeration unit (1D) are closed.

In this state, the refrigerant discharged from the first inverter compressor (2B) and the second inverter compressor (2C) passes through the outdoor gas pipe (9) from the first four-way switching valve (3A) through the outdoor heat pipe (9). It flows into the exchanger (4) and condenses. The condensed liquid refrigerant flows through the liquid pipe (10), flows through the second connecting liquid pipe (12) through the receiver (14), flows into the indoor heat exchanger (41) through the indoor expansion valve (42), and evaporates. I do. The evaporated gas refrigerant flows from the connecting gas pipe (17) through the first four-way switching valve (3A) and the second four-way switching valve (3B) to the suction pipe (6c) of the second inverter compressor (2C). , The first inverter compressor (2B) and the second
Return to the inverter compressor (2C). Repeat this cycle,
Cool the interior of the store. A part of the low-pressure gas refrigerant is diverted from the suction pipe (6c) of the second inverter compressor (2C) to the communication pipe (21), and is diverted from the second auxiliary pipe (24) to the first inverter compressor (2C). Return to 2B).

The capacity of the compressor during the cooling operation is controlled as shown in FIG. 12, and the following two determinations are made in this control. That is, in step ST11,
The room temperature Tr detected by the room temperature sensor (73) is the set temperature Tset
It is determined whether or not the condition 1 that the temperature is higher than the temperature obtained by adding 3 ° C. to the temperature is satisfied. In step ST12, it is determined whether or not a condition 2 that the room temperature Tr is lower than the set temperature Tset is satisfied.

If the condition 1 of step ST11 is satisfied, the process proceeds to step ST13, where the capacity of the first inverter compressor (2B) or the second inverter compressor (2C) is increased, and the process returns. If the condition 1 in step ST11 is not satisfied and the condition 2 in step ST12 is satisfied, the process proceeds to step ST14, in which the capacity of the first inverter compressor (2B) or the second inverter compressor (2C) is increased. To return. If the condition 2 in step ST12 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated.

As shown in FIG. 13, the control for increasing the compressor capacity is performed by first increasing the first inverter compressor (2B) from the stopped state to the minimum capacity (see point A).
2nd while keeping the inverter compressor (2B) at the minimum capacity
Drive the inverter compressor (2C) from the stopped state to increase the capacity. Thereafter, when the load further increases, the capacity of the first inverter compressor (2B) is increased while maintaining the second inverter compressor (2C) at the maximum capacity (see point B). The control for decreasing the compressor capacity is the reverse of the increase control described above.

The degree of opening of the indoor expansion valve (42) is controlled based on the detected temperatures of the indoor heat exchange sensor (71) and the gas temperature sensor (72), and is the same in the cooling mode hereinafter. .

<Refrigeration operation> This refrigeration operation is an operation in which only the refrigeration unit (1C) and the refrigeration unit (1D) are cooled. During this refrigeration operation, as shown in FIG. 3, the non-inverter compressor (2A) and the first inverter compressor (2B) constitute a first-system compression mechanism (2D), and the second inverter compressor (2D) 2C) constitutes the second system compression mechanism (2E). Then, only the non-inverter compressor (2A) and the first inverter compressor (2B), which are the first system compression mechanism (2D), are driven, and the booster compressor (53) is also driven.

Further, the first four-way switching valve (3A) switches to the first state as shown by the solid line in FIG. Furthermore, the solenoid valve (7g) of the refrigeration unit (1C) and the refrigeration unit (1D)
, While the two electromagnetic valves (7a, 7b), the outdoor expansion valve (26), and the indoor expansion valve (42) of the communication pipe (21) are closed.

In this state, the refrigerant discharged from the non-inverter compressor (2A) and the first inverter compressor (2B) exchanges outdoor heat with the first four-way switching valve (3A) via the outdoor gas pipe (9). It flows into the vessel (4) and condenses. The condensed liquid refrigerant flows through the liquid pipe (10), flows through the receiver (14), flows through the first connecting liquid pipe (11), and partially passes through the refrigeration expansion valve (46) to the refrigeration heat exchanger (45). Flow and evaporate.

On the other hand, the other liquid refrigerant flowing through the first communication liquid pipe (11) flows through the branch liquid pipe (13), flows through the refrigeration expansion valve (52) to the refrigeration heat exchanger (51), and evaporates. . The gas refrigerant evaporated in the refrigeration heat exchanger (51) is supplied to the booster compressor (5
It is sucked into 3), compressed, and discharged to the branch gas pipe (16).

The gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booster compressor (53) are:
Merge with the low-pressure gas pipe (15) and use the non-inverter compressor (2
Return to A) and the first inverter compressor (2B). This circulation is repeated to cool the inside of the refrigerator, which is a refrigeration showcase and a freezing showcase.

Therefore, the refrigerant pressure in the refrigerating heat exchanger (51) is sucked by the booster compressor (53), and is lower than the refrigerant pressure in the refrigerating heat exchanger (45). As a result, for example, the refrigerant temperature (evaporation temperature) in the refrigerating heat exchanger (51) becomes −40 ° C., and the refrigerant temperature (evaporation temperature) in the refrigerating heat exchanger (45) becomes −10 ° C.
Becomes

The capacity of the compressor during the refrigeration operation is controlled as shown in FIG. 14. In this control, the following two determinations are made. That is, in step ST21,
It is determined whether or not the condition 1 that the low-pressure refrigerant pressure LP detected by the low-pressure pressure sensors (65, 66) is higher than 392 kPa is satisfied. In step ST22, the low-pressure refrigerant pressure
It is determined whether the condition 2 that the LP is lower than 245 kPa is satisfied.

If the condition 1 in step ST21 is satisfied, the process proceeds to step ST23, in which the capacity of the first inverter compressor (2B) or the non-inverter compressor (2A) is increased, and the process returns. If the condition 1 in step ST21 is not satisfied and the condition 2 in step ST22 is satisfied, the process proceeds to step ST24, in which the capacity of the first inverter compressor (2B) or the non-inverter compressor (2A) is increased and the process is returned. I do. If the condition 2 in step ST22 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated.

In the control for increasing the compressor capacity, as shown in FIG. 15, first, the first inverter compressor (2B) is driven with the non-inverter compressor (2A) stopped (see point A). Increase capacity. After the first inverter compressor (2B) rises to the maximum capacity (see point B), if the load further increases, the non-inverter compressor (2A) is driven and at the same time, the first inverter compressor (2B) is lowered. Reduce to capacity (see point C). Thereafter, when the load further increases, the capacity of the first inverter compressor (2B) is increased.
The control for decreasing the compressor capacity is the reverse of the increase control described above.

The degree of opening of the refrigerating expansion valve (46) and the refrigerating expansion valve (52) is controlled by a superheat degree control by a temperature-sensitive cylinder.
Hereinafter, the same applies to each operation.

<First Cooling and Refrigerating Operation> The first cooling and refrigerating operation is performed by the cooling of the indoor unit (1B) and the refrigerating unit (1C).
And the cooling of the refrigeration unit (1D). During the first cooling and refrigeration operation, as shown in FIG. 4, the non-inverter compressor (2A) and the first inverter compressor (2A)
B) constitutes the first system compression mechanism (2D), and the second inverter compressor (2C) constitutes the second system compression mechanism (2E). Then, the non-inverter compressor (2A),
Inverter compressor (2B) and second inverter compressor (2
While driving C), the booster compressor (53) is also driven.

