JP2012117690A - Heat storage type air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat storage type air conditioner that avoids a refrigerant deficiency of a heat source unit and improves reliability.SOLUTION: The heat storage type air conditioner, equipped with interior units 1a, 1b, heat source units 2a, 2b connected in parallel so as to constitute one freezing cycle together with the interior units 1a, 1b, heat storage units 3a, 3b connected between the interior units 1a, 1b and heat source units 2a, 2b, and a controller 4, includes heat storage gas piping 50a which leads a refrigerant in a vapor-liquid two-phase state flowing out of a heat storage heat exchanger 22 of the heat storage unit 3a during heat storage operation to an upstream side of a compressor 7 of the heat source unit 2a, and heat storage gas piping 50b which leads a refrigerant in a vapor-liquid two-phase state flowing out of a heat storage heat exchanger 22 of the heat storage unit 3b during heat storage operation to an upstream side of a compressor 7 of the heat source unit 2b.

Description

  The present invention relates to a heat storage type air conditioner including a plurality of heat source units.

  2. Description of the Related Art Conventionally, a regenerative air conditioner that performs heat storage operation that generates ice at night (that is, stores cold energy) and performs heat storage cooling operation that uses ice during the day (that is, using heat storage) is known. (For example, refer to Patent Document 1). A heat storage air conditioner described in Patent Literature 1 includes a plurality of indoor units, and, for example, two heat source units (outdoor units) connected in parallel so as to form one refrigeration cycle together with these indoor units, And an ice storage unit connected between the indoor unit and the heat source unit. The number of heat source units can be changed to 3 or 4 or more according to the air conditioning load.

  In the heat storage type air conditioner described in Patent Document 1, in the case of the heat storage operation (ice making operation), the gas refrigerant is compressed by the compressors in the two heat source units, and is condensed by the outdoor heat exchanger to be the liquid refrigerant. The liquid refrigerant is supplied to one heat storage unit. Then, the heat in the heat storage tank (the heat exchanger in the heat storage tank) heats the liquid refrigerant and the water in the heat storage tank, thereby evaporating the liquid refrigerant into a gas refrigerant, and the water in the heat storage tank. To produce ice. The gas refrigerant is returned to the two heat source units.

  In the case of cooling operation using heat storage, as in the case of heat storage operation (ice making operation), the gas refrigerant is compressed by the compressors in the two heat source units and condensed in the outdoor heat exchanger to form liquid refrigerant. Is supplied to one heat storage unit. Then, the liquid refrigerant is supercooled by heat exchange between the liquid refrigerant and the ice in the heat storage tank in the heat storage heat exchanger of the heat storage unit, and the liquid refrigerant is supplied to a plurality of indoor units. The liquid refrigerant is evaporated into a gas refrigerant in the indoor heat exchanger of the indoor unit, and the gas refrigerant is returned to the two heat source units.

Japanese Patent Laid-Open No. 10-292937 (see FIGS. 1 and 2)

  However, there are the following problems in the above-described prior art.

  That is, as is apparent from the drawing, the heat storage air conditioner described in Patent Document 1 is configured to return the gas refrigerant from one heat storage unit to two heat source units during the heat storage operation. Specifically, the piping that becomes the outlet side of the heat storage heat exchanger of the heat storage unit during the heat storage operation is connected to the upstream side from the branch portion of the piping that divides the gas refrigerant to the two heat source units. Further, both of the two heat source units are operated during the heat storage operation.

  Here, on the outlet side of the heat storage heat exchanger during the heat storage operation, it is necessary to make a gas-liquid two-phase state in which the liquid refrigerant is mixed with the gas refrigerant. The reason is that, for example, if the refrigerant is superheated and gasified on the outlet side of the heat storage heat exchanger during the heat storage operation, the amount of icing on the outlet side of the heat storage heat exchanger decreases, and the amount of icing in the heat storage tank does not increase. This is because a uniform defect occurs. And if the amount of icing in the heat storage tank becomes non-uniform, a large stress is generated when the water expands to become ice and the heat transfer tube may be damaged. Therefore, it is desirable to make the amount of icing in the heat storage tank uniform, and the refrigerant is in a gas-liquid two-phase state on the outlet side of the heat storage heat exchanger during the heat storage operation.

  And in the branch part of piping which distributes a refrigerant | coolant to the two heat-source units mentioned above, according to the shape and attachment attitude | position of the branch part, a diversion ratio of a refrigerant, especially a liquid refrigerant changes. Therefore, depending on the conditions, there is a difference in the return amount of the refrigerant, particularly the liquid refrigerant, between the two heat source units. Then, a difference is also caused in the return amount of the oil dissolved in the liquid refrigerant. Therefore, there is a difference in the amount of oil held between the two heat source units, and a decrease in the amount of oil may cause problems such as poor lubrication in the compressor. Therefore, it was not preferable in terms of reliability.

  An object of the present invention is to provide a heat storage type air conditioner capable of avoiding a shortage of refrigerant in a heat source unit and improving reliability.

  (1) In order to achieve the above object, the present invention constitutes at least one indoor unit including an indoor heat exchanger for exchanging heat between refrigerant and indoor air, and constitutes one refrigeration cycle together with the indoor unit. A plurality of heat source units including a compressor that compresses the refrigerant and an outdoor heat exchanger that exchanges heat between the refrigerant and outdoor air, connected in parallel to the indoor unit via a gas pipe and a liquid pipe, and the indoor unit And a plurality of or one heat storage unit provided with a heat storage heat exchanger connected between the heat source unit and the heat storage medium to exchange heat with the heat storage medium, and the compressor to control the outdoor heat exchange And a control means for controlling a plurality of solenoid valves to selectively flow to any of the heat storage heat exchanger and the indoor heat exchanger, and the control means includes the compression And a plurality of solenoid valves to control at least the outdoor heat exchanger as a condenser and the heat storage heat exchanger as an evaporator, or the outdoor heat exchanger as a condenser and the heat storage heat exchange. In a regenerative air conditioner that switches to a regenerative cooling operation that operates as a supercooler and an indoor heat exchanger as an evaporator, a refrigerant in a gas-liquid two-phase state that flows out of the regenerative heat exchanger during a regenerative operation, Each of the heat storage units is configured to be supplied to the compressor in the corresponding one heat source unit.

  In the present invention as described above, it is possible to avoid distributing the gas-liquid two-phase refrigerant from one heat storage unit to a plurality of heat source units during the heat storage operation. Therefore, it is possible to avoid the shortage of refrigerant in the heat source unit that is likely to occur due to the distribution of the refrigerant in the gas-liquid two-phase state to the plurality of heat source units, and it is possible to improve the reliability.

  (2) In the above (1), preferably, the plurality of heat storage units are provided in the same number as the heat source unit, and each of the plurality of heat storage units and the plurality of heat source units are provided. Each one of each of the heat source units is connected so as to correspond to the gas-liquid two-phase refrigerant flowing out from the heat storage heat exchanger of each of the heat storage units during the heat storage operation. A plurality of first heat storage gas pipes led out to the side are provided.

