JPH11270920A - Multifunctional heat pump system and method of its operation control - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a multifunctional heat pump system capable of performing a cooling and heating operation, a hot water supply operation, a heat storage operation, a cold heat storage operation and multifunctional operations thereof. SOLUTION: A refrigerating cycle is composed of a compressor 1, an outdoor heat exchanger 2, an indoor heat exchanger 3, a cold heat storage tank 4 and a hot water supply heat exchanger 5. The outlet piping of the compressor is divided into two directions. One pipeline is connected to a four-way valve 8 through an evaporation pressure regulating valve 9 and a sixth valve SV6 in parallel therewith via a first valve SV1, a four-way valve 8, the outdoor heat exchanger 2, a second valve SV2, regulating valves V1 and V2 and the indoor heat exchanger 3 to form a circuit 35. The other pipeline includes a circuit 36 combined with the second valve SV2 through a regulating valve V3 for the hot water supply heat exchanger via a fourth valve SV4 and the hot water supply heat exchanger 5, a circuit 37 combined with the second valve SV2 through a regulating valve V4 via a third valve SV3 and the cold heat storage tank 4 by branching from the upstream side of the fourth valve SV4 and a circuit 38 combined with an inlet side through a valve SV5 by branching from the downstream side of the third valve SV3. Thus, before the start of an operation mode in which the shortage of refrigerant is anticipated, the refrigerant is recovered to the heat exchanger of a condensation side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multifunctional heat pump system capable of independent operation of heating and cooling, hot water supply, heat storage, and cold storage, and an overlap operation thereof, and a method of controlling the operation thereof.

[0002]

2. Description of the Related Art In recent years, an increase in power consumption at the peak of summer power has hindered a stable supply of power and caused a rise in capital investment costs, and reduction of power consumption during peak times has become a social requirement. Conventionally, as a power load leveling measure, a cool storage / heat storage operation using a heat pump is performed at night and a cooling / heating load reduction using a cool storage / heat storage source is performed at a peak in the daytime. In addition, the hot water supply operation using nighttime electric power can be applied to a low-cost nighttime electric power rate system, and the running cost can be reduced.

Conventionally, an air conditioning system having a cold storage / heat storage function and a hot water supply system are often separate devices, and since separate heat sources are required, heat cannot be effectively used, and the entire device becomes larger. There was a problem of doing. Japanese Patent No. 2665310 discloses a system capable of performing operations such as cooling and heating, hot water supply, heat storage, and cold storage with one heat pump system.
And Japanese Patent Application Laid-Open No. 5-172436 are known. FIG. 18 shows a heat pump system disclosed in Japanese Patent No. 2665310. In FIG. 18, 4
0 is a heat pump, 41 is a cooling / heating heat exchanger, 42 is a hot water supply heat exchanger, 43 is a cooling / heating load, 44 is a load heat exchanger, 45 is a cold storage heat tank, 46 is a hot water storage tank, 47 is a bathtub, 48
Is a heat exchanger for heating, and SV1 to SV6 and P1 to
P4 is an electromagnetic valve and a pump provided in the refrigerant circuit, respectively. The system shown in FIG. 18 uses the heat medium that has exchanged heat with the heat pump 40 during the cooling / heating operation and the cold storage operation to pump P1,
This is a method of circulating at P2, and there is a problem that energy loss such as heat transfer loss and pump power loss occurs, and heat utilization efficiency is reduced. In addition, there is a restriction in performing combined operation, such as simultaneous operation of cooling and cold storage cannot be performed.

FIG. 19 shows a heat pump system disclosed in Japanese Patent Application Laid-Open No. 5-172436. In FIG. 19, 50a and 50b are compressors, 51 is an outdoor heat exchanger, 5
2 is an indoor heat exchanger, 53 is a cold storage heat tank, 54 is a hot water supply heat exchanger, 55a and 55b are oil separators, 56a and 56b are capillary tubes, 57a and 57b are inverters for controlling the capacity of the compressor, 58a and 58b. Is an accumulator, EV1 to EV3
Is an expansion valve, SV1 to SV9 are solenoid valves, and CV1 and CV2 are check valves. In the system of FIG. 19, simultaneous operation of cold storage (evaporation temperature of about 0 ° C. to about 30 ° C.) and cooling (evaporation temperature of about 10 ° C.) of greatly different evaporation temperatures, and heat storage (condensation temperature of about 5 ° C. to about (40 ° C.) and heating (condensing temperature of about 45 ° C.).
Although it is possible to operate by operating a and 50b, two or more compressors are required, and a somewhat complicated control such as equal oil return control to the two compressors is required.

[0005]

SUMMARY OF THE INVENTION The present invention has been made in order to solve the above-mentioned problems, and enables a single refrigeration cycle system to perform heating and cooling, hot water supply, heat storage, cold storage and their overlapping operation. It is an object of the present invention to provide a multifunctional heat pump system. Further, another object of the present invention is to use the multi-function heat pump system in the operation mode from another heat exchanger in which the refrigerant is accumulated in order to secure the amount of refrigerant and the refrigerating machine oil necessary for performing the operation mode. It is an object of the present invention to provide an operation control method of a multifunctional heat pump system that enables safe and reliable recovery of a refrigerant to a heat exchanger to be performed.

[0006]

In the present invention, the above-mentioned problems have been solved by constructing a multifunctional heat pump system as follows. (Claim 1) A refrigerant circuit comprising one compressor and connecting the compressor with an outdoor heat exchanger, an indoor heat exchanger, a cold storage heat tank and a hot water supply heat exchanger, each of which is a heat exchanger. By switching the flow of the refrigerant to the vessel, a refrigeration cycle that enables independent operation of cooling / heating, hot water supply, heat storage, and cold storage and a combined operation thereof is configured. (Claim 2) One refrigerator is connected to an outdoor heat exchanger, an indoor heat exchanger, a cold storage heat tank and a hot water supply heat exchanger to form a refrigeration cycle, and the compressor discharge side pipes are connected in two directions. After branching, one is provided with a sixth valve provided in parallel with the evaporating pressure regulating valve via a first valve, a switching valve, an outdoor heat exchanger, a second valve, a flow regulating valve, and an indoor heat exchanger. A refrigerant circuit connected to the switching valve via the switching valve, and further connected to the switching valve and a compressor suction side pipe, and a fourth valve, a hot water supply heat exchanger, and a flow control valve for an indoor heat exchanger. A refrigerant circuit joined to the second valve via a flow control valve for a hot water supply heat exchanger provided in parallel, a third valve branched from an upstream of the fourth valve and a cold storage tank Is connected to the second valve via a flow control valve for a regenerator provided in parallel with the flow control valve for the indoor heat exchanger. And medium circuit, a structure in which and a refrigerant suction circuit that is merged connected to the compressor intake piping via a fifth valve branches downstream of said third valve. (Claim 3) In the invention of claim 2, an outdoor unit,
A branch unit, an indoor unit, a regenerative heat storage tank, each unit of a hot water supply tank, including a hot water supply heat exchanger and at least a flow control valve in the branch unit, the outdoor unit, the indoor unit, the regenerative heat storage tank, It is configured to include a pipe portion connected to each of the hot water supply tanks. (Claim 4) In the invention of claim 2 or claim 3,
By providing a capillary tube and a seventh valve in parallel with the third valve provided in the refrigerant circuit on the cold storage heat tank side, heat storage and heating or heat storage and hot water supply can be operated simultaneously. .