The first four-way switching valve (3A) and the second four-way switching valve (3B) switch to the first state as shown by the solid lines in FIG. Further, the solenoid valve (7g) of the refrigeration unit (1C) and the solenoid valve (7h) of the refrigeration unit (1D) are opened, while the two solenoid valves (7a, 7b) of the communication pipe (21) are opened.
And the outdoor expansion valve (26) is closed.

In this state, the refrigerant discharged from the non-inverter compressor (2A), the first inverter compressor (2B), and the second inverter compressor (2C) merge in the high-pressure gas pipe (8), and It flows from the four-way switching valve (3A) to the outdoor heat exchanger (4) via the outdoor gas pipe (9) and condenses. The condensed liquid refrigerant flows through the liquid pipe (10) and passes through the receiver (14) to the first refrigerant.
The liquid flows separately into the communication liquid pipe (11) and the second communication liquid pipe (12).

The liquid refrigerant flowing through the second communication liquid pipe (12) flows through the indoor expansion valve (42) to the indoor heat exchanger (41) and evaporates. The evaporated gas refrigerant flows from the connecting gas pipe (17) through the first four-way switching valve (3A) and the second four-way switching valve (3B) to the suction pipe (6c), and to the second inverter compressor (2C). Return to

On the other hand, a part of the liquid refrigerant flowing through the first communication liquid pipe (11) passes through the refrigeration expansion valve (46) and reaches the refrigeration heat exchanger (4).
Flow to 5) and evaporate. In addition, the first communication liquid pipe (11)
The other liquid refrigerant flowing through the refrigerant flows through the branch liquid pipe (13), passes through the refrigeration expansion valve (52), flows into the refrigeration heat exchanger (51), and evaporates. The gas refrigerant evaporated in the refrigerating heat exchanger (51) is sucked and compressed by the booster compressor (53), and is discharged to the branch gas pipe (16).

The gas refrigerant evaporated in the refrigerating heat exchanger (45) and the gas refrigerant discharged from the booster compressor (53) are:
Merge with the low-pressure gas pipe (15) and use the non-inverter compressor (2
Return to A) and the first inverter compressor (2B).

This circulation is repeated to cool the inside of the store, which is a room, and at the same time, cool the inside of the refrigerator, which is a showcase for refrigeration and a case for freezing.

The behavior of the refrigerant during the first cooling and freezing operation will be described with reference to FIG.

The refrigerant is compressed to the point A by the second inverter compressor (2C). The refrigerant is compressed to point B by the non-inverter compressor (2A) and the first inverter compressor (2B). The refrigerant at point A and the refrigerant at point B merge and condense to become the refrigerant at point C. Part of the refrigerant at point C is decompressed to point D by the indoor expansion valve (42).
It evaporates at 5 ° C. and is sucked into the second inverter compressor (2C) at point E.

A part of the refrigerant at the point C is decompressed to the point F by the refrigerating expansion valve (46), evaporates at, for example, -10 ° C., and the non-inverter compressor (2A) and the first It is sucked by the inverter compressor (2B).

A part of the refrigerant at the point C is sucked by the booster compressor (53).
The pressure is reduced to a point, evaporates at, for example, −40 ° C., and is sucked into the booster compressor (53) at point I. The refrigerant compressed to the point J by the booster compressor (53) is drawn into the non-inverter compressor (2A) and the first inverter compressor (2B) at the point G.

As described above, the refrigerant in the refrigerant circuit (1E) is evaporated at different temperatures by the first system compression mechanism (2D) and the second system compression mechanism (2E), and is further evaporated by the booster compressor (53). The two-stage compression results in three types of evaporation temperatures.

<Second cooling / refrigeration operation> This second cooling / refrigeration operation is an operation when the cooling capacity of the indoor unit (1B) during the first cooling / refrigeration operation is insufficient. As shown in FIG. 5, the second cooling / freezing operation is basically the same as that of the first cooling / freezing operation, but the solenoid valve (7b) of the second auxiliary pipe (24) in the communication pipe (21) is used. Is different from the first cooling and refrigeration operation in that the is opened.

Therefore, during the second cooling and refrigeration operation, the non-inverter compressor (2A), the first and second inverter compressors (2B) and (2C) are operated similarly to the first cooling and refrigeration operation. The discharged refrigerant is condensed in the outdoor heat exchanger (4), and is cooled by the indoor heat exchanger (41) and the refrigerated heat exchanger (4).
Evaporate in 5) and the refrigeration heat exchanger (51).

Then, the refrigerant evaporated in the indoor heat exchanger (41) returns to the second inverter compressor (2C), and the refrigerant evaporated in the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51) is The operation returns to the non-inverter compressor (2A) and the first inverter compressor (2B). However, since the second auxiliary pipe (24) in the communication pipe (21) is in communication, the indoor heat exchanger ( 41) The refrigerant pressure drops to the suction pressure of the non-inverter compressor (2A) and the first inverter compressor (2B). As a result, the evaporation temperature of the indoor heat exchanger (41) decreases,
The lack of cooling capacity is compensated.

The control for switching between the second cooling refrigerating operation and the first cooling refrigerating operation will now be described with reference to FIG.

First, in step ST31, it is determined whether the solenoid valve (7) of the second sub pipe (24) is closed, and the solenoid valve (7) of the second sub pipe (24) is closed. Then, the process proceeds to step ST32, and the above-described first cooling and refrigeration operation is executed. Thereafter, steps ST33 to ST36
Are determined.

That is, in step ST33, it is determined whether or not the condition 1 that the room temperature Tr is higher than the temperature obtained by adding 3 ° C. to the set temperature Tset is satisfied. In step ST34, it is determined whether or not the condition 2 that the first inverter compressor (2B) is operating at the maximum capacity (maximum frequency) is satisfied. In step ST35, it is determined whether or not the condition 3 that the capabilities of the non-inverter compressor (2A) and the first inverter compressor (2B) are not maximum is satisfied. In step ST36, it is determined whether or not a condition 4 that the low-pressure refrigerant pressure is lower than 392 kPa is satisfied.

Then, the above steps ST33 to ST36
If any of the four conditions 1 to 4 is not satisfied, the process returns as it is, and the first cooling / refrigerating operation is continued.

On the other hand, if all of the four conditions 1 to 4 in steps ST33 to ST36 are satisfied, the process proceeds to step ST37, in which the solenoid valve (7b) of the second sub pipe (24) is opened, and the second cooling is performed. Switch to refrigeration operation. In other words, in this case, since the cooling capacity is insufficient, the indoor heat exchanger (41)
To lower the evaporation temperature.

Also, the solenoid valve (7b) of the second sub pipe (24)
Is the time of the second cooling and freezing operation in which
Two determinations, T41 and ST42, are performed.
That is, in step ST41, it is determined whether or not the condition 5 that the room temperature Tr is higher than the temperature obtained by adding 3 ° C. to the set temperature Tset is satisfied. In step ST42, condition 6 that the room temperature Tr is lower than the set temperature Tset
Is determined.