  (3) In the above (2), preferably, the heat storage unit is provided at a position upstream of the heat storage heat exchanger during the heat storage operation, and an expansion valve that decompresses the refrigerant during the heat storage operation, and the heat storage unit during the heat storage operation. A temperature detector provided at a position downstream of the heat storage heat exchanger, and the control means has the same refrigerant temperature detected by the temperature detectors of all the heat storage units during the heat storage operation. Thus, the opening degree of the expansion valve is corrected.

  The upstream sides of the compressors in the plurality of heat source units communicate with each other via a gas pipe, and the refrigerant pressure on the upstream side of the compressors in all the heat source units, that is, the heat storage heat exchangers of all the heat storage units during the heat storage operation The refrigerant pressure on the downstream side is substantially the same. Therefore, if the expansion valve is corrected so that the refrigerant temperatures downstream of the heat storage heat exchangers of all the heat storage units are the same during the heat storage operation as in the present invention, the flow rate ratio of the refrigerant between the heat storage units is balanced. Can be adjusted well. As a result, the balance of the flow rate ratio of the refrigerant between the heat storage units can be improved. Therefore, shortage of refrigerant in the heat source unit can be avoided and reliability can be improved.

  (4) In the above (1), preferably, the control means drives the compressor in any one of the plurality of heat source units during the heat storage operation, and the other heat source. Stop the compressor in the unit.

  (5) In the above (4), preferably, each of the heat storage units is connected so that all the heat storage units correspond to each other, and the gas-liquid flowing out from the heat storage heat exchanger of the heat storage unit during the heat storage operation A second heat storage gas pipe for deriving a two-phase refrigerant to the upstream side of the compressor of the heat source unit; and the control means controls the compressor driven during the heat storage operation of the plurality of heat source units. One of them is selectively switched to that of the heat source unit.

  (6) In the above (4), preferably, the heat storage heat exchanger in all the heat storage units is connected so that one specific heat storage unit corresponds to all the heat storage units. A third heat storage gas pipe for leading the refrigerant in the gas-liquid two-phase state flowing out from the upstream side of the compressor in the one specific heat source unit, and the control means drives the compression during the heat storage operation The machine is fixed to that of the specific one heat source unit.

  (7) In any one of the above (2), (3), (5), and (6), preferably, the heat source unit connects a gas pipe from the indoor unit to a suction side of the compressor. At least one switching to communicate with one of the gas pipe and the discharge side gas pipe and to communicate the gas pipe from the heat exchanger with the other of the suction side gas pipe and the discharge side gas pipe of the compressor; The control means includes a switching valve, and the control means controls the plurality of electromagnetic valves including the compressor and the switching valve to operate the outdoor heat exchanger as an evaporator and the indoor heat exchanger as a condenser. Switching to operation is possible, and the first, second, or third heat storage gas pipe is connected to the suction side gas pipe of the compressor.

  (8) In any one of the above (2), (3), and (5) to (7), preferably, the heat storage unit is located upstream of the heat storage heat exchanger during heat storage operation. An expansion valve that depressurizes the refrigerant during the heat storage operation, a receiver tank provided at a position upstream of the expansion valve during the heat storage operation, a liquid pipe from the heat source unit and the indoor unit, and the receiver tank A first solenoid valve that communicates and blocks between, and a second solenoid valve that communicates and blocks between the heat storage heat exchanger and the first, second, or third heat storage gas pipe, A refrigerant return pipe connected between the receiver tank and the first, second, or third heat storage gas pipe; and a third solenoid valve for communicating / blocking the refrigerant return pipe; The control means is configured to perform the first and second operations during the heat storage operation. While the magnetic valve is open, the third electromagnetic valve is closed, and the expansion valve is controlled to be in the throttled state, the first and second electromagnetic valves are closed during the operation other than the heat storage operation, The third solenoid valve is controlled to be in an open state, and the expansion valve is controlled to be in a fully closed state.

  In the present invention, the refrigerant of the refrigeration cycle circulates through the receiver tank by controlling the first and second electromagnetic valves to the open state and the expansion valve to the throttle state during the heat storage operation. On the other hand, the refrigerant of the refrigeration cycle circulates without passing through the receiver tank by controlling the first and second electromagnetic valves to the closed state and the expansion valve to the fully closed state during other operations than the heat storage operation. That is, surplus refrigerant is stored in the receiver tank only during the heat storage operation, and the amount of refrigerant to the heat storage heat exchanger can be adjusted. Further, if the refrigerant stored in the receiver tank during the heat storage operation is stored as it is during the operation other than the heat storage operation, the refrigerant may be insufficient. Therefore, in the present invention, the third solenoid valve is controlled to be closed during the heat storage operation, while the third solenoid valve is controlled to be opened during the operation other than the heat storage operation. Thereby, the refrigerant | coolant in a receiver tank can be returned to a heat source unit etc. via refrigerant | coolant return piping and thermal storage gas piping at the time of driving | operations other than heat storage operation. Therefore, the refrigerant shortage of the heat source unit can be avoided even during other operation than the heat storage operation, and the reliability can be improved.

  According to the present invention, a shortage of refrigerant in the heat source unit can be avoided, and reliability can be improved.

It is a block diagram showing the whole structure of the thermal storage type air conditioner in the 1st Embodiment of this invention. It is a figure showing the structure of the indoor unit in the 1st Embodiment of this invention. It is a figure showing the structure of the heat-source unit in the 1st Embodiment of this invention. It is a figure showing the structure of the thermal storage unit in the 1st Embodiment of this invention, and shows the open / close state of the valve at the time of thermal storage operation. It is a figure showing the controller in the 1st Embodiment of this invention with a related apparatus. It is a figure showing the structure of the thermal storage unit in the 1st Embodiment of this invention, and shows the opening-and-closing state of the valve at the time of the thermal storage utilization cooling operation. It is a figure showing the structure of the heat storage unit in the 1st Embodiment of this invention, and shows the opening-and-closing state of the valve at the time of the heat storage non-use cooling operation or heating operation. It is a figure showing the structure of the thermal storage unit in the 2nd Embodiment of this invention, and shows the open / close state of the valve at the time of thermal storage operation. It is a figure showing the controller in the 2nd Embodiment of this invention with a related apparatus. It is a figure showing the whole structure of the thermal storage type air conditioning apparatus in the 3rd Embodiment of this invention. It is a figure showing the whole heat storage type air conditioner in a modification of the present invention.

  A first embodiment of the present invention will be described with reference to FIGS.

  FIG. 1 is a block diagram showing the overall configuration of a heat storage type air conditioner in the present embodiment. FIG. 2 is a diagram illustrating the configuration of the indoor unit in the present embodiment. FIG. 3 is a diagram illustrating the configuration of the heat source unit in the present embodiment. FIG. 4 is a diagram showing the configuration of the heat storage unit in the present embodiment, and shows the open / closed state of the valve during the heat storage operation (black is closed, white is open). FIG. 5 is a diagram illustrating the controller according to this embodiment together with related devices.