[0007] Further, an operation control method for a multifunctional heat pump system according to the present invention solves the above-mentioned problem by being configured as follows. (Claim 5) In the operation method of the multifunctional heat pump system according to any one of claims 1 to 4, before starting a specific operation mode in which refrigerant shortage is expected, during a refrigerant recovery operation and after refrigerant recovery, a four-way valve or The refrigerant is recovered in the condensing-side heat exchanger used in the operation mode without switching the switching valve having the same function. (Claim 6) In the invention of claim 5, when recovering the refrigerant, the recovery operation is performed for a fixed time. (Claim 7) In the invention of claim 5, when recovering the refrigerant, the pressure sensor attached to the compressor suction side pipe performs the recovery operation until the pressure reaches a predetermined pressure.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 FIG. FIG. 1 is a circuit diagram showing the overall configuration of the multifunctional pump system of the present invention. The multifunctional pump system of the present invention includes an outdoor unit 13 including a compressor 1, an outdoor heat exchanger 2, a four-way valve 8, a first solenoid valve SV1, and connection terminals 15 to 18 of a refrigerant circuit, and a hot water supply heat exchanger. 5, connection terminals of second to sixth solenoid valves SV2 to SV6, first to fourth flow control valves V1 to V4, evaporation pressure control valve 9, water flow control valve 10, water pump 11, and refrigerant circuit 19-22 and 23-28, and connection end 2 of hot water supply circuit
A branch unit 14 including the branch units 9 and 30; an indoor unit (also referred to as an indoor heat exchanger) 3 connected to each of the connection ends 23 to 30 of the branch unit 14; a cold storage heat tank 4 and a hot water supply tank 6 Have been. 7 is a hot water tank 6
It is a hot water heater that heats the water inside.

The outdoor unit 13 has one compressor 1, and its discharge-side pipe is branched in two directions. One branch pipe from the branch part 31 is connected via the first solenoid valve SV 1 and the four-way valve 8. To the outdoor heat exchanger 2, the other branch pipe is connected to the connection end 18, and the connection end 15 is connected to the outdoor heat exchanger 2.
The other end of the compressor 1 is connected to a suction pipe of the compressor 1, and the connection end 16 is connected to the compressor 1 via a four-way valve 8.
The circuit configuration is connected to the suction side. In addition, 1
Reference numeral 2 denotes a pressure sensor provided in a suction pipe of the compressor 1.

The branch unit 14 has connection ends 19 to 2 connected to connection ends 15 to 18 of the outdoor unit 13, respectively.
2 and a connection end 19 connected to the connection end 15 is configured such that the first to fourth flow control valves V1 to V4 are connected in parallel at the second solenoid valve SV2 and the branch portion 32,
The second flow control valves V1 and V2 are connected to connection ends 23 and 2 respectively.
4 and the third flow control valve V3 is connected to the hot water supply heat exchanger 5
And the fourth flow control valve V4 is connected to the connection end 2
7 is connected to the other end of the hot water supply heat exchanger 5 via a fourth solenoid valve SV4, and the connection end 21 connected to the connection end 17 is connected to the fifth end. And the third solenoid valve SV3 is connected between the branch portion 34 and the branch portion 33 on the upstream side of the fourth solenoid valve SV4, while the solenoid valve SV5 is connected to the connection end 28 via the branch portion 34, The connection end 20 connected to the connection end 16 is connected to the connection end 2 via a sixth solenoid valve SV6 connected in parallel with the evaporation pressure regulating valve 9.
5 and a connection end 26, respectively, and connection ends 29 and 30
Have a circuit configuration connected to the piping of the hot water supply tank 6, respectively. The four connection ends 23 to 26 of the branch unit 14 are used here to connect the two indoor units 3 in parallel, and the connection ends 27 and 28 are connected to the cold storage heat tank 4. ing.

Therefore, in this multifunctional heat pump system, the compressor discharge side pipe is branched in two directions at the branch part 31, one of which is the first solenoid valve SV1, the four-way valve 8, the outdoor heat exchanger 2, the second Solenoid valve SV2, the first for indoor heat exchanger,
Through the second flow control valves V1, V2 and the indoor heat exchanger 3,
Sixth solenoid valve SV provided in parallel with evaporation pressure regulating valve 9
6, the indoor heat exchanger side refrigerant circuit 35 which is connected to the four-way valve 8 and further connects the four-way valve 8 to the compressor suction side pipe.
And the other via a fourth solenoid valve SV4 and a hot water supply heat exchanger 5, via a third flow control valve V3 for the hot water supply heat exchanger provided in parallel with the flow control valves V1 and V2 for the indoor heat exchanger. A hot water supply heat exchanger side refrigerant circuit 36 that is connected to the second solenoid valve SV2 at the branch portion 32; and a third solenoid valve SV3 that branches off (branch portion 33) from upstream of the fourth solenoid valve SV4. After passing through the cold storage heat tank 4, the flow rate regulating valves V1, V2 for the indoor heat exchanger
Flow control valve V4 for regenerative heat storage tank provided in parallel with
And the refrigerant circuit 37 connected to the second regenerative valve SV2 via the second solenoid valve SV2, and branches (branch 34) from the downstream of the third solenoid valve SV3 and is compressed via the fifth solenoid valve SV5. The refrigerant suction circuit 38 is connected to the machine suction side pipe.

By configuring the multifunctional heat pump system as described above, in addition to normal cooling / heating operation, cooling / cooling, radiation / heating, cold storage, heat storage, hot water supply, simultaneous cooling / hot water supply, simultaneous cold storage / cooling, Each operation such as simultaneous cold storage / hot water supply, simultaneous cold storage / cooling / hot water supply, and simultaneous hot water supply / heating can be performed. In addition, as described above, the branch circuit portion of the refrigerant, the hot water supply heat exchanger, the pump, and the like are housed in the branch unit 14 to form a single unit configuration. As shown in FIG. The multifunctional heat pump system of the present invention can be configured with little modification to the machine 3, the cold storage tank 4, and the hot water tank 6.

Table 1 shows the solenoid valves SV1 to SV1 for each operation mode.
SV6 shows the open / close state of the flow control valves V1 to V4. In the figures and tables, the valve described as the solenoid valve SV can be replaced with a valve having an opening / closing function, for example, a flow regulating valve.

[0014]

[Table 1]

Hereinafter, the specific flow of the refrigerant in each operation mode will be described with reference to FIGS. In each figure, the flow of the refrigerant is indicated by solid arrows.