If the condition 5 of step ST41 is satisfied, the process moves to step ST43, where the compression mechanism (2D) of the first system of the non-inverter compressor (2A) and the first inverter compressor (2B) is used. Improve ability. If the condition of step ST41 is satisfied 6, the process proceeds to step ST44 to lower the capacity of the first-system compression mechanism (2D) of the non-inverter compressor (2A) and the first inverter compressor (2B). .

When the capacity of the first system compression mechanism (2D) is increased, when the capacity of the first system compression mechanism (2D) is reduced, or when the condition 5 in step ST41 and the condition in step ST42 are satisfied.
If none of the conditions 6 is satisfied, none of the conditions in step ST
Moving to 45, it is determined whether the low-pressure refrigerant pressure is lower than 245 kPa.

When the low-pressure refrigerant pressure is higher than 245 kPa, the cooling performance is insufficient, so the flow returns as it is, and the second cooling refrigerating operation is continued. On the other hand, if the low-pressure refrigerant pressure is lower than 245 kPa, the shortage of the cooling capacity has been resolved, and the routine proceeds to step ST46, where the solenoid valve (7b) of the second sub pipe (24) is closed to perform the first cooling refrigeration. Switch to operation and return.

<Heating Mode> As shown in FIG. 18, the heating mode is switched to any one of the heating operation, the freezing operation, the first heating / freezing operation, the second heating / freezing operation, and the third heating / freezing operation.

In this heating mode operation, the following 3
Two decisions are made. That is, in step ST51, the air conditioning thermostat is ON and the low-pressure pressure sensor (65,
It is determined whether the condition 1 that the low-pressure refrigerant pressure detected by 66) is higher than 98 kPa is satisfied. Step ST
In 52, it is determined whether or not the condition 2 that the low-pressure refrigerant pressure is lower than 98 kPa is satisfied while the air conditioning thermostat is ON. In step ST53, it is determined whether or not the condition 3 that the air conditioning thermostat is OFF and the low-pressure refrigerant pressure is higher than 98 kPa is satisfied. The air conditioning thermo ON means a state in which the refrigerant is condensed in the indoor heat exchanger (41) to perform a heating operation.
F indicates a state where the indoor expansion valve (42) is closed and the refrigerant does not flow through the indoor heat exchanger (41), and the indoor fan (43) is driven to suspend the heating operation. .

When the operation in the heating mode is started, first, the determination in step ST51 is performed. And
When the condition 1 of step ST51 is satisfied, the process proceeds to step ST54, in which the first heating / refrigeration operation or the second heating / refrigeration operation in the heating mode 1 is performed, and the process returns. If the condition 1 in step ST51 is not satisfied, the process proceeds to step ST52.
If the condition 2 is satisfied, the process proceeds to step ST55, where the heating operation or the third heating / freezing operation is performed, and the process returns. If the condition 2 of step ST52 is not satisfied and the condition 3 of step ST53 is satisfied,
The process moves to step 56, where a freezing operation is performed and the process returns. If the condition 3 of step ST53 is not satisfied, the operation is continued as it is and the routine returns.

The respective operations of the heating operation, the first heating / refrigeration operation, the second heating / refrigeration operation, and the third heating / refrigeration operation will now be described. The refrigeration operation is the same as the refrigeration operation in the cooling mode.

<Heating operation> This heating operation is an operation for heating only the indoor unit (1B) and the floor heating circuit (35). During the heating operation, as shown in FIG. 6, the non-inverter compressor (2A) forms a first-system compression mechanism (2D), and the first inverter compressor (2B) and the second inverter compressor (2C). ) Constitute the second system compression mechanism (2E). Then, only the first inverter compressor (2B) and the second inverter compressor (2C) as the second system compression mechanism (2E) are driven.

The first four-way switching valve (3A) switches to the second state as shown by the solid line in FIG. 6, and the second four-way switching valve (3B) is shown by the solid line in FIG. Thus, the state is switched to the first state. Further, while the solenoid valve (7b) of the second sub pipe (24) of the communication pipe (21) is open, the solenoid valve (7a) of the first sub pipe (23) of the communication pipe (21) and the refrigeration unit (1C) ) Solenoid valve (7g) and refrigeration unit (1D) solenoid valve (7h) are closed.

In this state, the refrigerant discharged from the first inverter compressor (2B) and the second inverter compressor (2C) is supplied from the first four-way switching valve (3A) through the communication gas pipe (17) to the indoor heat exchanger. It flows to the exchanger (41) and condenses. The condensed liquid refrigerant flows through the second communication liquid pipe (12), flows through the floor heating circuit (35), and flows through the floor heating heat exchanger (36) to the receiver (14). Thereafter, the liquid refrigerant flows through the outdoor expansion valve (26) of the auxiliary liquid pipe (25) to the outdoor heat exchanger (4) and evaporates. The evaporated gas refrigerant flows from the connecting gas pipe (17) through the first four-way switching valve (3A) and the second four-way switching valve (3B) to the suction pipe (6c) of the second inverter compressor (2C). Return to the first inverter compressor (2B) and the second inverter compressor (2C). This circulation is repeated to heat the interior of the store, and at the same time, perform floor heating. A part of the low-pressure gas refrigerant is diverted from the suction pipe (6c) of the second inverter compressor (2C) to the communication pipe (21), and is diverted from the second auxiliary pipe (24) to the first inverter compressor (2C). Return to 2B).

The capacity of the compressor during the heating operation is controlled as shown in FIG. 19. In this control, the following two determinations are made. That is, in step ST61,
The room temperature Tr detected by the room temperature sensor (73) is the set temperature Tset
It is determined whether or not the condition 1 that the temperature is higher than the temperature obtained by adding 3 ° C. to the temperature is satisfied. In step ST62, it is determined whether or not the condition 2 that the room temperature Tr is lower than the set temperature Tset is satisfied.

If the condition 1 in step ST61 is satisfied, the process proceeds to step ST63, in which the capacity of the first inverter compressor (2B) or the second inverter compressor (2C) is increased, and the process returns. If the condition 1 of step ST61 is not satisfied and the condition 2 of step ST62 is satisfied, the process proceeds to step ST64 to increase the capacity of the first inverter compressor (2B) or the second inverter compressor (2C). To return. If the condition 2 of step ST62 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated. The compressor capacity increase / decrease control is performed as shown in FIG.

The degree of opening of the outdoor expansion valve (26) is controlled by the degree of superheat by the saturation temperature corresponding to the pressure based on the low pressure sensors (65, 66) and the temperature detected by the suction temperature sensors (67, 68). The degree of opening of the indoor expansion valve (42) is supercooled based on the temperatures detected by the indoor heat exchange sensor (71) and the liquid temperature sensor (76). In particular, since the refrigerant temperature after flowing out of the floor heating heat exchanger (36) is used, a predetermined floor heating capacity is maintained. The outdoor expansion valve (26) and the indoor expansion valve (4
The opening control of 2) is the same in the heating mode hereinafter.

<First Heating / Refrigeration Operation> This first heating / refrigeration operation uses the indoor unit (1) without using the outdoor heat exchanger (4).
B) Heating and refrigeration unit (1C) and refrigeration unit (1
This is a heat recovery operation for cooling in D). As shown in FIG. 7, the first heating and refrigeration operation is performed by the non-inverter compressor (2).
A) and the first inverter compressor (2B) constitute a first system compression mechanism (2D), and the second inverter compressor (2C) constitutes a second system compression mechanism (2E). Then, the non-inverter compressor (2A) and the first inverter compressor (2A)
While driving B), the booster compressor (53) is also driven. The second inverter compressor (2C) is stopped.