  1 to 5, the heat storage type air conditioner includes, for example, two indoor units 1a and 1b and, for example, two units connected in parallel so as to constitute one refrigeration cycle together with these indoor units 1a and 1b. Heat source units 2a and 2b, two heat storage units 3a and 3b, for example, connected between the indoor units 1a and 1b and the heat source units 2a and 2b, and a controller 4 are provided.

  The indoor units 1 a and 1 b are connected in parallel to the common gas pipe 30 and the common liquid pipe 40. Specifically, the indoor unit 1a is connected to the common gas pipe 30 via an indoor branch gas pipe 31a, and is connected to the common liquid pipe 40 via an indoor branch liquid pipe 41a. The indoor unit 1b is connected to the common gas pipe 30 via an indoor branch gas pipe 31b, and is connected to the common liquid pipe 40 via an indoor branch liquid pipe 41b.

  The indoor unit 1a includes an indoor heat exchanger 5 that exchanges heat between the refrigerant and room air, an indoor fan (not shown) that blows indoor air to the indoor heat exchanger 5, and a liquid refrigerant side of the indoor heat exchanger 5. And an indoor expansion valve (solenoid valve) 6 for depressurizing the refrigerant during cooling operation, which will be described later. The indoor unit 1b has the same configuration as the indoor unit 1a, and a description thereof will be omitted.

  The heat source units 2 a and 2 b are connected in parallel to the common gas pipe 30 and the common liquid pipe 40. Specifically, the heat source unit 2a is connected to the common gas pipe 30 via the outdoor branch gas pipe 32a, and is connected to the common liquid pipe 40 via the outdoor branch liquid pipes 42a and 42b and the heat storage unit 3a. ing. The heat source unit 2b is connected to the common gas pipe 30 via the outdoor branch gas pipe 32b, and is connected to the common liquid pipe 40 via the outdoor liquid pipes 42c and 42d and the heat storage unit 3b. An outdoor branch liquid pipe (communication pipe) 42e is connected between the outdoor branch liquid pipes 42a and 42c, and the heat source units 2a and 2b and the heat storage units are connected via the outdoor branch liquid pipes 42a, 42c and 42e. The units 3a and 3b are connected in parallel to each other.

  Further, as a major feature of the present embodiment, the heat storage gas pipe 50a is connected so that the heat storage unit 3a and the heat source unit 2a correspond, and the heat storage gas pipe 50b is connected so that the heat storage unit 3b and the heat source unit 2b correspond. (Details will be described later). Thereby, three pipes (specifically, the outdoor branch gas pipe 32a, the outdoor branch liquid pipe 42a, and the heat storage gas pipe 50a) are connected to the heat source unit 2a, and three pipes (in detail) are connected to the heat source unit 2b. Are connected to the outdoor branch gas pipe 32b, the outdoor branch liquid pipe 42c, and the heat storage gas pipe 50b).

  The heat source unit 2a includes a compressor 7 that compresses refrigerant, an outdoor heat exchanger 8 that exchanges heat between the refrigerant and outdoor air, an outdoor fan 9 that blows outdoor air to the outdoor heat exchanger 8, and an outdoor heat exchanger. 8 is provided on the liquid refrigerant side (lower side in FIG. 3), and an outdoor expansion valve (solenoid valve) 10 for depressurizing the refrigerant during heating operation to be described later. The heat source unit 2a switches the outdoor branch gas pipe 32a to communicate with one of the suction side gas pipe (low pressure gas pipe) 11 and the discharge side gas pipe (high pressure gas pipe) 12 of the compressor 7. A three-way valve 13b (electromagnetic valve) that switches the valve 13a (electromagnetic valve) and the gas pipe 14 from the outdoor heat exchanger 8 to communicate with the other of the suction side gas pipe 11 and the discharge side pipe 12 of the compressor 7 And. In addition, the thermal storage gas piping 50a mentioned above is connected to the suction side gas piping 11 of the compressor 7 of the thermal storage unit 2a.

  Further, the heat source unit 2a includes a supercooling circuit 15 for supercooling the liquid refrigerant during a heat storage non-use cooling operation described later. The subcooling circuit 15 includes a bypass pipe 17 connected between the liquid pipe 16 from the outdoor heat exchanger 8 and the suction side pipe 11 of the compressor 7, and a bypass expansion valve ( (Electromagnetic valve) 18 and a supercooling heat exchanger 19 for exchanging heat between the refrigerant on the bypass pipe 17 side and the refrigerant on the liquid pipe 16 side. Then, during the heat storage non-use cooling operation, the bypass expansion valve 18 is controlled to the throttle state (in other words, between the fully closed state and the fully open state). Thereby, a part of the refrigerant from the outdoor heat exchanger 8 is depressurized by the bypass expansion valve 18 to lower the temperature, and the supercooling heat exchanger 19 exchanges heat with the remaining liquid refrigerant. Thereby, a part of the refrigerant evaporates to become superheated gas, and this superheated gas flows out to the suction gas pipe 11 of the compressor 7. On the other hand, the remaining refrigerant is supercooled and flows out to the outdoor branch liquid pipe 42a.

  The heat source unit 2b has the same configuration as the heat source unit 2a, and a description thereof will be omitted.

  The heat storage unit 3 a is provided in the heat storage tank 21, a liquid pipe 20 connected between the outdoor branch liquid pipes 42 a and 42 b, a heat storage tank (water tank) 21 that stores water as a heat storage medium, and the heat storage tank 21. And a heat storage heat exchanger 22 for exchanging heat between the refrigerant and water. Further, a branch pipe 23a connected between one inlet / outlet side (right side in FIG. 3) of the heat storage heat exchanger 22 and the liquid pipe 20, and an on-off valve (electromagnetic valve) 24a interposed in the branch pipe 23a. A receiver tank 25 and a heat storage expansion valve (solenoid valve) 26. The heat storage expansion valve 26 is for depressurizing the refrigerant during a heat storage operation described later, and the receiver tank 25 is for storing surplus refrigerant during a heat storage operation described later. In addition, since the surplus refrigerant | coolant amount stored by the receiver tank 25 is decided according to the internal volume of the heat storage heat exchanger 22, the volume of the receiver tank 25 is designed based on this.

  Further, the heat storage unit 3a is interposed between the branch pipe 23b connected between the portion of the branch pipe 23a between the heat storage expansion valve 26 and the heat storage heat exchanger 22 and the liquid pipe 20, and the branch pipe 23b. And a check valve 27 that allows a flow from the heat storage heat exchanger 22 side to the liquid pipe 20 side. Further, a branch pipe 23c connected between the other inlet / outlet side (the left side in FIG. 3) of the heat storage heat exchanger 22 and the above-described heat storage gas pipe 50a, and an open / close valve (electromagnetic) interposed in the branch pipe 23c. Valve) 24b, a refrigerant return pipe 28 connected between the heat storage gas pipe 50a side (left side in FIG. 4) and the receiver tank 25 from the on-off valve 24b in the branch pipe 23c, and the refrigerant return pipe 28. And an open / close valve (electromagnetic valve) 24c. In addition, a branch pipe 23d connected between the heat storage heat exchanger 22 side (right side in FIG. 4) and the liquid pipe 20 from the on-off valve 24b in the branch pipe 23c, and an on-off valve interposed in the branch pipe 23d ( 24d, and an open / close valve (solenoid valve) 24e positioned between the connecting part of the branch pipe 23b (and the connecting part of the branch pipe 23a) and the connecting part of the branch pipe 24d in the liquid pipe 20. .