(1) Cooling / cooling operation FIG. 2 is a diagram showing the flow of refrigerant during cooling / cooling operation. In this case, the third and sixth solenoid valves are opened, and the first, second,
The fourth and fifth solenoid valves are closed. Further, the first and second flow control valves are opened in a throttled state, the fourth flow control valve is fully opened, and the third flow control valve is closed. Evaporation pressure control valve 9
Is closed. The four-way valve 8 has a connection end 16 at the compressor 1.
In order to communicate with the refrigerant suction side. In the open / closed state of each of the above valves, the high-pressure refrigerant discharged from the compressor 1 passes through the third solenoid valve SV3 from the branch portion 31 through the connection ends 18 and 22, and further cools through the connection end 28. After entering the heat tank 4, in the cold storage heat tank 4, heat exchange is performed with ice produced by night power and condensed to become a liquid refrigerant.
7 through a fourth flow control valve (fully open) V4, and are throttled while being diverted by the first and second flow control valves V1 and V2, respectively.
After becoming a low-pressure two-phase refrigerant, it enters each indoor unit 3 from the connection ends 23 and 24, evaporates and becomes a gas refrigerant in each indoor unit 3,
Further, they are merged through the connection ends 25 and 26, respectively, and are sucked into the compressor 1 again through the sixth solenoid valve SV6, the connection ends 20 and 16, and the four-way valve 8. In addition, it is also possible to operate only one indoor unit by closing the first or second flow control valve.

In this refrigeration cycle, since the refrigerant is condensed by using ice or cold water in the cold storage heat tank 4, the cooling capacity is lower than that in the case of performing heat exchange with the outside air as in a normal cooling operation. , And efficient operation becomes possible. In addition, since cold storage is performed using inexpensive late-night power, running costs can be reduced and peak power during the day can be reduced. This operation mode is operated when the cold storage heat source is available and there is a cooling request from the user during the peak power hours during the daytime in summer.

(2) Radiation and heating operation FIG. 3 is a diagram showing the flow of refrigerant during the radiation and heating operation. In this case, the first, fifth and sixth solenoid valves are opened and the second and fifth solenoid valves are opened.
The third and fourth solenoid valves are closed. Further, the first and second flow control valves are opened in a throttled state, the fourth flow control valve is fully opened, and the third flow control valve is closed. The evaporation pressure regulating valve 9 is also closed. The four-way valve 8 is switched so that the connection end 16 communicates with the refrigerant discharge side of the compressor 1. In the open / closed state of each of the above valves, the high-pressure refrigerant discharged from the compressor 1 passes through the first solenoid valve SV 1, the four-way valve 8, and the connection terminals 16 and 20 from the branch portion 31 to the sixth solenoid valve. After passing through the SV 6, each of the indoor units 3 enters the indoor unit 3 from the connection end 25, 26, exchanges heat in each indoor unit 3, condenses into a liquid refrigerant, and then flows through the connection end 23, 24 to the first and second flow rates. Regulating valve V1,
The refrigerant is throttled at V2, becomes a low-pressure two-phase refrigerant, passes through a fourth flow control valve (fully opened) V4, enters the cold storage heat tank 4 from the connection end 27, exchanges heat with high-temperature hot water in the cold storage heat tank 4, and evaporates. It becomes a gas refrigerant, the connection end 28, the fifth solenoid valve SV5, the connection end 2
The refrigerant is sucked into the compressor 1 again via the compressors 1 and 17. In this case, it is also possible to operate one indoor unit by closing the first or second flow control valve.

In this refrigeration cycle, the refrigerant is evaporated using hot water in the cold storage heat tank 4, so that the heating capacity is improved as compared with a case where heat exchange is performed with the outside air as in a normal heating operation. In addition, efficient operation becomes possible, and the rise of the heating capacity is quickened. In addition, since heat is stored using inexpensive late-night power, peak heating power during the day can be cut. This operation mode is operated when the hot water heat source of the cold storage heat tank can be used in winter and there is a heating request from the user.

(3) Simultaneous Cooling / Hot Water Supply Operation FIG. 4 is a diagram showing the flow of refrigerant during simultaneous cooling / hot water supply operation. In this case, the fourth and sixth solenoid valves are opened, and the first and second solenoid valves are opened.
The second, third, and fifth solenoid valves are closed. First,
The second flow control valve is opened to the throttle state, the third flow control valve is fully opened, and the fourth flow control valve is closed. The evaporation pressure regulating valve 9 is also closed. The four-way valve 8 is switched so that the connection end 16 communicates with the refrigerant suction side of the compressor 1. In the open / closed state of each of the above valves, the high-pressure refrigerant discharged from the compressor 1 enters the hot water supply heat exchanger 5 from the branch portion 31 through the connection ends 18 and 22 and the fourth solenoid valve SV4. After the heat exchange with the water in the hot water supply tank 6 in the hot water supply heat exchanger 4, the refrigerant is condensed to become a liquid refrigerant, and then the first and second flow rates are respectively adjusted through the third flow rate control valve (fully opened) V3. After being shunted while being diverted by the valves V1 and V2, the refrigerant becomes a low-pressure two-phase refrigerant, enters the indoor units 3 from the connection terminals 23 and 24, evaporates and becomes a gas refrigerant in each indoor unit 3, and becomes a gas refrigerant. 25
Through the sixth solenoid valve SV6, the connection ends 20, 16 and the four-way valve 8 to be sucked into the compressor 1 again. The flow of water in the hot water supply tank 6 is controlled by the water pump 11.
Of the hot water supply heat exchanger 5 through the connection end 29 from the lower part of the hot water supply, and further circulates from the connection end 30 to the upper part of the hot water supply tank 6.

In this refrigeration cycle, hot water can be supplied using waste heat discarded to the outside air during normal cooling operation, so that simultaneous cooling and hot water supply can be performed economically. This operation mode is operated when the amount of hot water in the hot water supply tank decreases in summer and there is a cooling request from the user.

(4) Simultaneous operation of cold storage and cooling FIG. 5 is a diagram showing the flow of refrigerant during simultaneous operation of cold storage and cooling. In this case, the first, second and fifth solenoid valves are opened,
The third, fourth, and sixth solenoid valves are closed. First,
The second and fourth flow control valves are opened in a throttled state, and the third flow control valve is closed. The evaporation pressure regulating valve 9 is kept open.
The four-way valve 8 is switched so that the connection end 16 communicates with the refrigerant suction side of the compressor 1. In the open / closed state of each of the above valves, the high-pressure refrigerant discharged from the compressor 1 passes through the first solenoid valve SV1 and the four-way valve 8 from the branch portion 31 and exchanges heat with the outside air in the outdoor unit 2. After being condensed to become a liquid refrigerant, the refrigerant is branched to the indoor unit 3 side and the cold storage heat tank 4 side at the branch part 32 through the connection ends 15 and 19 and the second solenoid valve SV2. Each of the first and second flow control valves V1 and V2 is throttled by the first and second flow control valves V1 and V2 to form a low-pressure two-phase refrigerant. , From the connection terminals 24 and 25, the evaporation pressure regulating valve 9,
It returns to the compressor 1 via the connection ends 20, 16 and the four-way valve 8.
On the other hand, the cold storage heat tank 4 side is throttled by the fourth flow control valve V4 to become a low-pressure two-phase refrigerant, enters the cold storage heat tank 4 from the connection end 27, exchanges heat with water or ice in the cold storage heat tank 4, and evaporates. , And is sucked into the compressor 1 from the connection end 28 via the fifth solenoid valve SV5 and the connection ends 21 and 17.