Further, the first four-way switching valve (3A) is switched to the second state as shown by the solid line in FIG. 7, and the second four-way switching valve (3B) is shown by the solid line in FIG. Thus, the state is switched to the first state. Furthermore, solenoid valve (7g) of refrigeration unit (1C)
And the solenoid valve (7h) of the refrigeration unit (1D) is open, while the two solenoid valves (7a, 7b) and the outdoor expansion valve (26) of the communication pipe (21) are closed.

In this state, the refrigerant discharged from the non-inverter compressor (2A) and the first inverter compressor (2B) exchanges indoor heat via the connecting gas pipe (17) from the first four-way switching valve (3A). It flows into the vessel (41) and condenses. The condensed liquid refrigerant flows through the floor heating circuit (35) from the second connecting liquid pipe (12),
It flows from the floor heating heat exchanger (36) to the first communication liquid pipe (11) via the receiver (14).

A part of the liquid refrigerant flowing through the first communication liquid pipe (11) flows through the refrigeration expansion valve (46) to the refrigeration heat exchanger (45) and evaporates. Further, another liquid refrigerant flowing through the first communication liquid pipe (11) flows through the branch liquid pipe (13), and the refrigeration expansion valve (5).
After passing through 2), it flows to the freezing heat exchanger (51) and evaporates. The gas refrigerant evaporated in the refrigerating heat exchanger (51) is sucked and compressed by the booster compressor (53), and is discharged to the branch gas pipe (16).

The gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booster compressor (53) are:
Merge with the low-pressure gas pipe (15) and use the non-inverter compressor (2
Return to A) and the first inverter compressor (2B). This circulation is repeated to heat the inside of the store, which is a room, and perform floor heating, and at the same time, cool the inside of the refrigerator, which is a showcase for refrigeration and a showcase for freezing. In other words, the cooling capacity (the amount of heat of evaporation) between the refrigeration unit (1C) and the refrigeration unit (1D) and the heating capacity (the amount of heat of condensation) of the indoor unit (1B) and the floor heating circuit (35) are balanced, and 100% Heat recovery is performed.

The compressor capacity and the like during the first heating / freezing operation are controlled as shown in FIG. 20, and the following four determinations are made in this control.

That is, in step ST71, the room temperature Tr detected by the room temperature sensor (73) is lower than the temperature obtained by subtracting 3 ° C. from the set temperature Tset, and the low-pressure pressure sensor (65,
It is determined whether the condition 1 that the low-pressure refrigerant pressure LP detected by 66) is higher than 392 kPa is satisfied. In step ST72, the room temperature Tr is increased by 3 ° C. from the set temperature Tset.
And the low pressure refrigerant pressure LP is lower than 245 kP
It is determined whether the condition 2 that is lower than a is satisfied. In step ST73, the room temperature Tr is set to the set temperature.
It is determined whether a condition 3 that the pressure is higher than Tset and the low-pressure refrigerant pressure LP is higher than 392 kPa is satisfied. In step ST74, it is determined whether or not the condition 4 that the room temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.

If the condition 1 in step ST71 is satisfied, the process proceeds to step ST75, in which the capacity of the first inverter compressor (2B) or the non-inverter compressor (2A) is increased, and the process returns. If the condition 1 in step ST71 is not satisfied and the condition 2 in step ST72 is satisfied, the process proceeds to step ST76, and switches to a third heating / refrigeration operation described later, that is, an operation with insufficient heating capacity, and returns. If the condition 2 in step ST72 is not satisfied and the condition 3 in step ST73 is satisfied, the process proceeds to step ST77, and the process returns to the second heating / refrigerating operation described later, that is, the operation in which the heating capacity is excessive, and returns.
If condition 3 of step ST73 is not satisfied, step S
If the condition 4 of T74 is satisfied, the process proceeds to step ST78.
Then, increase the capacity of the first inverter compressor (2B) or the non-inverter compressor (2A) and return. If the condition 4 in step ST74 is not satisfied, the condition is satisfied with the current compression function, so the process returns and repeats the above operation. The compressor capacity increase / decrease control is shown in FIG.
This is performed as shown in FIG.

<Second Heating / Refrigeration Operation> This second heating / refrigeration operation is an overheating operation in which the heating capacity of the indoor unit (1B) is excessive during the first heating / refrigeration operation. During the second heating and refrigeration operation, as shown in FIG. 8, the non-inverter compressor (2A) and the first inverter compressor (2B) constitute a first-system compression mechanism (2D), and the second inverter Compressor (2
C) constitutes the second system compression mechanism (2E). And
The non-inverter compressor (2A) and the first inverter compressor (2B) are driven, and the booster compressor (53) is also driven. The second inverter compressor (2C) is stopped.

The second heating / refrigeration operation is an operation when the heating capacity is excessive during the first heating / refrigeration operation.
The second four-way switching valve (3B) is the same as the above-described first heating and refrigeration operation except that the second four-way switching valve (3B) is switched to the second state, as shown by the solid line in FIG.

Therefore, the non-inverter compressor (2A)
And a part of the refrigerant discharged from the first inverter compressor (2B) is supplied to the indoor heat exchanger (41) in the same manner as in the first heating and refrigeration operation.
To condense. The condensed liquid refrigerant is supplied to the floor heating circuit (3
5), and from the floor heating heat exchanger (36) to the liquid pipe (10).

On the other hand, the other refrigerants discharged from the non-inverter compressor (2A) and the first inverter compressor (2B)
The gas flows from the auxiliary gas pipe (19) through the outdoor gas pipe (9) via the second four-way switching valve (3B) and the first four-way switching valve (3A), and is condensed in the outdoor heat exchanger (4). The condensed liquid refrigerant flows through the liquid pipe (10), merges with the liquid refrigerant from the floor heating circuit (35), flows into the receiver (14), and flows through the first connecting liquid pipe (11).

Thereafter, a part of the liquid refrigerant flowing through the first communication liquid pipe (11) flows into the refrigeration heat exchanger (45) and evaporates.
Further, the other liquid refrigerant flowing through the first communication liquid pipe (11) is:
It flows into the freezing heat exchanger (51) and evaporates. The gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booster compressor (53) merge in the low-pressure gas pipe (15),
Return to the non-inverter compressor (2A) and the first inverter compressor (2B). This circulation is repeated to heat the inside of the store, which is a room, and perform floor heating, and at the same time, cool the inside of the refrigerator, which is a showcase for refrigeration and a showcase for freezing. In other words, the cooling capacity (the amount of heat of evaporation) between the refrigeration unit (1C) and the refrigeration unit (1D) and the heating capacity (the amount of heat of condensation) between the indoor unit (1B) and the floor heating circuit (35) do not balance, and the remaining condensation does not occur. The heat is released outside the room by the outdoor heat exchanger (4).

The capacity of the compressor and the air flow rate of the outdoor fan (4F) during the second heating / refrigeration operation are controlled as shown in FIG. 21, and the following four judgments are made.