  The heat storage unit 3b has the same configuration as the heat storage unit 3a, and a description thereof is omitted.

  The controller 4 includes the indoor expansion valve 6 in the indoor units 1a and 1b, the three-way valves 13a and 13b in the heat storage units 2a and 2b, the compressor 7, the outdoor blower 9, the outdoor expansion valve 10, the bypass expansion valve 18, and the heat storage. The on-off valves 24a to 24e and the heat storage expansion valve 26 in the units 3a and 3b are controlled. Thereby, switching to any one of the heat storage operation, the heat storage use cooling operation, the heat storage non-use cooling operation, and the heating operation is performed. In the present embodiment, the specifications of the indoor units 1a and 1b are the same (specifically, the capabilities of the indoor heat exchanger 5, the indoor blower, and the indoor expansion valve 6 are the same), and the specifications of the heat source units 2a and 2b are the same. Same (specifically, the capacity of the compressor 7, the outdoor heat exchanger 8, the outdoor blower 9, the outdoor expansion valve 10, the bypass expansion valve 18, and the supercooling heat exchanger 19 is the same), specifications of the heat storage units 3a and 3b Are the same (specifically, the heat storage heat exchanger 22, the receiver tank 25, and the heat storage expansion valve 26 have the same capabilities), and the controller 4 sets the control amounts of the indoor units 1a and 1b to be the same, and the heat source unit 2a, The control amount of 2b is the same, and the control amounts of the heat storage units 3a and 3b are the same. As one specific example, the rotation speed of the compressor 7 in the heat source units 2a and 2b is the same.

  Next, the main effect is demonstrated with the operation | movement at the time of the thermal storage driving | operation in this embodiment.

(1) During heat storage operation A heat storage operation is performed in which ice is generated (stores cold energy) in the heat storage tank 21 of the heat storage units 3a and 3b. During the heat storage operation, the controller 4 operates both the heat source units 2a and 2b. Specifically, the compressor 7 and the outdoor blower 9 in the heat source units 2a and 2b are driven, and the outdoor expansion valve 10 is controlled to be fully opened, and the bypass expansion valve 18 is controlled to be fully closed. Further, the three-way valves 13a and 13b are controlled, and the outdoor branch gas pipe 32a is connected to the suction side gas pipe 11 of the compressor 7 as shown by the solid line in FIG. The pipe 14 is switched to communicate with the discharge side pipe 12 of the compressor 7. Thereby, the gas refrigerant is compressed by the compressor 7, the gas refrigerant flows into the outdoor heat exchanger 8 via the three-way valve 13b, and is condensed in the outdoor heat exchanger 8 to become a liquid refrigerant (that is, outdoor heat). The exchanger 8 operates as a condenser), and the liquid refrigerant (specifically, saturated liquid refrigerant) is supplied to the heat storage units 3a and 3b via the outdoor branch liquid pipes 42a, 42c, and 42e.

  Further, as shown in FIG. 4, the controller 4 controls the on-off valves 24a, 24b, 24e in the heat storage units 3a, 3b to be in an open state and the on-off valves 24c, 24d to be in a closed state, and the heat storage expansion valve 26 to be turned on. Control the aperture state. As a result, the liquid refrigerant from the heat source units 3a and 3b flows into the receiver tank 25 via the on-off valves 24e and 24a, a part of which flows out from the receiver tank 25 to the heat storage expansion valve 26, and the remainder (surplus). It is stored in the receiver tank 25. That is, the amount of refrigerant stored in the heat storage heat exchanger 22 fluctuates only during the heat storage operation, and the refrigerant amount is automatically adjusted by the receiver tank 25 during the heat storage operation. Then, the liquid refrigerant is depressurized and lowered in temperature by the heat storage expansion valve 26, and the liquid refrigerant is evaporated by heat exchange with the water in the heat storage tank 21 in the heat storage heat exchanger 22 to become a gas refrigerant (that is, heat storage). The heat exchanger 22 operates as an evaporator). On the other hand, the water in the heat storage tank 21 is deprived of heat due to the heat exchange with the refrigerant described above, the temperature gradually decreases, and when it sufficiently decreases, the water accumulates around the heat storage heat exchanger 22.

  Here, on the outlet side of the heat storage heat exchanger 22, a gas-liquid two-phase state in which the liquid refrigerant is mixed with the gas refrigerant is provided. The reason is that, for example, when the refrigerant is superheated and gasified on the outlet side of the heat storage heat exchanger 22, the amount of icing on the outlet side of the heat storage heat exchanger 22 decreases, and the amount of icing in the heat storage tank 21 is uneven. This is because a problem occurs. And if the amount of icing in the heat storage tank 21 becomes non-uniform | heterogenous, when water will become ice and volume expansion will occur, there exists a possibility that a heat exchanger tube may be damaged. Therefore, it is desirable to make the amount of icing in the heat storage tank 21 uniform, and the refrigerant is in a gas-liquid two-phase state on the outlet side of the heat storage heat exchanger 22.

  In the present embodiment, the gas-liquid two-phase refrigerant flowing out of the heat storage heat exchanger 22 of the heat storage unit 3a flows to the suction side of the compressor 7 of the heat source unit 2a via the on-off valve 24b and the heat storage gas pipe 50a. Returned. Further, the gas-liquid two-phase refrigerant flowing out from the heat storage heat exchanger 22 of the heat storage unit 3b is returned to the suction side of the compressor 7 of the heat source unit 2b via the on-off valve 24b and the heat storage gas pipe 50b. That is, the gas-liquid two-phase refrigerant is not distributed from the heat storage unit 3a to the heat source units 2a, 2b, and similarly, the gas-liquid two-phase refrigerant is not distributed from the heat storage unit 3b to the heat source units 2a, 2b. It is possible to avoid the shortage of refrigerant in the heat source unit that is likely to occur due to the distribution of the refrigerant in the liquid two-phase state. Therefore, for example, problems such as poor lubrication in the compressor 7 can be avoided, and the reliability can be improved.

  In the present embodiment, since both the heat source units 2a and 2b are operated during the heat storage operation, for example, compared with a case where only one of the heat source units 2a and 2b is operated, the heat storage operation time is shortened and the heat storage rate ( In other words, it is possible to improve the heat storage amount per unit time.

  Next, other operations and effects will be described together with the operations during the operation other than the heat storage operation in the present embodiment (specifically, during the heat storage use cooling operation, during the heat storage non-use cooling operation, and during the heating operation).

