WO2018143726A1 - Heat pump system - Google Patents

Abstract

The present invention relates to a heat pump system comprising: an outdoor unit installed in an outdoor space; a plurality of heat load units supplied with cold air and warm air; and an intermediate unit arranged between the outdoor unit and the plurality of heat load units, wherein the intermediate unit is connected to the outdoor unit through a refrigerant tube and is connected to the plurality of heat load units through a heat medium tube.

Description

Heat pump system

The present invention relates to a heat pump system, and more particularly, to a heat pump system including both a cooling unit used for cooling with a heat load unit and a heating unit used for heating.

In general, the heat pump system is for generating cold and warm air through the refrigerant, and includes a configuration such as a compressor, a condenser, an evaporator and an expansion device.

The heat pump system includes an outdoor unit disposed in an outdoor space, a cooling unit used for cooling, a heating unit used for heating, and an intermediate unit for distributing the refrigerant to the cooling unit and the heating unit. Therefore, cool air is supplied to the cooling unit and warm air is supplied to the heating unit through the refrigerant.

One aspect of the present invention is to provide a heat pump system capable of supplying either cold or warm air, or both cold and warm air, in a simpler configuration.

According to an aspect of the present invention, a heat pump system includes an outdoor unit disposed in an outdoor space, a plurality of heat load units receiving cold and warm air, and an intermediate unit disposed between the outdoor unit and the plurality of heat load units. The intermediate unit is connected to the outdoor unit through a refrigerant pipe through which a refrigerant passes, and is connected to the plurality of heat load units through a heat pipe through which a heat medium passes.

In addition, the plurality of heat load units include a cooling unit that receives and uses cold air and a heating unit that receives and uses warm air.

The outdoor unit may include a compressor for compressing a refrigerant, an outdoor heat exchanger for allowing the refrigerant to exchange heat with outdoor air, a four-way valve for guiding the refrigerant discharged from the compressor to one of the outdoor heat exchanger and the intermediate unit, and a refrigerant. And an outdoor expansion valve for expanding under reduced pressure.

In addition, the intermediate unit includes a cooling heat exchanger for heat exchange between the heat medium and the refrigerant transferred from the cooling unit, a heating heat exchanger for heat exchange between the heat medium and the refrigerant delivered from the heating unit, and an intermediate expansion valve for expanding the refrigerant under reduced pressure. do.

In addition, the first refrigerant pipe for guiding the refrigerant discharged from the compressor to the four-way valve, the second refrigerant pipe for guiding the refrigerant from the four-way valve to the outdoor heat exchanger, and the refrigerant from the four-way valve to the heating heat exchanger A third refrigerant pipe connected to the suction side of the compressor from the four-way valve to the suction side of the compressor, a fifth refrigerant pipe guiding the refrigerant from the cooling heat exchanger to the suction side of the compressor, and the outdoor heat exchanger. A sixth refrigerant pipe branched into two to form a cooling refrigerant pipe connected to the cooling heat exchanger and the other forming a heating refrigerant pipe connected to the heating heat exchanger, and the second refrigerant pipe and the third refrigerant pipe. A seventh refrigerant pipe for connecting the valve, and an on / off valve disposed in the seventh refrigerant pipe to selectively flow the refrigerant through the seventh refrigerant pipe. It includes more.

In addition, the fifth refrigerant pipe for guiding the refrigerant from the cooling heat exchanger to the suction side of the compressor, a pressure sensor for detecting the pressure of the refrigerant outlet side of the cooling heat exchanger, and the pressure sensor disposed in the fifth refrigerant pipe And a refrigerant flow rate control valve whose opening degree is controlled such that the pressure detected by the value is within a setting range.