That is, in step ST81, the room temperature Tr detected by the room temperature sensor (73) is lower than the temperature obtained by subtracting 3 ° C. from the set temperature Tset, and the low-pressure pressure sensor (65,
It is determined whether the condition 1 that the low-pressure refrigerant pressure LP detected by 66) is higher than 392 kPa is satisfied. In step ST82, the room temperature Tr is increased by 3 ° C. from the set temperature Tset.
And the low pressure refrigerant pressure LP is lower than 245 kP
It is determined whether the condition 2 that is lower than a is satisfied. In step ST83, the room temperature Tr is set to the set temperature.
It is determined whether a condition 3 that the pressure is higher than Tset and the low-pressure refrigerant pressure LP is higher than 392 kPa is satisfied. In step ST84, it is determined whether or not the condition 4 that the room temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.

If the condition 1 in step ST81 is satisfied, the process proceeds to step ST85, in which the capacity of the first inverter compressor (2B) or the non-inverter compressor (2A) is increased, and the process returns. If the condition 1 in step ST81 is not satisfied and the condition 2 in step ST82 is satisfied, the process proceeds to step ST86 and the outdoor fan (4F)
And returns. That is, since the heating capacity tends to be insufficient, the amount of heat condensed in the outdoor heat exchanger (4) is given to the indoor heat exchanger (41). If the condition 2 in step ST82 is not satisfied and the condition 3 in step ST83 is satisfied, the process proceeds to step ST87 and the outdoor fan (4
F) Increase the air flow and return. That is, since the heating capacity is rather low, the amount of heat condensed in the indoor heat exchanger (41) is given to the outdoor heat exchanger (4). Step ST8 above
When the condition 3 of 3 is not satisfied and the condition 4 of step ST84 is satisfied, the process proceeds to step ST88, and the process returns after reducing the capacity of the first inverter compressor (2B) or the non-inverter compressor (2A). In addition, the above step ST84
If the condition 4 is not satisfied, since the current compression function is satisfied, the process returns and repeats the above operation.
The control for increasing or decreasing the compressor capacity is performed as shown in FIG.

<Third heating / refrigeration operation 1> This third heating / refrigeration operation is performed during the first heating / refrigeration operation.
The heating capacity of B) is insufficient.
As shown in FIG. 9, one mode of the third heating / refrigeration operation is as follows.
The non-inverter compressor (2A) and the first inverter compressor (2B) constitute a first system compression mechanism (2D), and the second inverter compressor (2C) constitutes a second system compression mechanism (2E). Constitute. Then, while driving the non-inverter compressor (2A) and the first inverter compressor (2B), the booster compressor (53) is also driven. The second inverter compressor (2C) is stopped.

The third heating / refrigeration operation is an operation when the heating capacity is insufficient during the first heating / refrigeration operation.
That is, this is the case where the amount of heat of evaporation is insufficient, and is the same as the above-mentioned first heating / refrigeration operation except that the solenoid valve (7b) in the second sub pipe (24) of the communication pipe (21) is open. It is.

Therefore, the non-inverter compressor (2A)
And the refrigerant discharged from the first inverter compressor (2B) flows into the indoor heat exchanger (41) and is condensed similarly to the first heating and refrigeration operation. The condensed liquid refrigerant flows through the floor heating circuit (35), and flows from the floor heating heat exchanger (36) to the receiver (14).

Thereafter, a part of the liquid refrigerant from the receiver (14) flows through the first communication liquid pipe (11), and
Part of the liquid refrigerant flowing through 1) flows into the refrigeration heat exchanger (45) and evaporates. The other liquid refrigerant flowing through the first communication liquid pipe (11) flows into the refrigeration heat exchanger (51) and evaporates. The gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booster compressor (53) are connected to the low-pressure gas pipe (1).
Merge in 5) and return to the non-inverter compressor (2A) and first inverter compressor (2B).

On the other hand, another liquid refrigerant from the receiver (14) flows through the liquid pipe (10) to the outdoor heat exchanger (4) and evaporates. The evaporated gas refrigerant flows through the outdoor gas pipe (9), passes through the first four-way switching valve (3A) and the second four-way switching valve (3B), and the suction pipe (6c) of the second inverter compressor (2C). Flows through. The gas refrigerant flows into the low-pressure gas pipe (15) via the second sub pipe (24) of the communication pipe (21), and merges with the gas refrigerant from the refrigeration unit (1C) and the refrigeration unit (1D), Return to the non-inverter compressor (2A) and the first inverter compressor (2B).

This circulation is repeated to heat the inside of the store, which is a room, and perform floor heating, and at the same time, cool the inside of the refrigerator, which is a showcase for refrigeration and a showcase for freezing. That is,
The cooling capacity (heat evaporation amount) of the refrigeration unit (1C) and the refrigeration unit (1D), the indoor unit (1B) and the floor heating circuit (3
The heating capacity (condensed heat) of 5) does not balance, and insufficient evaporation heat is obtained from the outdoor heat exchanger (4).

The compressor capacity and outdoor fan (4F) air volume during the third heating / refrigeration operation are controlled as shown in FIG. 22, and the following four determinations are made.

That is, in step ST91, the room temperature Tr detected by the room temperature sensor (73) is lower than the temperature obtained by subtracting 3 ° C. from the set temperature Tset, and the low-pressure pressure sensor (65,
It is determined whether the condition 1 that the low-pressure refrigerant pressure LP detected by 66) is higher than 392 kPa is satisfied. In step ST92, the indoor temperature Tr is increased by 3 ° C. from the set temperature Tset.
And the low pressure refrigerant pressure LP is lower than 245 kP
It is determined whether the condition 2 that is lower than a is satisfied. In step ST93, the room temperature Tr is set to the set temperature.
It is determined whether a condition 3 that the pressure is higher than Tset and the low-pressure refrigerant pressure LP is higher than 392 kPa is satisfied. In step ST94, it is determined whether or not the condition 4 that the room temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.

If the condition 1 in step ST91 is satisfied, the process proceeds to step ST95, in which the capacity of the first inverter compressor (2B) or the non-inverter compressor (2A) is increased, and the process returns. If the condition 1 in step ST91 is not satisfied and the condition 2 in step ST92 is satisfied, the process proceeds to step ST96, and since the heating capacity is likely to be insufficient, the mode is switched to the second heating / refrigeration operation 2 described later. To return. If the condition 2 in step ST92 is not satisfied and the condition 3 in step ST93 is satisfied, the process proceeds to step ST97, where the flow rate of the outdoor fan (4F) is reduced, and the process returns. If the condition 3 in step ST93 is not satisfied and the condition 4 in step ST94 is satisfied, the process proceeds to step ST98, in which the capacity of the first inverter compressor (2B) or the non-inverter compressor (2A) is reduced and the process returns. I do. If the condition 4 in step ST94 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated. The control for increasing or decreasing the compressor capacity is performed as shown in FIG.

<Third Heating / Refrigeration Operation 2> This third heating / refrigeration operation 2 is another mode of the third heating / refrigeration operation, and is an operation for driving the second inverter compressor (2C). In the third heating and refrigeration operation, as shown in FIG. 10, the non-inverter compressor (2A) and the first inverter compressor (2B) constitute a first-system compression mechanism (2D), and the second inverter compressor Machine (2C) constitutes the second system compression mechanism (2E). Then, the non-inverter compressor (2A), the first inverter compressor (2B), and the second inverter compressor (2C) are driven, and the booster compressor (53) is also driven.