(2) Cooling operation using heat storage Cooling operation using ice in the heat storage tank 21 of the heat storage units 3a and 3b (that is, using heat storage) is performed. During the heat storage cooling operation, the controller 4 operates one or both of the heat source units 2a and 2b according to the load on the indoor unit side. Specifically, the compressor 7 and the outdoor blower 9 in one or both of the heat source units 2a and 2b are driven, and the outdoor expansion valve 10 is controlled to be fully opened, and the bypass expansion valve 18 is controlled to be fully closed. Further, the three-way valves 13a and 13b are controlled, and the outdoor branch gas pipe 32a is connected to the suction side gas pipe 11 of the compressor 7 as shown by the solid line in FIG. The pipe 14 is switched to communicate with the discharge side pipe 12 of the compressor 7. Thereby, the gas refrigerant is compressed by the compressor 7, the gas refrigerant flows into the outdoor heat exchanger 8 via the three-way valve 13b, and is condensed in the outdoor heat exchanger 8 to become a liquid refrigerant (that is, outdoor heat). The exchanger 8 operates as a condenser), and the liquid refrigerant (specifically, saturated liquid refrigerant) is supplied to the heat storage units 3a and 3b via the outdoor branch liquid pipes 42a, 42c, and 42e.

  Further, as shown in FIG. 6, the controller 4 controls the on-off valves 24a, 24b, 24e in the heat storage units 3a, 3b to be closed and the on-off valves 24c, 24d to be opened, and fully closes the heat storage expansion valve 26. Control to the state. Thereby, the liquid refrigerant from one or both of the heat source units 2a and 2b flows into the heat storage heat exchanger 22 via the on-off valve 24d and is supercooled by heat exchange with the ice in the heat storage tank 21 (that is, The heat storage heat exchanger 22 operates as a supercooler), and the supercooled liquid refrigerant flows out through the check valve 27 and is supplied to the indoor unit through the common liquid pipe 40 and the like.

  Further, the controller 4 controls, for example, the indoor expansion valve 6 in the indoor units 1a and 1b to the throttle state (or controls the indoor expansion valve 6 in one of the indoor units 1a and 1b to the throttle state and The indoor expansion valve 6 is fully closed). Thereby, the liquid refrigerant from the heat storage units 3a and 3b is depressurized and lowered in temperature by the indoor expansion valve 6, and the liquid refrigerant is evaporated by heat exchange with indoor air in the indoor heat exchanger 5 to become a gas refrigerant ( That is, the indoor heat exchanger 5 operates as an evaporator), and the gas refrigerant (specifically, saturated gas refrigerant or superheated gas refrigerant) is returned to the heat source unit via the common gas pipe 30 and the like, It returns to the compressor 7 through the three-way valve 13a.

  In this heat storage-based cooling operation, the liquid refrigerant is supercooled by heat exchange with ice in the heat storage tank 21 of the heat storage units 3a, 3b to obtain a low temperature state with a low specific enthalpy, and the liquid refrigerant is used in the indoor heat exchanger 5 of the indoor unit. Since the enthalpy difference at the time of evaporating is increased, the cooling capacity is improved. Further, the cooling capacity can be improved without increasing the work of the compressor, and a highly efficient cooling operation can be performed.

(3) Cooling operation not using heat storage Cooling operation is performed in which the ice in the heat storage tank 21 of the heat storage units 3a and 3b is not used (that is, heat storage is not used). During the heat storage non-use cooling operation, the controller 4 operates one or both of the heat source units 2a and 2b according to the load on the indoor unit side. Specifically, the compressor 7 and the outdoor blower 9 in one or both of the heat source units 2a and 2b are driven, and the outdoor expansion valve 10 is controlled to be fully opened. Further, the bypass expansion valve 18 is controlled to the throttle state. Further, the three-way valves 13a and 13b are controlled, and the outdoor branch gas pipe 32a is connected to the suction side gas pipe 11 of the compressor 7 as shown by the solid line in FIG. The pipe 14 is switched to communicate with the discharge side pipe 12 of the compressor 7. Thereby, the gas refrigerant is compressed by the compressor 7, the gas refrigerant flows into the outdoor heat exchanger 8 through the three-way valve 13b, and is condensed in the outdoor heat exchanger 8 to become a liquid refrigerant (that is, outdoor The heat exchanger 8 operates as a condenser). Then, a part of the liquid refrigerant is depressurized and reduced in temperature by the bypass expansion valve 18, and evaporated by heat exchange with the remaining liquid refrigerant in the supercooling heat exchanger 19, and this superheated gas is converted into a compressor. 7 flows out into the suction gas pipe 11. On the other hand, the liquid refrigerant supercooled by the heat exchange described above flows out to the heat storage units 3a and 3b through the outdoor branch liquid pipes 42a, 42c and 42e.

  Further, as shown in FIG. 7, the controller 4 controls the on-off valves 24a, 24b, 24d in the heat storage units 3a, 3b to be closed and the on-off valves 24c, 24e to be in the open state, and fully closes the heat storage expansion valve 26. Control to the state. Thereby, the liquid refrigerant from one or both of the heat source units 2a and 2b flows out through the on-off valve 24e and is supplied to the indoor unit through the common liquid pipe 40 and the like.

  Further, the controller 4 controls, for example, the indoor expansion valve 6 in the indoor units 1a and 1b to the throttle state (or controls the indoor expansion valve 6 in one of the indoor units 1a and 1b to the throttle state and The indoor expansion valve 6 is fully closed). Thereby, the liquid refrigerant from the heat storage units 3a and 3b is depressurized and lowered in temperature by the indoor expansion valve 6, and the liquid refrigerant is evaporated by heat exchange with indoor air in the indoor heat exchanger 5 to become a gas refrigerant ( That is, the indoor heat exchanger 5 operates as an evaporator), and the gas refrigerant (specifically, saturated gas refrigerant or superheated gas refrigerant) is returned to the heat source unit via the common gas pipe 30 and the like, It returns to the compressor 7 through the three-way valve 13a.

(4) During heating operation During the heating operation, the controller 4 operates one or both of the heat source units 2a and 2b according to the load on the indoor unit side. Specifically, the compressor 7 and the outdoor blower 9 in one or both of the heat source units 2a and 2b are driven, and the bypass expansion valve 18 is controlled to be fully opened. Further, the outdoor expansion valve 10 is controlled to be in the throttle state. Further, the three-way valves 13a and 13b are controlled, and the outdoor branch gas pipe 32a is communicated to the discharge side pipe 12 of the compressor 7 as shown by the dotted line in FIG. 14 is switched to communicate with the suction side gas pipe 11 of the compressor 7. Thereby, the gas refrigerant is compressed by the compressor 7, and the gas refrigerant flows out through the three-way valve 13a and is supplied to the indoor unit through the common gas pipe 30 and the like.

  For example, the controller 4 controls the indoor expansion valve 6 in the indoor units 1a and 1b to a fully open state (or controls the indoor expansion valve 6 in one of the indoor units 1a and 1b to a fully open state and The indoor expansion valve 6 is fully closed). Thereby, the refrigerant from the heat source unit is condensed by the heat exchange with the indoor air in the indoor heat exchanger 5 to become a liquid refrigerant (that is, the indoor heat exchanger 5 operates as a condenser), and the liquid refrigerant (details) , A saturated liquid refrigerant or a supercooled liquid refrigerant) flows out to the heat storage units 3a and 3b through the common gas pipe 30 and the like.