In addition, a fifth refrigerant pipe for guiding the refrigerant from the cooling heat exchanger to the suction side of the compressor, a cooling temperature sensor for detecting the temperature of the heat medium cooled through the cooling heat exchanger, and branched from the cooling refrigerant pipe, the fifth refrigerant pipe. A refrigerant bypass pipe connected to a refrigerant pipe, and a bypass disposed in the refrigerant bypass pipe to open a flow path of the refrigerant bypass pipe when the temperature of the heat medium detected by the cooling temperature sensor is lower than a set threshold value. It further comprises an expansion valve.

In addition, a defrost bypass tube, one end of which is connected to the third refrigerant pipe for guiding the refrigerant from the four-way valve to the heating heat exchanger, and the other end is connected to the suction side of the compressor to the fifth refrigerant pipe, and the defrost bypass. The apparatus may further include a refrigerant flow path switching valve arranged in the pipe to open a flow path of the defrost bypass pipe when a defrost demand is generated in the outdoor heat exchanger.

In addition, a cooling heat medium supply pipe for supplying the heat medium cooled by the cooling heat exchanger to the cooling unit, a cooling heat medium recovery tube for passing the heat medium absorbed heat passing through the cooling unit to the cooling heat exchanger, and the heating heat exchanger And a heating heat medium supply pipe for supplying the heat medium cooled in the heating unit to the heating unit, and a heating heat medium recovery tube for transferring the heat medium passing through the heating unit to release heat.

The apparatus further includes a cooling pump arranged in the cooling heat medium recovery pipe and a heating pump arranged in the heating heat medium recovery pipe.

In addition, a cooling heat medium bypass pipe whose one end is connected to the cooling heat medium supply pipe and the other end is connected to the cooling heat medium recovery pipe, and a heating heat medium bypass pipe whose one end is connected to a heating heat medium supply pipe and the other end is connected to a heating heat medium recovery pipe. And a cooling heat medium bypass valve disposed in the cooling heat medium bypass pipe to open and close a flow path of the cooling heat medium bypass pipe, and a heating arranged in the heating heat medium bypass pipe to open and close a flow path of the heating heat medium bypass pipe. It further comprises a thermal medium bypass valve.

In addition, a first connection bypass tube having one end connected to the heating heat medium supply pipe and the other end connected to the cooling heat medium recovery pipe, and one end connected to the cooling heat medium supply pipe and the other end connected to the heating heat medium recovery pipe A second connection bypass pipe, a first connection bypass valve disposed in the first connection bypass pipe to open and close a flow path of the first connection bypass pipe, and a second connection bypass pipe disposed in the second connection bypass pipe. It further comprises a second connection bypass valve for opening and closing the flow path of the connection bypass pipe.

In addition, a cooling heat medium supply valve disposed in the cooling heat medium supply pipe to adjust an amount of the heat medium supplied to the cooling unit, and a cooling heat medium recovery arranged in the cooling heat medium recovery pipe to adjust an amount of the heat medium recovered from the cooling unit. A heating heating medium supply valve disposed in the heating heating medium supply pipe and adjusting the amount of the heating medium supplied to the heating unit, and a heating heating medium disposed in the heating heating medium recovery pipe and adjusting the amount of the heating medium recovered from the heating unit. It further comprises a recovery valve.

A heating refrigerant temperature sensor disposed on the refrigerant discharge side of the heating heat exchanger to detect a temperature of the refrigerant, a heating refrigerant pressure sensor disposed on the refrigerant discharge side of the heating heat exchanger to detect a pressure of the refrigerant, and the fifth refrigerant It further comprises a refrigerant flow rate control valve disposed in the tube is adjusted to the opening degree according to the supercooling degree of the refrigerant outlet side of the heating heat exchanger.

As described above, in the heat pump system according to an aspect of the present invention, since the outdoor unit and the intermediate unit are connected through the refrigerant pipe, and the intermediate unit and the heat load unit are connected through the heat medium pipe, the refrigerant pipes are not connected to the heat load unit. The connection structure of the tubes is simplified, thus facilitating the construction of the heat pump system.

1 is a schematic structural diagram of a heat pump system according to an embodiment of the present invention.