In the cold storage / cooling simultaneous operation, a difference in evaporation pressure is generated between the cold storage heat tank 4 for evaporating the refrigerant and the indoor unit 3, and a large amount of refrigerant flows into the cold storage heat tank 4 having a low evaporation pressure. Therefore, since the capacity of the indoor unit 3 may not be achieved, the evaporation pressure adjusting valve 9 is provided on the indoor unit 3 side to adjust the evaporation pressure on the indoor unit 3 side. Here, the evaporation pressure adjustment valve has a pressure adjustment spring and a pressure control valve inside, and the pressure control valve operates so as to always balance the inlet side pressure and the repulsive force of the spring,
This is a valve that keeps the inlet pressure constant.

In this operation mode, operation is performed when there is a cooling request from a user during cold storage at night, and simultaneous operation of cooling and cold storage is possible, so that a stable amount of cold storage can be ensured. Becomes

(5) Simultaneous operation of cold storage and hot water supply FIG. 6 is a diagram showing the flow of refrigerant during simultaneous operation of cold storage and hot water supply. In this case, the fourth and fifth solenoid valves are opened, and the first and fifth solenoid valves are opened.
The second, third, and sixth solenoid valves are closed. First,
The second flow control valve is closed, the third flow control valve is fully opened, and the fourth flow control valve is open in a throttled state. The evaporation pressure regulating valve 9 is closed. The four-way valve 8 may be switched in either direction. When the valves are in the open / closed state, the high-pressure refrigerant discharged from the compressor 1
1 through the connection terminals 18 and 22 and the fourth solenoid valve SV4, enters the hot water supply heat exchanger 5, and performs heat exchange with the water in the hot water supply tank 6 in the hot water supply heat exchanger 5 to condense the liquid refrigerant. After that, through the third flow control valve (fully open) V3, the fourth
After being throttled by the flow control valve V4 to become a low-pressure two-phase refrigerant, enters the cold storage heat tank 4 from the connection end 27, evaporates and becomes a gas refrigerant in the cold storage heat tank 4, and the fifth electromagnetic wave from the connection end 28. Valve S
V5, and is sucked into the compressor 1 via the connection ends 21 and 17.
The flow of water in the hot water supply tank 6 enters the hot water supply heat exchanger 5 from the lower part of the hot water supply tank 6 through the connection end 29 by the water pump 11, and is further circulated from the connection end 30 to the upper part of the hot water supply tank 6. I have.

In this refrigeration cycle, a hot water supply operation that effectively utilizes waste heat discarded to the outside air in a normal cold storage operation can be performed, and economical simultaneous operation of cold storage and hot water supply can be realized. In addition, since nighttime power can be used, running costs can be reduced. This operation mode is operated during the summer night when the cold storage heat tank 4 has no ice and the cold storage operation needs to be performed, and the amount of hot water in the hot water storage tank 6 is insufficient.

(6) Simultaneous operation of cold storage / cooling / hot water supply FIG. 7 is a diagram showing the flow of refrigerant during simultaneous operation of cold storage / cooling / hot water supply. In this case, open the fourth and fifth solenoid valves,
The first, second, third, and sixth solenoid valves are closed. Also,
The first, second, and fourth flow control valves are opened in the throttle state, and the third
The flow control valve of is fully opened. The evaporation pressure regulating valve 9 is kept open. The four-way valve 8 is switched so that the connection end 16 communicates with the suction side of the compressor 1. In the open / closed state of each of the above valves, the high-pressure refrigerant discharged from the compressor 1 is:
The fourth solenoid valve S from the branch portion 31 through the connection ends 18 and 22
After passing through V4, it enters the hot water supply heat exchanger 5, where it exchanges heat with the water in the hot water supply tank 6 in the hot water supply heat exchanger 5 to be condensed into a liquid refrigerant, and then through the third flow control valve V3. The indoor unit 3 is branched to the side of the indoor unit 3 and the side of the cold storage heat tank 4, and the indoor unit 3 side is throttled by the first and second flow control valves V1 and V2 to become low-pressure two-phase refrigerant. Machine 3
Then, each indoor unit 3 exchanges heat with the outside air and evaporates to become a gas refrigerant, and returns to the compressor 1 from the connection ends 25 and 26 via the evaporation pressure regulating valve 9, the connection ends 20, 16 and the four-way valve 8. On the other hand, the cold storage heat tank 4 side is throttled by the fourth flow control valve V4 to become a low-pressure two-phase refrigerant, and enters the cold storage heat tank 4 from the connection end 27.
The heat exchange with water or ice in the cold storage heat tank 4 evaporates and turns into a gaseous refrigerant. From the connection end 28, the fifth solenoid valve SV5 and the connection end 2
The refrigerant is sucked into the compressor 1 through the compressors 1 and 17. In the simultaneous operation of cold storage / cooling / hot water supply, a difference in evaporation pressure is generated between the cold storage heat tank 4 for evaporating the refrigerant and the indoor unit 3, and a large amount of refrigerant is present on the cold storage heat tank 4 having a low evaporation pressure. Since the flow may flow and the capacity on the indoor unit 3 side may not be exhibited, the evaporation pressure adjusting valve 9 is provided on the indoor unit 3 side to adjust the evaporation pressure on the indoor unit 3 side.

In this refrigeration cycle, cooling and hot water supply can be performed at the same time while cold storage and hot water supply are performed at night when the electricity rate is low. Therefore, stable cold storage and hot water supply can be ensured, and hot water supply by cooling and exhaustion of cold storage can be operated simultaneously. It is possible and economical. This operation mode is operated during the summer night when there is no ice in the cold storage tank 4 and it is necessary to perform the cold storage operation, and when the amount of hot water in the hot water storage tank 6 is insufficient and there is a cooling request from the user.

(7) Simultaneous operation of hot water supply and heating FIG. 8 is a diagram showing the flow of refrigerant during simultaneous operation of hot water supply and heating. In this case, the first, second, fourth, and sixth solenoid valves are opened, and the third and fifth solenoid valves are closed. First,
The second and third flow control valves are opened in a throttled state, and the fourth flow control valve is closed. The evaporation pressure regulating valve 9 is also closed.
The four-way valve 8 is switched so that the connection end 16 communicates with the suction side of the compressor 1. When the valves are in the open / closed state, the high-pressure refrigerant discharged from the compressor 1 flows into the branch portion 31.
, And the hot water supply heat exchanger 5 side is connected to the connection end 1.
After passing through the fourth solenoid valve SV4 via the heaters 8 and 22, the heat exchanger 5 performs heat exchange with water in the hot water supply tank 6 to condense into a liquid refrigerant, and then the third flow control valve V3 , And becomes a low-pressure two-phase refrigerant.
Through the sixth solenoid valve SV6 through the solenoid valve SV1, the four-way valve 8, and the connection terminals 16 and 20, and enters each indoor unit 3 from the connection terminals 25 and 26, and performs heat exchange at each indoor unit 3 to condense. After being turned into a liquid refrigerant, the refrigerant is throttled by the first and second flow control valves V1 and V2 via the connection ends 23 and 24, respectively, to become a low-pressure two-phase refrigerant. The two low-pressure two-phase refrigerants merge at the branch portion 32, exchange heat with the outside air in the outdoor heat exchanger 2 via the second solenoid valve SV2 and the connection ends 19 and 15, evaporate, become a gas refrigerant, and become a four-way valve. After that, it is sucked into the compressor 1.