  Further, as shown in FIG. 7, the controller 4 controls the on-off valves 24a, 24b, 24d in the heat storage units 3a, 3b to be closed and the on-off valves 24c, 24e to be in the open state, and fully closes the heat storage expansion valve 26. Control to the state. Thereby, the liquid refrigerant from one or both of the indoor units 1a and 1b flows out through the on-off valve 24e and is supplied to the heat source unit through the common liquid pipe 40 and the like.

  In one or both of the heat source units 2a and 2b, the liquid refrigerant is depressurized and reduced in temperature by the outdoor expansion valve 10, and the liquid refrigerant is evaporated by heat exchange with outdoor air in the outdoor heat exchanger 8. It becomes a refrigerant (that is, the outdoor heat exchanger 8 operates as an evaporator), and the gas refrigerant is returned to the compressor 7 through the three-way valve 13b.

  Note that, in the above-described case where the heat storage non-utilizing cooling operation and the heating operation are performed, the controller 4 has been described as an example of controlling the on-off valve 24d in the heat storage units 3a and 3b to be closed. In order to fill the valve, the on-off valve 24d may be controlled to be in an open state.

  As described above, in the present embodiment, the refrigerant in the refrigeration cycle passes through the receiver tank 25 by controlling the on-off valves 24a, 24b, and 24e to the open state and the heat storage expansion valve 26 to the throttled state during the heat storage operation. On the other hand, during the operation other than the heat storage operation, the refrigerant in the refrigeration cycle circulates without passing through the receiver tank 25 by controlling the on-off valves 24a and 24b to be closed and the heat storage expansion valve 26 to be fully closed. ing. Thereby, surplus refrigerant | coolant is stored by the receiver tank 25 only at the time of a thermal storage driving | operation, and the refrigerant | coolant amount to the thermal storage heat exchanger 22 can be adjusted. In addition, if the refrigerant stored in the receiver tank 25 during the heat storage operation is stored as it is during the operation other than the heat storage operation, the refrigerant may be insufficient. Therefore, in the present embodiment, the on-off valve 24c is controlled to be closed during the heat storage operation, while the on-off valve 24c is controlled to be open during other operations than the heat storage operation. Thereby, at the time of operation other than the heat storage operation, the refrigerant in the receiver tank 25 of the heat storage unit 3a is returned to the compressor 7 of the heat source unit 2a via the refrigerant return pipe 28 and the heat storage gas pipe 50a, and the receiver tank of the heat storage unit 3b. The refrigerant in 25 is returned to the compressor 7 of the heat source unit 2b through the refrigerant return pipe 28 and the heat storage gas pipe 50b. Therefore, the refrigerant shortage of the heat source unit can be avoided even during other operation than the heat storage operation, and the reliability can be improved.

  In the first embodiment, the heat source unit 2a (or 2b) is configured such that the outdoor branch gas pipe 32a (or 32b) is one of the suction side gas pipe 11 and the discharge side gas pipe 12 of the compressor 7. And three-way valves (switching valves) 13a and 13b for switching the gas pipe 14 from the outdoor heat exchanger 8 to communicate with the other of the suction side gas pipe 11 and the discharge side pipe 12 of the compressor 7. However, the present invention is not limited to this. That is, instead of the three-way valves 13a and 13b, for example, the outdoor branch gas pipe 32a (or 32b) is communicated with one of the suction side gas pipe and the discharge side gas pipe of the compressor 7, and the outdoor heat exchanger 8 May be provided with one four-way valve (switching valve) that switches the gas pipe from the other side to the other of the suction side gas pipe and the discharge side pipe of the compressor 7. Further, for example, the above-described three-way valve and four-way valve may not be provided, and the heating operation may not be performed. In these cases, the same effect as described above can be obtained.

  Moreover, in the said 1st Embodiment, although heat source unit 2a, 2b demonstrated taking the case where the supercooling circuit 15 was provided as an example, it is not restricted to this, The supercooling circuit 15 does not need to be provided. In this case, the same effect as described above can be obtained.

  Moreover, in the said 1st Embodiment, although heat source unit 2a, 2b demonstrated taking as an example the case where each provided the one compressor 7, it is not restricted to this. That is, a plurality of compressors may be provided. Then, the number of operating units may be variably controlled so that the refrigerant flow rates of the heat source units 2a and 2b are equal, or the rotational speed of one of the compressors may be variably controlled via an inverter. In such a case, the same effect as described above can be obtained.

  Moreover, in the said 1st and 2nd embodiment, the case where it applies to the structure provided with the two indoor units 1a and 1b, the two heat source units 2a and 2b, and the two heat storage units 3a and 3b. Although described as an example, the present invention is not limited to this. That is, for example, one or three or more indoor units may be provided. Moreover, for example, the heat source unit and the heat storage unit may be provided in the same number, and may be provided in three or more units. In that case, the same number of heat storage gas pipes may be provided. That is, the heat storage gas pipes may be connected so that each of the plurality of heat storage units corresponds to one of the plurality of heat source units. In such a case, the same effect as described above can be obtained.

  A second embodiment of the present invention will be described with reference to FIGS. Note that in this embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted as appropriate.

  FIG. 8 is a diagram illustrating the configuration of the heat storage unit in the present embodiment. FIG. 9 is a diagram illustrating the controller according to the present embodiment together with related devices.

  In the present embodiment, a temperature sensor (temperature detector) 29 is provided in the branch pipe 23c of the heat storage units 3a and 3b (that is, a position on the downstream side of the heat storage exchanger 22 during the heat storage operation). The refrigerant temperature detected by the temperature sensor 29 of the heat storage units 3 a and 3 b is output to the controller 4.

  During the heat storage operation, the controller 4 corrects the opening degree of the heat storage expansion valve 26 so that the detected temperature of the temperature sensor 29 of the heat storage unit 3a and the detected temperature of the temperature sensor 29 of the heat storage unit 3b are the same. Specifically, for example, the difference between the detected temperature of the temperature sensor 29 of the heat storage unit 3a and the detected temperature of the temperature sensor 29 of the heat storage unit 3b is calculated, and the opening degree of the heat storage expansion valve 26 of the heat storage unit with the higher detected temperature is calculated. Increase according to the difference. Thereby, the refrigerant | coolant flow volume of the downstream of the heat storage exchanger 22 in heat storage unit 3a, 3b can be made the same.

  More specifically, the upstream side of the compressor 7 in the heat source units 2a and 2b communicates with each other via the outdoor branch gas pipes 32a and 32b, and the refrigerant pressure upstream of the compressor 7 in the heat source units 2a and 2b, that is, The refrigerant pressure on the downstream side of the heat storage heat exchanger 22 in the heat storage units 3a and 3b is substantially the same. And since the specification of heat storage unit 3a, 3b is the same, if the opening degree of the heat storage expansion valve 26 is corrected so that the refrigerant temperature of the downstream of the heat storage heat exchanger 22 in heat storage unit 3a, 3b may become the same. The refrigerant flow rate ratio between the heat storage units 3a and 3b can be adjusted to be the same. As a result, the flow rate ratio of the refrigerant between the heat source units 2a and 2b is the same. Moreover, the effect that the refrigerant | coolant flow volume in one of heat-source unit 2a, 2b decreases and it can prevent that it superheats and gasifies at the exit side of the thermal storage heat exchanger 22 is also acquired.