The second heating / refrigeration operation 2 is an operation in the case where the heating capacity is insufficient in the third heating / refrigeration operation 1, that is, the case where the amount of heat of evaporation is insufficient. ), Except that the solenoid valve (7b) in the second sub pipe (24) is closed and the second inverter compressor (2C) is driven.

Therefore, the non-inverter compressor (2A)
The refrigerant discharged from the first inverter compressor (2B) and the second inverter compressor (2C) flows through the connecting gas pipe (17) to the indoor heat exchanger (41) and condenses. The condensed liquid refrigerant flows through the floor heating circuit (35), and flows from the floor heating heat exchanger (36) to the receiver (14).

Thereafter, a part of the liquid refrigerant from the receiver (14) flows through the first communication liquid pipe (11), and
Part of the liquid refrigerant flowing through 1) flows into the refrigeration heat exchanger (45) and evaporates. The other liquid refrigerant flowing through the first communication liquid pipe (11) flows into the refrigeration heat exchanger (51) and evaporates. The gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booster compressor (53) are connected to the low-pressure gas pipe (1).
Merge in 5) and return to the non-inverter compressor (2A) and first inverter compressor (2B).

On the other hand, another liquid refrigerant from the receiver (14) flows through the liquid pipe (10) to the outdoor heat exchanger (4) and evaporates. The evaporated gas refrigerant flows through the outdoor gas pipe (9), flows through the first four-way switching valve (3A) and the second four-way switching valve (3B), and flows through the suction pipe (6c), and the second inverter compressor ( 2C)
Return to

This circulation is repeated to heat the inside of the store, which is a room, and perform floor heating, and at the same time, cool the inside of the refrigerator, which is a showcase for refrigeration and a showcase for freezing. That is,
The cooling capacity (heat evaporation amount) of the refrigeration unit (1C) and the refrigeration unit (1D), the indoor unit (1B) and the floor heating circuit (3
The heating capacity (condensed heat) of 5) does not balance, and insufficient evaporation heat is obtained from the outdoor heat exchanger (4). In particular, non-inverter compressor (2A) and first inverter compressor (2B)
And the second inverter compressor (2C) to secure the heating capacity.

The compressor capacity and the outdoor fan (4F) air volume in the second heating / refrigeration operation 2 are controlled as shown in FIG. 23, and the following four determinations are made.

That is, in step ST101, the room temperature Tr detected by the room temperature sensor (73) is lower than the temperature obtained by subtracting 3 ° C. from the set temperature Tset, and the low pressure pressure sensor (6
It is determined whether the condition 1 that the low-pressure refrigerant pressure LP detected by (5, 66) is higher than 392 kPa is satisfied. In step ST102, the room temperature Tr is lower than the temperature obtained by subtracting 3 ° C. from the set temperature Tset, and the low-pressure refrigerant pressure LP is 24
It is determined whether Condition 2 of lower than 5 kPa is satisfied. In step ST103, it is determined whether or not the condition 3 that the indoor temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is higher than 392 kPa is satisfied.
In step ST104, the room temperature Tr is set to the set temperature Ts.
It is determined whether the condition 4 that the pressure is higher than et and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.

Then, condition 1 in step ST101 described above
If the condition is satisfied, the process proceeds to step ST105, where the second
While increasing the capacity of the inverter compressor (2C), the first inverter compressor (2B) or the non-inverter compressor (2A)
And return. Step ST101 above
If the condition 1 of step ST102 is not satisfied and the condition 2 of step ST102 is satisfied, the process proceeds to step ST106, where the refrigeration unit (1C) and the refrigerating unit (1D) have too little capacity. While increasing the capacity of (2C), reduce the capacity of the first inverter compressor (2B) or the non-inverter compressor (2A) and return. If the condition 2 of step ST102 is not satisfied, step ST103
If the condition 3 is satisfied, the process proceeds to step ST107, where the capacity of the refrigeration unit (1C) and the refrigerating unit (1D) tends to be insufficient, so that the capacity of the second inverter compressor (2C) is reduced. 1 Increase the capacity of the inverter compressor (2B) or non-inverter compressor (2A) and return. If the condition 3 of step ST103 is not satisfied and the condition 4 of step ST104 is satisfied, the process proceeds to step ST108, where the capacity of the second inverter compressor (2C) is reduced and the first inverter compressor (2B) is reduced. Or reduce the capacity of the non-inverter compressor (2A) and return.
If the condition 4 in step ST104 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated.

<Switching of Heating Mode> Next, another switching operation between the first heating and refrigeration operation and the second heating and refrigeration operation will be described with reference to FIG.

In this case, the determination is made based on the high-pressure refrigerant pressure HP detected by the high-pressure pressure sensor (61). First, step S
At T111, it is determined whether or not the condition 1 that the high-pressure refrigerant pressure HP is higher than 2646 kPa is satisfied. When the condition 1 is satisfied, the high pressure refrigerant pressure is high and the current heating capacity is large, and the process proceeds to step ST112.
It is determined whether the outdoor heat exchanger (4) is an evaporator.

When the outdoor heat exchanger (4) is an evaporator, for example, in the state of the third heating / freezing operation 1 or the like, the process proceeds from the step ST112 to the step ST113, and the air volume of the outdoor fan (4F) is changed. Is determined to be the lowest. When the air volume of the outdoor fan (4F) is the minimum, the process proceeds from step ST113 to step ST114, and the second
Switch to heating / refrigeration operation and return.

In the above step ST113,
If the air volume of the outdoor fan (4F) is not the minimum, step S
The process proceeds to T115, in which the flow rate of the outdoor fan (4F) is reduced, and the process returns. If the outdoor heat exchanger (4) is not an evaporator in step ST112, step ST11
It moves to 6 and judges whether the air volume of the outdoor fan (4F) is the maximum or not. When the air volume of this outdoor fan (4F) is the maximum,
The process moves from step ST116 to step ST117, and returns after lowering the compression function. On the other hand, step S
In T116, when the air volume of the outdoor fan (4F) is not the maximum, the process proceeds to step ST118 and the outdoor fan (4F)
And return.

If the condition 1 in step ST111 is not satisfied, the process moves to step ST121, where the high-pressure refrigerant pressure HP
Is smaller than or equal to 1960 kPa. If this condition 2 is satisfied, it means that the high-pressure refrigerant pressure is low and the current heating capacity is low, and the process proceeds to step ST122 to determine whether or not the outdoor heat exchanger (4) is a condenser.

When the outdoor heat exchanger (4) is a condenser, for example, in the state of the second heating / freezing operation, the process proceeds from step ST122 to step ST123.
It is determined whether the air volume of the outdoor fan (4F) is minimum. If the air volume of this outdoor fan (4F) is the minimum, step S
The process moves from T123 to step ST124, switches to the first heating / refrigeration operation, and returns. If the airflow of the outdoor fan (4F) is not the lowest in step ST123, the process proceeds to step ST125 and the outdoor fan (4F)
Return after reducing the air flow in F).

By the above switching, switching to the first heating / refrigeration operation or the second heating / refrigeration operation is performed.