2 is a circuit diagram showing the flow of the refrigerant and the heat medium when the cooling mode is performed in the heat pump system according to an embodiment of the present invention.

3 is a circuit diagram showing the flow of the refrigerant and the heat medium when the heating mode is performed in the heat pump system according to the exemplary embodiment of the present invention.

4 is a circuit diagram showing the flow of the refrigerant and the heat medium when the cooling center mode is performed in the heat pump system according to the exemplary embodiment of the present invention.

5 is a circuit diagram showing the flow of the refrigerant and the heat medium when the heating center mode is performed in the heat pump system according to an embodiment of the present invention.

6 is a view showing a case in which the heat pump system according to an embodiment of the present invention performs the low pressure pressure retention control.

FIG. 7 is a diagram illustrating a case in which a heat pump system performs a cold water temperature prevention prevention control according to an embodiment of the present invention.

8 is a view showing a case in which the heat pump system according to an embodiment of the present invention performs defrost control.

9 is a diagram illustrating a case in which the heat pump system according to an embodiment of the present invention performs the first defrost mode.

FIG. 10 is a diagram illustrating a case in which the heat pump system performs a second defrost mode according to an embodiment of the present invention.

11 is a diagram illustrating a case in which the heat pump system performs freeze protection control according to an embodiment of the present invention.

12 is a diagram illustrating a case in which the heat pump system performs water bypass defrost control according to an embodiment of the present invention.

FIG. 13 is a diagram illustrating a case in which a heat pump system performs supercooling control according to an embodiment of the present invention.

Configurations shown in the embodiments and drawings described herein is a preferred embodiment of the disclosed invention, there can be various modifications that can replace the embodiments and drawings of the present specification at the time of the filing of the present application.

In addition, the same reference numerals or signs given in each drawing of the present specification represent parts or components that perform substantially the same function.

Also, the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting and / or limiting the disclosed invention. Singular expressions include plural expressions unless the context clearly indicates otherwise. As used herein, the terms "comprise", "comprise" or "have" are intended to designate that the features, numbers, steps, actions, components, parts, or combinations thereof described in the specification exist. Or any other feature or number, step, operation, component, part, or combination thereof, is not excluded in advance.

In addition, terms including ordinal numbers such as "first", "second", and the like used in the present specification may be used to describe various components, but the components are not limited by the terms. It is used only to distinguish one component from another. For example, without departing from the scope of the present invention, the first component may be referred to as the second component, and similarly, the second component may also be referred to as the first component. The term “and / or” includes any combination of a plurality of related items or any item of a plurality of related items.

In addition, terms such as "leading", "back", "top", "bottom", "top", and "bottom" as used herein are defined based on the drawings, and the shape and position of each component by this term. Is not limited.

Hereinafter, a heat pump system according to an embodiment of the present invention will be described in detail with reference to the drawings.

1 is a schematic diagram of a heat pump system 1 according to an embodiment of the present invention.

As shown in FIG. 1, the heat pump system 1 includes an outdoor unit 10 disposed in an outdoor space, heat load units 30L and 30H disposed in a space or a device requiring cold or warm air, and an outdoor unit ( 10) and an intermediate unit 20 disposed between the heat load units 30L and 30H to allow the cold and warm air generated in the outdoor unit 10 to be distributedly supplied to the heat load units 30L and 30H.

The outdoor unit 10 operates as a heat source for generating cold and warm air through the refrigerant, including a heat pump cycle, and supplies the cold or warm air to the heat load units 30L and 30H through the intermediate unit 20. The outdoor unit 10 is arranged in an outdoor space, that is, a rooftop or a veranda of a building.

The intermediate unit 20 allows the coolant and the warm air to be delivered to the heat load units 30L and 30H by allowing the refrigerant delivered from the outdoor unit 10 and the heat medium transferred from the heat load units 30L and 30H to heat exchange with each other.