  Therefore, in the present embodiment, compared with the first embodiment, a shortage of refrigerant in the heat source unit can be avoided, and the reliability can be improved.

  In the first and second embodiments, the heat source units 2a and 2b have the same specifications, the heat storage units 3a and 3b have the same specifications, and the outdoor branch liquid between the outdoor branch liquid pipes 42a and 42c. The case where the pipe 42e is provided has been described as an example, but is not limited thereto. That is, for example, the outdoor branch liquid pipe 42e is not provided between the outdoor branch liquid pipes 42a and 42c, the compressor 7 or the like of one heat source unit 2a has a relatively large capacity, and the other heat source unit 2b is compressed. The heat storage heat exchanger 22 or the like of one heat storage unit 3b is made to have a relatively large capacity and the heat storage heat exchanger of the other heat storage unit 3a so as to correspond to the capacity ratio of the machine 7 or the like. 22 or the like may be a relatively small capacity. In that case, the refrigerant and the heat source unit 2a and the heat storage unit 3a have a large flow rate of refrigerant and the other heat source unit 2b and the heat storage unit 3b have a small flow rate of refrigerant. The compressor of 2b is supplied with a refrigerant having a flow rate corresponding to each capacity. Therefore, also in such a modification, the same effect as the first and second embodiments can be obtained.

  Moreover, in the said 1st or 2nd embodiment, as shown in above-mentioned FIG. 5 or FIG. 9, the compressor 7, the outdoor air blower 9, and the electromagnetic valves 6, 13a, 13b, 10, 18, 24a-24e. However, the controller 4 (control means) that controls the indoor units 1a and 1b, the heat source units 2a and 2b, and the heat storage units 3a and 3b is described as an example. Absent. That is, for example, each indoor unit 1a, 1b is provided with a first control unit that controls the electromagnetic valve 6, and the heat source unit 2a, 2b is provided with a compressor 7, an outdoor blower 9, and electromagnetic valves 13a, 13b, 10, 18 respectively. A second control unit for controlling the electromagnetic valves, and a third control unit for controlling the electromagnetic valves 24a to 24e and 26 in the heat storage units 3a and 3b, respectively, and the first to third control units control in cooperation with each other. You may comprise. In this case, the same effect as described above can be obtained.

  A third embodiment of the present invention will be described with reference to FIG. In the present embodiment, the compressor or the like that is driven during the heat storage operation is selectively switched to that of any one of the plurality of heat source units. In addition, the same code | symbol is attached | subjected to the part equivalent to the said 1st Embodiment, and description is abbreviate | omitted suitably.

  FIG. 10 is a block diagram showing the overall configuration of the heat storage type air conditioner in the present embodiment.

  In the present embodiment, the heat source units 2a and 2b and the heat storage units 3a and 3b are connected in parallel to each other via the heat storage gas pipes 51a to 51c. In other words, the heat storage gas pipes 51a to 51c are connected so that the heat storage units 2a and 2b correspond to the heat storage unit 3b so that the heat source units 2a and 2b correspond to the heat storage unit 3a. ing.

  And the controller 4 drives the compressor 7 and the outdoor air blower 9 in any one heat source unit of the heat source units 2a and 2b during the heat storage operation, and the compressor 7 and the outdoor air blower 9 in the other heat source units are driven. Stop. More specifically, the heat storage operation is generally performed for a long time at night, and the required compressor capacity is sufficiently small as compared with the cooling operation with a high daytime load. Therefore, it is relatively easy to ensure the heat storage amount of the two heat storage units by operating one heat source unit.

  The controller 4 selectively switches the compressor 7 or the like that is driven during the heat storage operation to that of the heat source unit 2a or 2b based on the accumulated operation time (and information such as the past number of operations). Thereby, the integrated operation time of the heat source units 2a and 2b is made uniform. Further, when one of the heat source units 2a and 2b fails, the other heat source unit is switched to operate and the operation is continued.

  In the present embodiment configured as described above, for example, when the compressor 7 or the like of the heat source unit 2a is driven during the heat storage operation and the compressor 7 or the like of the heat source unit 2b is stopped, the heat storage heat exchange of the heat storage unit 3a is performed. Although the gas-liquid two-phase refrigerant flowing out of the storage unit 22 and the gas-liquid two-phase refrigerant flowing out of the heat storage heat exchanger 22 of the heat storage unit 3a merge through the heat storage gas pipes 51a to 51c, the heat source in operation Only the suction side of the compressor 7 of the unit 2a is returned. Thereby, since the refrigerant in the gas-liquid two-phase state is not distributed to the heat source units 2a and 2b during the heat storage operation, it is possible to avoid the refrigerant shortage of the heat source unit that is likely to occur due to the distribution of the refrigerant in the gas-liquid two-phase state. Therefore, for example, problems such as poor lubrication in the compressor 7 can be avoided, and the reliability can be improved.

  Although not specifically described in the third embodiment, for example, the compressor 7 and the like of the heat source unit 2a and the compressor 7 and the like of the heat source unit 2b may have the same capacity. For example, the compressor 7 or the like of one heat source unit 2a may have a relatively large capacity while the compressor 7 or the like of the other heat source unit 2b may have a relatively small capacity. In that case, the controller 4 selects a heat source unit that operates during the heat storage operation depending on conditions such as when it is desired to perform the heat storage operation in a short time or when the outside air temperature is high and it is difficult to secure a predetermined heat storage amount. Also good. In this case, the same effect as described above can be obtained.

  Moreover, in the said 3rd Embodiment, it demonstrated as an example the case where the compressor 7 etc. which are driven at the time of heat storage operation were selectively switched to the one of the heat source units 2a and 2b. However, it is not limited to this. That is, for example, the compressor 7 or the like that is driven during the heat storage operation may be fixed to that of the heat source unit 2a. In such a modified example, as shown in FIG. 11, heat storage gas pipes 52a and 52b connected so that only the heat storage unit 2a corresponds to the heat storage units 3a and 3b may be provided. Also in this case, the gas-liquid two-phase refrigerant flowing out of the heat storage heat exchanger 22 of the heat storage unit 3a and the gas-liquid two-phase refrigerant flowing out of the heat storage heat exchanger 22 of the heat storage unit 3a during the heat storage operation are stored in the heat storage gas. Although they merge through the pipes 50a and 50b, they are returned only to the suction side of the compressor 7 of the operating heat source unit 2a. Therefore, a shortage of refrigerant in the heat source unit 2a can be avoided, and the reliability can be improved.

  In the third embodiment and the modified example, as in the second embodiment, the temperature sensor 29 is provided in the branch pipe 23c of the heat storage units 3a and 3b, and the controller 4 performs the temperature of the heat storage unit 3a during the heat storage operation. You may correct the opening degree of the thermal storage expansion valve 26 so that the detection temperature of the sensor 29 and the detection temperature of the temperature sensor 29 of the thermal storage unit 3b may become the same. In this case, overheating gasification on the outlet side of the heat storage heat exchanger 22 can be prevented.