<Refrigerant Recovery Operation> Next, a refrigerant recovery operation is performed in the above-described refrigeration operation and first heating refrigeration operation.
That is, in FIG. 7, since the liquid refrigerant may accumulate in the outdoor heat exchanger (4) and the outdoor gas pipe (9), the communication pipe (2
The solenoid valve (7b) in the second sub pipe (24) of 1) is opened for a few minutes, or the second inverter compressor (2C) is driven for a predetermined time to recover the surplus refrigerant.

In FIG. 2, the low-pressure gas pipe (15)
Since the liquid refrigerant may accumulate in the communication pipe (21),
Open the solenoid valve (7) in the sub pipe (24) for a few minutes and collect the excess refrigerant.

As a result, liquid back at the next start-up is prevented, smooth start-up can be performed, and the amount of refrigerant charged can be reduced.

-Effects of Embodiment 1- As described above, according to the present embodiment, the heating operation, the first heating / refrigeration operation, the second heating / refrigeration operation, and the third heating / refrigeration operation are selectively performed. Therefore, it is possible to perform the operation corresponding to the operation condition. As a result, energy-saving operation with less waste can be performed.

In particular, since the excess or insufficient heating capacity of the indoor heat exchanger (41) can be adjusted by the outdoor heat exchanger (4), the cooling capacity of the refrigeration heat exchanger (45) and the like can be reduced. It can always be kept at a predetermined value. As a result,
The quality of products such as refrigerators can be reliably maintained.

That is, when the first heating / freezing operation is performed, since the heat is not exhausted from the outdoor heat exchanger (4), an efficient operation can be performed.

When the second heating / freezing operation is performed, the heat of condensation is released from the outdoor heat exchanger (4), and the air conditioning heat exchanger (4) is operated.
It is possible to suppress the excessive operation of 1) and a decrease in the capacity of the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51).

In the third heating / refrigeration operation, the heat of evaporation is released from the outdoor heat exchanger (4), and the capacity of the air-conditioning heat exchanger (41) decreases, and the refrigeration heat exchanger (45) and the refrigeration heat exchanger ( 51)
Excessive operation can be suppressed.

Further, since the surplus refrigerant under various operating conditions is recovered, liquid back at the next start-up is prevented, so that the start-up can be performed smoothly and the refrigerant charge can be reduced.

[0172]

Second Embodiment Next, a second embodiment of the present invention will be described in detail with reference to the drawings.

In this embodiment, as shown in FIG. 25, a four-way switching valve (91) is provided instead of the solenoid valves (7a, 7b) of the communication pipe (21) of the second embodiment.

That is, the first sub pipe (2) of the communication pipe (21)
Each of the 3) and the second sub pipe (24) is provided with two check valves (7, 7). One port of the four-way switching valve (91) is connected to the first port via the first passage (92).
It is connected between two check valves (7, 7) in the auxiliary pipe (23).

The other port of the four-way switching valve (91) is connected to the second sub pipe (24) through the second passage (93).
It is connected between two check valves (7, 7). Another port of the four-way switching valve (91) is connected to the third passage (9).
4) is connected to the degassing pipe (28). The remaining one port of the four-way switching valve (91) is configured as a closed closed port. That is, the four-way switching valve (91) may be a three-way switching valve.

When the refrigerant flows from the second system compression mechanism (2E) to the first system compression mechanism (2D), the four-way switching valve (91) is switched to the solid line state in FIG. 92)
And the second passage (93). In this case, the gas refrigerant in the suction pipe (6c) of the second inverter compressor (2C) is
It flows through the first passage (92) from the auxiliary pipe (23), and the four-way switching valve (9
After flowing through 1), it flows into the second passage (93), and flows through the second auxiliary pipe (24) to the low-pressure gas pipe (15).

Further, the first system compression mechanism (2D)
When flowing the refrigerant to the compression mechanism (2E) of the system, the four-way switching valve (91) is switched to the solid line state in FIG.
And the second passage (93). In this case, the gas refrigerant in the low-pressure gas pipe (15) flows from the first sub pipe (23) through the first passage (92), passes through the four-way switching valve (91), and passes through the second passage (93).
To the suction pipe (6c) of the second inverter compressor (2C) via the second sub pipe (24).

When shutting off the suction side of the first system compression mechanism (2D) and the suction side of the second system compression mechanism (2E), the four-way switching valve (91) is set to the broken line state in FIG. switching,
The first passage (92) communicates with the third passage (94), and the second passage (93) is connected to the closing port. Other configurations, operations, and effects are the same as those of the first embodiment.

[0179]

In another embodiment of the present invention,
One air conditioning heat exchanger (41) and one refrigeration heat exchanger (45)
And one refrigeration heat exchanger (51) is provided. However, the present invention may be provided with a plurality of air conditioning heat exchangers (45), or a plurality of refrigeration heat exchangers (51). 45) may be provided, or a plurality of refrigeration heat exchangers (51) may be provided. That is, a plurality of air conditioning heat exchangers (41) may be connected in parallel with each other, or a plurality of refrigeration heat exchangers (45) may be connected in parallel with each other. Further, a plurality of refrigeration heat exchangers (51) may be connected in parallel with each other.

In the above embodiments, cooling and heating are performed. However, the present invention may be such that only the heating mode operation is performed.

[Brief description of the drawings]

1 to 24 show a first embodiment of the present invention,
FIG. 1 is a circuit diagram showing a refrigerant circuit.

FIG. 2 is a refrigerant circuit diagram showing a refrigerant flow during a cooling operation.

FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow during a refrigeration operation.

FIG. 4 is a refrigerant circuit diagram showing a refrigerant flow during a first cooling and freezing operation.

FIG. 5 is a refrigerant circuit diagram showing a refrigerant flow during a second cooling and freezing operation.

FIG. 6 is a refrigerant circuit diagram showing a refrigerant flow during a heating operation.

FIG. 7 is a refrigerant circuit diagram illustrating a refrigerant flow during a first heating and refrigeration operation.

FIG. 8 is a refrigerant circuit diagram showing a refrigerant flow during a second heating and refrigeration operation.

FIG. 9 is a refrigerant circuit diagram illustrating a refrigerant flow during a third heating / refrigeration operation (part 1).

FIG. 10 is a refrigerant circuit diagram showing a refrigerant flow during a third heating / refrigeration operation (part 2).

FIG. 11 is a control flowchart showing operation switching in a cooling mode.

FIG. 12 is a control flowchart showing capacity control during cooling operation.

FIG. 13 is a performance characteristic diagram showing a change characteristic of a compressor capacity during a cooling operation.

FIG. 14 is a control flowchart showing capacity control during a refrigeration operation.

FIG. 15 is a performance characteristic diagram showing a change characteristic of a compressor capacity during a refrigeration operation.

FIG. 16 is a Mollier chart showing refrigerant behavior during the first cooling and freezing operation.

FIG. 17 is a control flow chart showing operation switching between the first cooling and freezing operation and the first cooling and freezing operation.

FIG. 18 is a control flowchart showing operation switching in a heating mode.

FIG. 19 is a control flowchart showing control of a compressor capacity during a heating operation.

FIG. 20 is a control flowchart showing capacity control during the first heating / refrigeration operation.

FIG. 21 is a control flowchart showing capacity control during a second heating and refrigeration operation.