In this operation mode, the operation is performed when the amount of hot water in the hot water supply tank 6 is insufficient at night and a heating request is made by a user, and simultaneous operation of heating and hot water supply is possible. Highly efficient hot water supply is possible.

In the multifunctional heat pump system as shown in FIG. 1, the refrigerant in the refrigerant circuit depends on the temperature of the indoor / outdoor air and the stop time, and the compressor 1, the outdoor heat exchanger 2, the indoor unit 3, the cold storage tank 4, the hot water supply Since the refrigerant is dispersed and accumulated in the heat exchanger 5 together with the refrigerating machine oil, a shortage of the refrigerant or the refrigerating machine oil to the compressor 1 occurs during the operation in each operation mode, and the heating or the normal operation of the compressor becomes impossible. Inconveniences such as becoming inconsistent may occur.

According to the present invention, when the operation is started, the refrigerant is recovered to the condenser-side heat exchanger used in the operation mode, and the refrigerant amount and the refrigerating machine oil required for the operation mode are secured. This enables normal operation. Table 2 shows the solenoid valves SV1 to SV6 and the flow control valve V1 during the refrigerant recovery operation.
To V4.

[0033]

[Table 2]

When the refrigerant is recovered and the operation is continued thereafter, if the four-way valve 8 is inverted after the recovery of the refrigerant, the high and low pressures are suddenly balanced, so that a loud noise is generated or the high-pressure liquid is generated. There is a danger that the refrigerant will suddenly return to the compressor 1 and damage the compressor. Therefore, in the present invention, the above-described phenomenon is prevented by recovering the refrigerant without switching the four-way valve 8 in the refrigerant recovery and the subsequent operation, and the refrigerant recovery is performed by the heat exchange used in the operation mode. Therefore, the operation following the refrigerant recovery can be smoothly and continuously performed.

The operation time of the refrigerant recovery is a certain time after the start of the compressor operation, for example, one minute, or until the pressure sensor 12 attached to the compressor suction pipe reaches a certain pressure value.
For example, until it reaches 0 kgf / cm ² · G. In addition, the refrigerant recovery operation is not performed under all conditions, and the temperature of the heat exchanger that is not required for the operation is required from the information of the temperature sensor (not shown) attached to each heat exchanger. This is performed when the temperature is lower than the temperature of the heat exchanger to be performed. In the case where the refrigerant recovery is performed in other operation modes not described in Table 2, the recovery operation is performed to the condenser-side heat exchanger without switching the four-way valve 8 in the same manner.

The configuration of the cycle circuit during each refrigerant recovery operation will be described below with reference to FIGS.

(1) Refrigerant recovery operation before cooling operation FIG. 9 shows a circuit configuration at the time of refrigerant recovery operation before starting the cooling operation. FIG. 9 shows a circuit configuration in which the refrigerant is recovered in the outdoor heat exchanger 2 serving as a high-pressure condenser during the cooling operation. In this case, the second, third and fourth solenoid valves are closed and the first,
The fifth and sixth solenoid valves are kept open. Also, the first, second,
The third flow control valve is opened and the fourth flow control valve is closed. By operating the compressor 1, the refrigerant accumulated in the cold storage heat tank 4 is sucked into the compressor 1 via the fifth solenoid valve SV5 because the fourth flow control valve V4 is closed. Is done. In addition, since the fourth solenoid valve SV4 is closed, the refrigerant accumulated in the hot water supply heat exchanger 5 switches the third flow control valve V3 and the first flow control valve V1 or the second flow control valve V2. Via the indoor heat exchanger 3 via
Is sucked into the compressor 1 through the solenoid valve SV5 and the four-way valve 8. At this time, the refrigerant accumulated in the indoor heat exchanger 3 is also sucked at the same time. The refrigerant thus sucked into the compressor 1 is recovered by storing the outlet side in the outdoor heat exchanger 2 closed by the second solenoid valve SV2.

In this refrigerant recovery method, the refrigerant can be recovered and the cooling operation mode can be performed without switching the four-way valve 8 during and after the recovery, so that the generation of noise due to the inversion of the four-way valve 8 can be prevented, and the compressor 1 It is possible to prevent a compressor failure due to a sudden return of the liquid refrigerant to the compressor.

(2) Refrigerant Recovery Operation Before Heating Operation FIG. 10 shows a circuit configuration during the refrigerant recovery operation before the heating operation is started. FIG. 10 shows a circuit configuration for recovering the refrigerant in the indoor heat exchanger 3 that becomes a high-pressure condenser during the heating operation. In this case, the third and fourth solenoid valves are closed and the first and fourth solenoid valves are closed.
The second, fifth, and sixth solenoid valves are kept open. The third flow control valve is opened, and the first, second, and fourth flow control valves are closed. By operating the compressor 1, the cold storage heat tank 4
The refrigerant accumulated in the compressor 1 passes through the fifth solenoid valve SV5 because the fourth flow control valve V4 is closed.
Inhaled to. In addition, the refrigerant accumulated in the hot water supply heat exchanger 5 has the third solenoid valve SV4 closed, so that the third
Through the outdoor heat exchanger 2 and the four-way valve 8 via the flow control valve V3 and the second solenoid valve SV2. At this time, the refrigerant accumulated in the outdoor heat exchanger 2 is also sucked at the same time. The refrigerant thus sucked into the compressor 1 is recovered by storing the outlet side in the indoor heat exchanger 3 closed by the first flow control valve V1 and the second flow control valve V2.

In this refrigerant recovery method, since the refrigerant can be recovered and the heating operation mode can be performed without switching the four-way valve 8 during and after the recovery, the generation of the sound accompanying the inversion of the four-way valve 8 can be prevented, It is possible to prevent a compressor failure due to a sudden return of the liquid refrigerant to 1. In addition, since the high-temperature refrigerant discharged from the compressor 1 is stored in the indoor heat exchanger 3, the temperature of the indoor heat exchanger 3 rises, so that the heating operation after the completion of the refrigerant recovery is quickly started.