The intermediate unit 20 may be disposed adjacent to the outdoor unit 10 or may be disposed in a separate space from the outdoor unit 10. That is, the intermediate unit 20 may be disposed together with the outdoor unit 10 in an outdoor space, or may be disposed in a common space of a building or an upper space of a ceiling.

The outdoor unit 10 and the intermediate unit 20 are each housed in separate housings and are connected to each other through the refrigerant pipes P1, P2, P3, P4, P5, P6, P7, and P8 that deliver the refrigerant.

The heat load units 30L and 30H receive and use cold and warm air generated in the outdoor unit 10 through the intermediate unit 20.

The heat load units 30L and 30H are connected to the intermediate unit 20 through the heat medium tubes L1, L2, H1, and H2 through which the heat medium passes, and transfer the cooling unit 30L and warmth to receive and use cold air. The heating unit 30H which receives and uses is included.

The cooling unit 30L and the intermediate unit 20 are connected to each other through two cooling heat medium tubes L1 and L2 which transfer the heat medium. The cooling heat medium pipe is a cooling heat medium supply pipe (L1) for supplying the heat medium cooled by the cooling heat exchanger (21) to the cooling unit (30L), and the heat medium that absorbs heat while passing through the cooling unit (30L). Cooling medium recovery tube (L2) to be delivered to). The cooling pump 23 is arranged in the cooling heat medium recovery pipe L2. Therefore, the heat medium passes through the intermediate unit 20 and heat-exchanges with the refrigerant to be cooled, and the cooled heat medium is supplied to the cooling unit 30L to perform cooling in the cooling unit 30L.

The cooling unit 30L may be used as a cooling device that is disposed in the indoor space to cool the indoor space by the cold air delivered from the outdoor unit 10, or may be used as a cooling device that is arranged on a production line to cool the mold and the like. . In addition, it can be applied to various spaces and devices that require cooling, such as cold water supply.

The heating unit 30H may be used as a heating device that is disposed in the indoor space to heat the indoor space by the warmth transmitted from the outdoor unit 10, or may be used as a heating device that is arranged in a production line to heat a mold and the like. . In addition, it can be applied to various spaces and devices that require heating, such as hot water supply.

The heating unit 30H and the intermediate unit 20 are connected to each other through two heating heating medium tubes H1 and H2 which transfer the heating medium. The heating heat medium tube includes a heating heat medium supply pipe (H1) for supplying the heat medium cooled by the heating heat exchanger (22) to the heating unit (30H), and a heat medium that radiates heat through the heating unit (30H). ) Is heated to the heating medium recovery tube (H2). The heating pump 24 is arrange | positioned at the heating heat medium recovery pipe | tube H2. Therefore, the heat medium passes through the intermediate unit 20, heat exchanges with the refrigerant, and is heated, and the heated heat medium is transferred to the cooling unit 30L to perform the heating in the cooling unit 30L.

The intermediate unit 20 transmits cool air to the cooling unit 30L by allowing the low temperature refrigerant supplied from the outdoor unit 10 to heat exchange with the heat medium transferred through the cooling heat medium tube, and the high temperature supplied from the outdoor unit 10. The refrigerant of the heat transfer to the heating unit (30H) by allowing the heat exchange with the heat medium transferred through the heating medium pipe (H1, H2).

The heating unit 30H and the intermediate unit 20 are connected to the heating unit 30H through the heating heating medium tubes H1 and H2 through which the heating medium passes. The heating unit 30H and the intermediate unit 20 are connected to each other through two heating heat pipes H1 and H2.

The heat pump system 1 includes a refrigerant circuit for allowing refrigerant to circulate between the outdoor unit 10 and the intermediate unit 20, and a cooling heat medium circuit for causing the heat medium to circulate between the intermediate unit 20 and the cooling unit 30L. And a heating heating medium circuit for causing the heating medium to circulate between the intermediate unit 20 and the heating unit 30H.