FIG. 22 is a control flowchart showing capacity control in a third heating / refrigeration operation 1;

FIG. 23 is a control flowchart showing capacity control in a third heating / refrigeration operation No. 2;

FIG. 24 is a control flowchart showing operation switching in a heating mode.

FIG. 25 is a circuit diagram illustrating a main part of a refrigerant circuit according to the second embodiment of the present invention.

[Explanation of symbols]

 1 Refrigerator 1E Refrigerant circuit 1L High-pressure gas line 10 Liquid pipe (liquid line) 1M 1st low-pressure gas line 1N 2nd low-pressure gas line 21 Communication pipe (auxiliary line) 7a, 7b Solenoid valve (opening / closing mechanism) 2A Non-inverter Compressor 2B 1st inverter compressor 2C 2nd inverter compressor 2D 1st system compression mechanism 2E 2nd system compression mechanism 4 Outdoor heat exchanger (heat source side heat exchanger) 41 Indoor heat exchanger (air conditioning heat exchanger) ) 45 Refrigeration heat exchanger (cooling heat exchanger) 51 Refrigeration heat exchanger (cooling heat exchanger) 26, 42, 46, 52 Expansion valve (expansion mechanism)

 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Takeo Ueno 1304 Kanaokacho, Sakai-shi, Osaka Daikin Industries Inside the Kanaoka Plant of Sakai Seisakusho Co., Ltd. (72) Kazuhide Nomura 1304 Kanaokacho, Sakai-shi, Osaka Daikin Industries Stock (72) Inventor Akihiro Kajimoto 1304 Kanaoka-cho, Sakai-shi, Osaka Daikin Industries F-term in Sakai Works Kanaoka Factory (reference) 3L092 GA10 HA01 LA07

Claims (8)

[Claims] 1. A compressor (2B) and a heat source side heat exchanger (4)
, An expansion mechanism (26, 46...), An air conditioning heat exchanger (41) for air-conditioning the room, and a cooling heat exchanger (45) for cooling the inside of the refrigerator, and a refrigerant circuit (1E ), And the refrigerant circuit (1E) is provided with a refrigerant discharged from the compressor (2B).
Heating operation in which the refrigerant condenses in 1), evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26), and returns to the compressor (2B), and the refrigerant discharged from the compressor (2B) Air conditioning heat exchanger (4
Condensed in 1), passed through the expansion mechanism (46), and cooled in the cooling heat exchanger (4
5) Heat recovery operation in which the refrigerant evaporates and returns to the compressor (2B), and the refrigerant discharged from the compressor (2B) condenses in the heat source side heat exchanger (4), and the expansion mechanism (46) Via cooling heat exchanger (4
A refrigerating apparatus configured to perform at least selectively a refrigerating operation of performing a circulation that evaporates in 5) and returns to the compressor (2B). 2. A compressor (2B) and a heat source side heat exchanger (4).
, An expansion mechanism (26, 46...), An air conditioning heat exchanger (41) for air-conditioning the room, and a cooling heat exchanger (45) for cooling the inside of the refrigerator, and a refrigerant circuit (1E ), And the refrigerant circuit (1E) is provided with a refrigerant discharged from the compressor (2B).
Heating operation in which the refrigerant condenses in 1), evaporates in the heat source side heat exchanger (4) through the expansion mechanism (26), and returns to the compressor (2B), and the refrigerant discharged from the compressor (2B) A part of the refrigerant is condensed in the air-conditioning heat exchanger (41), and the other refrigerant is condensed in the heat source side heat exchanger (4). All the condensed liquid refrigerant passes through the expansion mechanism (46) and is cooled. ), The heating capacity is too high to circulate and return to the compressor (2B), and the refrigerant discharged from the compressor (2B) is condensed in the heat source side heat exchanger (4) and expanded by the expansion mechanism (46). Through the cooling heat exchanger (4
A refrigeration apparatus characterized in that the refrigeration apparatus is configured to at least selectively perform a refrigeration operation of performing circulation returning to the compressor (2B) in 5). 3. A compressor (2B) and a heat source side heat exchanger (4).
, An expansion mechanism (26, 46...), An air conditioning heat exchanger (41) for air-conditioning the room, and a cooling heat exchanger (45) for cooling the inside of the refrigerator, and a refrigerant circuit (1E ), And the refrigerant circuit (1E) is provided with a refrigerant discharged from the compressor (2B).
Heating operation in which the refrigerant condenses in 1), evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26), and returns to the compressor (2B), and the refrigerant discharged from the compressor (2B) Air conditioning heat exchanger (4
Part of the condensed liquid refrigerant condensed in 1) and the expansion mechanism (46)
Evaporates in the cooling heat exchanger (45), the other liquid refrigerant evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26), and the evaporated gas refrigerant returns to the compressor (2B) Insufficient heating capacity operation and the refrigerant discharged from the compressor (2B) condenses in the heat source side heat exchanger (4) and passes through the expansion mechanism (46) to the cooling heat exchanger (4).
A refrigeration apparatus characterized in that the refrigeration apparatus is configured to at least selectively perform a refrigeration operation of performing circulation returning to the compressor (2B) in 5). 4. The refrigerant circuit (1E) according to claim 1, wherein the refrigerant discharged from the compressor (2B) is condensed in the air-conditioning heat exchanger (41), and a part of the condensed liquid refrigerant is expanded. After passing through (46), it evaporates in the cooling heat exchanger (45), and the other liquid refrigerant evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26), and the evaporated gas refrigerant turns into the compressor (2B) A refrigeration apparatus characterized by being configured to be able to select a heating capacity shortage operation for performing circulation returning to the above. 5. The refrigerant circuit (1E) according to claim 2, wherein the refrigerant discharged from the compressor (2B) is condensed in the air-conditioning heat exchanger (41), and is cooled through the expansion mechanism (46). A refrigeration system characterized by being capable of selecting a heat recovery operation in which circulation is performed by evaporating in the cooler (45) and returning to the compressor (2B). 6. The refrigerant circuit (1E) according to claim 1, wherein a part of the refrigerant discharged from the compressor (2B) is condensed in the air-conditioning heat exchanger (41), and the other refrigerant exchanges heat on the heat source side. Excessive heating capacity operation, in which all liquid refrigerant condensed in the heat exchanger (4) evaporates in the cooling heat exchanger (45) through the expansion mechanism (46) and returns to the compressor (2B), and compression The refrigerant discharged from the air conditioner (2B) condenses in the air-conditioning heat exchanger (41), and a part of the condensed liquid refrigerant evaporates in the cooling heat exchanger (45) via the expansion mechanism (46), and the other liquid refrigerant Is evaporated in the heat source side heat exchanger (4) via the expansion mechanism (26), and the heating capacity is insufficient, in which the evaporated gas refrigerant circulates back to the compressor (2B). A refrigeration apparatus characterized by the above-mentioned. 7. The refrigerant circuit (1E) according to claim 1, wherein the refrigerant circuit (1E) includes a plurality of compressors (2B, 2C...),
A refrigeration apparatus characterized in that a refrigerant recovery operation for recovering surplus refrigerant in the refrigerant circuit (1E) to the compressors (2B ...) can be selected. 8. The refrigerant circuit (1E) according to claim 1, wherein the refrigerant circuit (1E) is provided with a floor heating heat exchanger (36) in series with the air conditioning heat exchanger (41). And refrigeration equipment.