(3) Refrigerant Recovery Operation Before Simultaneous Cooling / Hot Water Supply Operation FIG. 11 shows a circuit configuration at the time of refrigerant recovery operation before starting simultaneous cooling / hot water supply operation. FIG. 11 shows a circuit configuration for recovering the refrigerant in the hot water supply heat exchanger 5 which becomes a high-pressure condenser during the simultaneous cooling and hot water supply operation. In this case, the first and third solenoid valves are closed, and the second, fourth, fifth, and sixth solenoid valves are opened. In addition, the first and second flow control valves are opened, and the third and fourth flow control valves are closed. By operating the compressor 1, the refrigerant accumulated in the cold storage heat tank 4 loses the fifth solenoid valve SV5 because the fourth flow control valve V4 is closed.
And is sucked into the compressor 1 through the compressor. Further, since the first solenoid valve SV1 is closed, the refrigerant accumulated in the outdoor heat exchanger 2 passes through the second solenoid valve SV2 and the first flow control valve V1 and the second flow control. It is sucked into the compressor 1 through the valve V2, the indoor heat exchanger 3, the sixth solenoid valve SV6, and the four-way valve 8. At this time, the refrigerant accumulated in the indoor heat exchanger 3 is also sucked at the same time. The refrigerant thus sucked into the compressor 1 is recovered by storing the outlet side in the hot water supply heat exchanger 5 closed by the third flow control valve V3.

In this refrigerant recovery method, since the refrigerant can be recovered and the cooling / hot water supply simultaneous operation mode can be performed without switching the four-way valve 8 during and after the recovery, the generation of the sound accompanying the reversal of the four-way valve 8 can be prevented. In addition, it is possible to prevent compressor failure due to sudden return of the liquid refrigerant to the compressor 1. Also,
By storing the high-temperature refrigerant discharged from the compressor 1 in the hot-water supply heat exchanger 5, the temperature of the hot-water supply heat exchanger 5 rises, so that the rise of the hot-water supply operation after the completion of the refrigerant recovery is accelerated.

(4) Refrigerant Recovery Operation Before Heat Storage Operation FIG. 12 shows a circuit configuration during the refrigerant recovery operation before the start of the heat storage operation. FIG. 12 shows a circuit configuration in which the refrigerant is recovered in the cold storage heat tank 4 serving as a high-pressure condenser during the heat storage operation. In this case, the first, fourth and fifth solenoid valves are closed, and the second, fourth and fifth solenoid valves are closed.
The third and sixth solenoid valves are kept open. Also, the first, second,
The third flow control valve is open and the fourth flow control valve is closed. By operating the compressor 1, the refrigerant accumulated in the hot water supply heat exchanger 5 receives the third flow rate control valve V3 and the second solenoid valve SV because the fourth solenoid valve SV4 is closed.
2. The air is sucked into the compressor 1 through the outdoor heat exchanger 2 and the four-way valve 8. Further, since the first solenoid valve SV1 is closed, the refrigerant accumulated in the indoor heat exchanger 3 passes through the first flow control valve V1 and the second flow control valve V2, and passes through the second solenoid valve SV2. At the branch portion 32 before the cooling water, the refrigerant is collected by the hot water supply heat exchanger 5 and merged into the compressor 1. At this time, the refrigerant accumulated in the outdoor heat exchanger 2 is also sucked at the same time. The refrigerant thus sucked into the compressor 1 is recovered by storing the outlet side in the cold storage tank 4 closed by the fourth flow control valve V4.

In this refrigerant recovery method, since the refrigerant can be recovered and the heat storage operation mode can be performed without switching the four-way valve 8 during and after the recovery, the generation of the sound accompanying the reversal of the four-way valve 8 can be prevented, It is possible to prevent a compressor failure due to a sudden return of the liquid refrigerant to 1. In addition, cold storage heat tank 4
The high-temperature refrigerant discharged from the compressor 1 is stored in the tank, so that the temperature of the cold storage heat tank 4 rises.

(5) Refrigerant Recovery Operation Before Hot Water Supply Operation FIG. 13 shows a circuit configuration during the refrigerant recovery operation before the start of the hot water supply operation. FIG. 13 shows a circuit configuration for recovering the refrigerant in the hot water supply heat exchanger 5 which becomes a high-pressure condenser during the hot water supply operation. In this case, the first and third solenoid valves are closed, and the second and third solenoid valves are closed.
The fourth, fifth, and sixth solenoid valves are kept open. First,
The second flow control valve is opened, and the third and fourth flow control valves are closed. By operating the compressor 1, the cold storage heat tank 4
The refrigerant accumulated in the compressor 1 is sucked into the compressor 1 via the fifth solenoid valve SV5 because the fourth flow control valve V4 is closed. Further, the refrigerant accumulated in the outdoor heat exchanger 2 is drawn into the compressor 1 through the four-way valve 8 because the first solenoid valve SV1 is closed. At this time, the refrigerant accumulated in the indoor heat exchanger 3 also passes through the first flow control valve V1 and the second flow control valve V2, and simultaneously passes through the second solenoid valve SV2, the outdoor heat exchanger 2, and the four-way valve 8. It is sucked. The refrigerant thus sucked into the compressor 1 is recovered by storing the outlet side in the hot water supply heat exchanger 5 closed by the third flow control valve V3.

In this refrigerant recovery method, since the refrigerant can be recovered and the hot water supply operation mode can be performed without switching the four-way valve 8 during and after the recovery, the generation of the sound accompanying the inversion of the four-way valve 8 can be prevented, It is possible to prevent a compressor failure due to a sudden return of the liquid refrigerant to 1. In addition, since the temperature of the hot water supply heat exchanger 5 is increased by storing the high-temperature refrigerant discharged from the compressor 1 in the hot water supply heat exchanger 5, the rise of the hot water supply operation after the completion of the refrigerant recovery is accelerated.

(6) Refrigerant Recovery Operation Before Simultaneous Hot Water Supply / Heating Operation FIG. 14 shows a circuit configuration during the refrigerant recovery operation before the simultaneous hot water supply / heating operation starts. FIG. 14 shows an indoor heat exchanger 3 and a hot water supply heat exchanger 5 which become high-pressure condensers during simultaneous operation of hot water supply and heating.
It has a circuit configuration for recovering refrigerant. In this case, the third solenoid valve is closed, and the first, second, fourth, fifth, and sixth solenoid valves are opened. In addition, the first to fourth flow control valves are all closed. By operating the compressor 1, the refrigerant accumulated in the cold storage heat tank 4 is sucked into the compressor 1 via the fifth solenoid valve SV5 because the fourth flow control valve V4 is closed. . The refrigerant accumulated in the outdoor heat exchanger 2 is supplied to the first to fourth flow control valves V1 to V
Since 4 is closed, it is sucked into the compressor 1 through the four-way valve 8. The refrigerant sucked into the compressor 1 in this manner is connected to the indoor heat exchanger 3 whose outlet side is closed by the first flow control valve V1 and the second flow control valve V2, and to the third side by the outlet side. The hot water is collected in the hot water supply heat exchanger 5 closed by the flow control valve V3.