  Moreover, in the said 3rd Embodiment and modification, the case where it applies to the structure provided with the two indoor units 1a and 1b, the two heat source units 2a and 2b, and the two heat storage units 3a and 3b. Although described as an example, the present invention is not limited to this. That is, for example, one or three or more indoor units may be provided. Further, for example, three or more heat source units may be provided. Moreover, for example, one or more heat storage units may be provided. In those cases, the same effect as described above can be obtained.

1a, 1b Indoor unit 2a, 2b Heat source unit 3a, 3b Heat storage unit 4 Controller (control means)
5 Indoor heat exchanger 6 Indoor expansion valve (solenoid valve)
7 Compressor 8 Outdoor heat exchanger 10 Outdoor expansion valve (solenoid valve)
11 Suction side gas piping 12 Discharge side gas piping 13a, 13b Three-way valve (switching valve, solenoid valve)
14 Gas piping 20 Liquid piping 22 Heat storage heat exchanger 24a On-off valve (first solenoid valve)
24b On-off valve (second solenoid valve)
24c On-off valve (third solenoid valve)
24d Open / close valve (solenoid valve)
25 Receiver tank 26 Thermal storage expansion valve 28 Refrigerant return piping 29 Temperature sensor (temperature detector)
30 Common gas piping 31a, 31b Indoor side branch gas piping 32a, 32b Outdoor side branch gas piping 40 Common liquid piping 41a, 41b Indoor side branch liquid piping 42a-42e Outdoor side branch liquid piping 50a, 50b Thermal storage gas piping (1st Thermal storage gas piping)
51a-51c Thermal storage gas piping (2nd thermal storage gas piping)
52a, 52b Thermal storage gas piping (third thermal storage gas piping)

Claims (8)

At least one indoor unit including an indoor heat exchanger for exchanging heat between the refrigerant and room air;
A compressor that compresses refrigerant and an outdoor heat exchanger that exchanges heat with outdoor air are connected in parallel to the indoor unit via a gas pipe and a liquid pipe so as to form one refrigeration cycle together with the indoor unit. A plurality of heat source units provided,
A plurality of or one heat storage unit including a heat storage heat exchanger connected between the indoor unit and the heat source unit to exchange heat between the refrigerant and the heat storage medium;
Control means for controlling the compressor and controlling a plurality of solenoid valves for selectively circulating the refrigerant to any one of the outdoor heat exchanger, the heat storage heat exchanger, and the indoor heat exchanger And
The control means controls the compressor and the plurality of solenoid valves, and at least a heat storage operation for operating the outdoor heat exchanger as a condenser and the heat storage heat exchanger as an evaporator, and the outdoor heat exchanger. In a regenerative air conditioner that switches to a regenerative cooling operation that operates as a condenser, the regenerator heat exchanger as a subcooler, and the indoor heat exchanger as an evaporator,
The gas-liquid two-phase refrigerant flowing out of the heat storage heat exchanger during the heat storage operation is supplied to the compressor in one corresponding heat source unit for each of the heat storage units. A regenerative air conditioner. The regenerative air conditioner according to claim 1,
The heat storage unit includes a plurality of units and the same number as the heat source unit,
Each of the plurality of heat storage units and one of the plurality of heat source units are connected so as to correspond to each other, and the gas-liquid two flowing out from the heat storage heat exchanger of each heat storage unit during the heat storage operation A heat storage type air conditioner comprising a plurality of first heat storage gas pipes that lead out the refrigerant in the phase state to the upstream side of the compressor of each of the corresponding heat source units. The regenerative air conditioner according to claim 2,
The heat storage unit is
An expansion valve that is provided at a position on the upstream side of the heat storage heat exchanger during the heat storage operation and depressurizes the refrigerant during the heat storage operation;
A temperature detector provided at a position on the downstream side of the heat storage heat exchanger during heat storage operation,
The control means includes
The regenerative air conditioning apparatus, wherein the opening degree of the expansion valve is corrected so that the refrigerant temperatures detected by the temperature detectors of all the heat storage units are the same during the heat storage operation. The regenerative air conditioner according to claim 1,
The control means includes
A heat storage type air conditioner characterized in that during the heat storage operation, the compressor in any one of the plurality of heat source units is driven and the compressor in the other heat source unit is stopped. apparatus. The regenerative air conditioner according to claim 4,
Each of the heat storage units is connected so that all the heat storage units correspond to each other, and the refrigerant in the gas-liquid two-phase state that flows out of the heat storage heat exchanger of the heat storage unit during the heat storage operation is compressed in the heat source unit. A second heat storage gas pipe leading to the upstream side of the machine,
The control means includes
The regenerative air conditioner characterized in that the compressor driven during the heat storage operation is selectively switched to one of the heat source units of the plurality of heat source units. The regenerative air conditioner according to claim 4,
A specific one of the heat storage units is connected to all of the heat storage units, and the refrigerant in a gas-liquid two-phase state that flows out of the heat storage heat exchanger in all of the heat storage units during the heat storage operation is A third heat storage gas pipe led out upstream of the compressor in one specific heat source unit;
The control means includes
The heat storage type air conditioner characterized in that the compressor driven during the heat storage operation is fixed to the one specific heat source unit. The regenerative air conditioner according to any one of claims 2, 3, 5, and 6,
The heat source unit is
The gas pipe from the indoor unit is connected to one of the suction side gas pipe and the discharge side gas pipe of the compressor, and the gas pipe from the heat exchanger is connected to the suction side gas pipe and the discharge side gas of the compressor. Comprising at least one switching valve for switching to communicate with the other of the pipes;
The control means includes
By controlling the plurality of solenoid valves including the compressor and the switching valve, the outdoor heat exchanger can be switched to a heating operation that operates as an evaporator and the indoor heat exchanger as a condenser,
The first, second, or third heat storage gas pipe is:
A regenerative air conditioner connected to a suction side gas pipe of the compressor. The regenerative air conditioner according to any one of claims 2, 3, 5 to 7,
The heat storage unit is
An expansion valve that is provided at a position on the upstream side of the heat storage heat exchanger during the heat storage operation and depressurizes the refrigerant during the heat storage operation;
A receiver tank provided at a position upstream of the expansion valve during heat storage operation;
A first solenoid valve for communicating / blocking between the heat source unit and the liquid pipe from the indoor unit and the receiver tank;
A second solenoid valve that communicates and blocks between the heat storage heat exchanger and the first, second, or third heat storage gas pipe;
A refrigerant return pipe connected between the receiver tank and the first, second, or third heat storage gas pipe;
A third solenoid valve for communicating / blocking the refrigerant return pipe,
The operation control means includes
During the heat storage operation, the first and second solenoid valves are opened, the third solenoid valve is closed, and the expansion valve is controlled to be in the throttled state. And a second electromagnetic valve is closed, the third electromagnetic valve is opened, and the expansion valve is fully closed.

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