In this refrigerant recovery method, since the refrigerant can be recovered and the hot water supply / heating simultaneous operation mode can be performed without switching the four-way valve 8 during and after the recovery, the generation of the sound accompanying the reversal of the four-way valve 8 can be prevented. In addition, it is possible to prevent compressor failure due to sudden return of the liquid refrigerant to the compressor 1. Also,
By storing the high-temperature refrigerant discharged from the compressor 1 in the indoor heat exchanger 3 and the hot water supply heat exchanger 5, the indoor heat exchanger 3,
Since the temperature of the hot water supply heat exchanger 5 rises, the start-up of the simultaneous heating and hot water supply operation after the completion of the refrigerant recovery is accelerated.

Embodiment 2 FIGS. 15 and 16 show the capillary tube 39 and the seventh solenoid valve in parallel with the third solenoid valve SV3 of the multifunctional heat pump system according to the first embodiment.
FIG. 3 is a circuit configuration diagram of a multifunctional heat pump system that enables simultaneous operation of heat storage and heating, and simultaneous operation of heat storage and hot water supply by adding an electromagnetic valve SV7.

In the circuit configuration of the first embodiment, it is difficult to perform an operation in which the condensing temperatures differ greatly, such as simultaneous storage and heating, and simultaneous storage and supply of hot water. By providing 39, even when the water temperature in the cold storage heat tank 4 is low and the condensing pressure is low, simultaneous operation with hot water supply and heating with a higher condensing temperature becomes possible. In addition, the capillary tube 3
The ninth and seventh solenoid valves SV7 can be replaced with another throttle mechanism such as a flow control valve.

FIG. 15 is a diagram showing the flow of the refrigerant during the simultaneous operation of heat storage and heating. In this case, the first, second, sixth,
The seventh solenoid valve is opened, and the third, fourth, and fifth solenoid valves are closed. Further, the first, second, and fourth flow control valves are opened in a throttled state, and the third flow control valve is closed. The evaporation pressure regulating valve 9 is also closed. Further, the four-way valve 8 is switched so that the connection end 16 communicates with the discharge side of the compressor 1. The high-pressure refrigerant discharged from the compressor 1 is branched in two directions at a branch portion 31, and the cold storage heat tank side 4 is depressurized through the capillary tube 39, passes through the seventh solenoid valve SV 7, and is cooled.
After performing heat exchange with water to condense into a liquid refrigerant, it is throttled by a fourth flow control valve V4 to become a low-pressure two-phase refrigerant, and the other indoor unit 3 side receives the first electromagnetic wave. Valve SV1,
After passing through the four-way valve 8 and the sixth solenoid valve SV6 and exchanging heat in the indoor unit 3 to condense into a liquid refrigerant, it is throttled by the first and second flow control valves V1 and V2 and the low-pressure valve It becomes a phase refrigerant.
Then, both low-pressure two-phase refrigerants join at the branch portion 32,
The heat is exchanged with the outside air in the outdoor heat exchanger 2 via the second solenoid valve SV2 to evaporate and become a gas refrigerant.
Inhaled to.

In this refrigeration cycle, the condensing pressure is low because the water temperature of the regenerator 4 is low, and the difference between the condensing pressure on the heating side and the condensing pressure on the regenerative tank is large. A capillary tube 39 is provided at the inlet on the cold storage heat tank side, and simultaneous operation of heat storage and heating can be performed by lowering the condensing pressure from that on the heating side. In this operation mode, operation is performed when the water temperature of the regenerative heat storage tank is low at night and there is a heating request from the user, and simultaneous operation of heating and heat storage is possible. Can be secured.

FIG. 16 is a diagram showing the flow of the refrigerant during the simultaneous operation of heat storage and hot water supply. In this case, the second, fourth, and seventh solenoid valves are opened, and the first, third, fifth, and sixth solenoid valves are closed. In addition, the third and fourth flow control valves are opened in a throttle state, and the first and second flow control valves are closed. The evaporation pressure regulating valve 9 is also closed. The four-way valve 8 is connected to the outdoor heat exchanger 2.
Is connected to the suction side of the compressor 1.
The high-pressure refrigerant discharged from the compressor 1 is branched in two directions at a branch part 31, and the cold storage heat tank 4 side has a capillary tube 3.
9, passes through the seventh solenoid valve SV7, exchanges heat with water in the cold storage tank 4, condenses into liquid refrigerant, and is then throttled by the fourth flow control valve V4. The second hot-water supply heat exchanger 5 passes through the fourth solenoid valve SV4 and exchanges heat in the hot-water supply heat exchanger 5 to be condensed into a liquid refrigerant. Is throttled by the flow control valve V3 to become a low-pressure two-phase refrigerant. Then, the two low-pressure two-phase refrigerants join at the branch part 32, exchange heat with the outside air at the outdoor heat exchanger 2 via the second solenoid valve SV2, evaporate and become gaseous refrigerant, and the compressor 1 via the four-way valve 8 Inhaled to.

In this refrigeration cycle, the condensing pressure is lowered because the water temperature of the regenerator 4 is low, and the difference between the condensing pressure on the hot water supply side and the condensing pressure on the regenerative heat tank is large. A capillary tube 39 is provided at the inlet on the heat tank side, and the condensing pressure is made lower than that on the hot water supply side, thereby enabling simultaneous operation of heat storage and hot water supply. In this operation mode, operation is performed at night when the water temperature of the regenerative heat storage tank is low and the amount of hot water in the hot water supply tank is small, and simultaneous operation of hot water supply and heat storage is possible. It becomes possible.

[0055]

Since the present invention is configured as described above, it has the following effects.

With one refrigeration cycle system, it is possible to realize a multifunctional heat pump system having high heat utilization efficiency, which enables cooling / heating, hot water supply, heat storage, cold storage, and overlapping operation thereof.

Conventionally, an outdoor unit, an indoor unit, a cold storage tank, a hot water supply tank, and a branching unit (a unit having a pipe branching portion such as a hot water supply heat exchanger, a flow control valve, and a valve) are provided for each unit. Outdoor units, indoor units,
This makes it possible to configure a system that minimizes the need for modification to cold storage tanks and hot water supply tanks, and enables the construction of a multifunctional heat pump system at low cost.

By providing a capillary tube and a seventh valve in parallel with the third valve on the inlet side of the cold storage tank, even when the water temperature in the cold storage tank is low and the condensation pressure is low, Simultaneous operation with hot water supply and heating with a higher condensing temperature becomes possible.

At the start of the operation, the refrigerant is recovered to the heat exchanger used in the operation mode by the refrigerant recovery operation, and the refrigerant amount and the refrigerating machine oil required for the operation mode can be secured. Driving becomes possible.

By recovering the refrigerant without switching the four-way valve in the refrigerant recovery and the subsequent operation, the generation of the sound accompanying the inversion of the four-way valve is prevented, and the compressor failure due to the sudden return of the liquid refrigerant to the compressor is prevented. Can be prevented,
Further, since the refrigerant recovery is performed to the condensing heat exchanger used in the operation mode, the start-up of the operation following the refrigerant recovery can be smoothly and continuously performed.

[Brief description of the drawings]

FIG. 1 is a circuit configuration diagram of a multifunctional heat pump system according to a first embodiment of the present invention.

FIG. 2 is a configuration diagram of a refrigeration cycle circuit during a cooling / cooling operation of the multifunctional heat pump system according to Embodiment 1 of the present invention.

FIG. 3 is a refrigeration cycle circuit configuration diagram of the multifunctional heat pump system according to Embodiment 1 of the present invention during a heat radiation and heating operation.

FIG. 4 is a refrigeration cycle circuit configuration diagram of the multifunctional heat pump system according to the first embodiment of the present invention during simultaneous cooling and hot water supply operation.

FIG. 5 is a refrigeration cycle circuit configuration diagram of the multifunctional heat pump system according to Embodiment 1 of the present invention at the time of simultaneous cold storage / cooling operation.

FIG. 6 is a refrigeration cycle circuit configuration diagram during simultaneous operation of cold storage and hot water supply of the multi-function heat pump system according to Embodiment 1 of the present invention.

FIG. 7 is a refrigeration cycle circuit configuration diagram during simultaneous operation of cold storage, cooling, and hot water supply of the multi-function heat pump system according to the first embodiment of the present invention.

FIG. 8 is a configuration diagram of a refrigeration cycle circuit during simultaneous operation of hot water supply and heating of the multifunctional heat pump system according to Embodiment 1 of the present invention.

FIG. 9 is a refrigeration cycle circuit configuration diagram of the multifunctional heat pump system according to Embodiment 1 of the present invention at the time of refrigerant recovery before cooling operation.

FIG. 10 is a refrigeration cycle circuit configuration diagram of the multi-function heat pump system according to Embodiment 1 of the present invention at the time of refrigerant recovery before heating operation.

FIG. 11 is a refrigeration cycle circuit configuration diagram of the multifunctional heat pump system according to Embodiment 1 of the present invention at the time of refrigerant recovery before simultaneous cooling and hot water supply operation.

FIG. 12 is a refrigeration cycle circuit configuration diagram of the multifunctional heat pump system according to Embodiment 1 of the present invention at the time of recovering refrigerant before the heat storage operation.

FIG. 13 is a configuration diagram of a refrigeration cycle circuit of the multi-function heat pump system according to Embodiment 1 of the present invention at the time of refrigerant recovery before a hot-water supply operation.

FIG. 14 is a refrigeration cycle circuit configuration diagram of the multifunction heat pump system according to Embodiment 1 of the present invention at the time of refrigerant recovery before simultaneous hot water supply / heating operation.

FIG. 15 is a configuration diagram of a refrigeration cycle circuit during simultaneous operation of heat storage and heating of the multifunctional heat pump system according to Embodiment 2 of the present invention.

FIG. 16 is a configuration diagram of a refrigeration cycle circuit during simultaneous operation of heat storage and hot water supply of the multifunctional heat pump system according to Embodiment 2 of the present invention.

FIG. 17 is a conceptual diagram of an embodiment of the multifunctional heat pump system according to the present invention.

FIG. 18 is a refrigeration cycle circuit configuration diagram of a conventional multifunctional heat pump system.

FIG. 19 is a refrigeration cycle circuit configuration diagram of another conventional multifunctional heat pump system.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Compressor, 2 outdoor heat exchangers, 3 indoor units (indoor heat exchangers), 4 cold storage heat tanks, 5 hot water supply heat exchangers, 6 hot water supply tanks, 7 hot water supply heaters, 8 four-way valves, 9 evaporation pressure adjustment valves, 10 Flow control valve for water, 11 Pump for water, 12
Pressure sensor, 13 outdoor unit, 14 branch unit,
15-30 connection end, 31-34 branch, 35 indoor heat exchanger side refrigerant circuit, 36 hot water supply heat exchanger side refrigerant circuit,
37 Refrigerant storage tank side refrigerant circuit, 38 Refrigerant suction circuit, 39
Capillary tube, SV1 to SV7 Solenoid valve, V
1 to V4 Flow control valve.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Tetsuji Nana species 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsui Electric Co., Ltd. (72) Inventor Keiji Kurokawa 2-chome Watanabe-dori, Chuo-ku, Fukuoka City, Fukuoka Prefecture 1-82 Kyushu Electric Power Co., Inc.

Claims (7)

[Claims] 1. A refrigerant circuit comprising one compressor and connecting the compressor with an outdoor heat exchanger, an indoor heat exchanger, a cold storage heat tank and a hot water supply heat exchanger. By switching the flow of refrigerant to the
A multifunctional heat pump system comprising a refrigeration cycle capable of independent operation of hot water supply, heat storage, and cold storage and a combined operation thereof. 2. A refrigeration cycle is constituted by connecting one compressor, an outdoor heat exchanger, an indoor heat exchanger, a regenerative heat tank and a hot water supply heat exchanger, and a compressor discharge side pipe is connected in two directions. After branching, one is provided with a sixth valve provided in parallel with the evaporating pressure regulating valve via a first valve, a switching valve, an outdoor heat exchanger, a second valve, a flow regulating valve, and an indoor heat exchanger. A refrigerant circuit that is connected to the switching valve through the switching valve, and further connects the switching valve to a compressor suction side pipe; and the other is a fourth valve, a hot water supply heat exchanger, and a flow control valve for an indoor heat exchanger. A refrigerant circuit joined and connected to the second valve via a flow control valve for a hot water supply heat exchanger provided in parallel; and a third valve branched from an upstream of the fourth valve and a cold storage heat tank. Connected to the second valve via a flow control valve for a cold storage heat tank provided in parallel with the flow control valve for the indoor heat exchanger. A multifunction heat pump system, comprising: a refrigerant circuit; and a refrigerant suction circuit branched from a downstream of the third valve and connected to the compressor suction side pipe via a fifth valve. . 3. An outdoor unit, a branch unit, an indoor unit,
The branch unit includes a hot water supply heat exchanger and at least a flow control valve, and is connected to the outdoor unit, the indoor unit, the cold storage heat tank, and the hot water supply tank, respectively. The multifunctional heat pump system according to claim 2, further comprising a piping portion that is provided. 4. The multifunctional heat pump system according to claim 2, wherein a capillary tube and a seventh valve are provided in parallel with the third valve provided in the refrigerant circuit on the side of the cold storage heat tank. A multifunctional heat pump system characterized by enabling simultaneous operation of heat storage and heating, or heat storage and hot water supply. 5. The method for operating a multi-function heat pump system according to claim 1, wherein before starting a specific operation mode in which a shortage of refrigerant is expected, during a refrigerant recovery operation and after refrigerant recovery, a four-way valve or An operation control method for a multifunctional heat pump system, wherein a refrigerant is recovered in a condensing-side heat exchanger used in an operation mode without switching a switching valve having an equivalent function. 6. The operation control method for a multifunctional heat pump system according to claim 5, wherein, when the refrigerant is recovered, the recovery operation is performed for a predetermined time. 7. The multifunctional heat pump system according to claim 5, wherein, when the refrigerant is recovered, the pressure sensor attached to the compressor suction side pipe performs the recovery operation until the pressure reaches a predetermined pressure. Operation control method.