The refrigerant circuit generates cold and warm air and transmits the generated cold and warm air to the intermediate unit 20. The cold air delivered to the intermediate unit 20 is delivered to the cooling unit 30L through the cooling heat medium circuit, and the warm air delivered to the intermediate unit 20 is delivered to the heating unit 30H through the heating heat medium circuit.

The heat pump system 1 has four operating modes: a cooling mode, a heating mode, a cooling center mode, and a heating center mode. The heat pump system 1 selectively performs any one of the four operating modes in accordance with the needs of the heat load units 30L and 30H.

The cooling mode is an operation mode that is selected when only the cooling unit 30L is operated among the heat load units 30L and 30H. In the cooling mode, cold air is supplied only to the cooling unit 30L.

The heating mode is an operation mode selected when only the heating unit 30H operates among the heat load units 30L and 30H. In the heating mode, warmth is supplied only to the heating unit 30H.

In the cooling center mode, when the cooling unit 30L and the heating unit 30H of the heat load units 30L and 30H operate simultaneously, the load required on the cooling unit 30L side is applied to the heating unit 30H side. The operating mode is selected when the load is larger than the required load.

In the heating center mode, when the cooling unit 30L and the heating unit 30H among the heat load units 30L and 30H operate simultaneously, the load required on the heating unit 30H side is on the cooling unit 30L side. The operating mode is selected when the load is larger than the required load.

In the cooling center mode and the heating center mode, cold air is supplied to the cooling unit 30L and warm air is supplied to the heating unit 30H.

Hereinafter, the outdoor unit 10 will be described in more detail with reference to FIG. 1.

The outdoor unit 10 includes a compressor 11 for compressing a refrigerant at a high temperature and high pressure, a four-way valve 12 disposed at an outlet side of the compressor 11 to switch a flow path of the refrigerant discharged from the compressor 11, Check valve 13 for allowing the refrigerant to flow only in the forward direction, on / off valve 14 for switching the flow path of the refrigerant, and outdoor heat exchanger 15 for allowing the refrigerant to exchange heat with outdoor air passing through the outdoor unit 10. ).

In addition, the outdoor unit 10 includes a blower fan 16 through which the outdoor air passes through the outdoor heat exchanger 15, an accumulator 17 disposed on the suction side of the compressor 11 to separate the liquid refrigerant, and a refrigerant. It includes an outdoor expansion valve 18 for expanding under reduced pressure.

The compressor 11 is a device for compressing a refrigerant at high temperature and high pressure, and may be configured as an inverter compressor capable of controlling the capacity.

Four-way valve 12 is composed of an electromagnetic valve for switching the flow path is connected to the compressor 11 through the first refrigerant pipe (P1), and connected to the outdoor heat exchanger (15) through the second refrigerant pipe (P2) And a heat exchanger 22 to be described later through the third refrigerant pipe P3, and connected to the suction side of the compressor 11 through the fourth refrigerant pipe P4. Since the accumulator 17 is connected to the suction side of the compressor 11, the fourth refrigerant pipe P4 is connected to the accumulator 17.

Therefore, the refrigerant discharged from the compressor 11 is transferred to the four-way valve 12 through the first refrigerant pipe P1, and then the four-way valve 12 is used as one of the outdoor heat exchanger 15 and the heat exchanger 22. You are guided.

The four-way valve 12 switches the flow path so that the refrigerant discharged from the compressor 11 is transferred to the heating heat exchanger 22 to be described later through the third refrigerant pipe P3 in which the check valve 13 is disposed. 2 to be delivered to the outdoor heat exchanger (16) through the refrigerant pipe (P2).

Switching of the flow path through the four-way valve 12 is made in accordance with the operation mode, that is, corresponding to the load change required by the cooling unit 30L and the heating unit 30H.

The check valve 13 is for preventing the backflow of the refrigerant and is disposed in the second refrigerant pipe P2 for guiding the refrigerant discharged from the compressor 11 to the heating heat exchanger 22.

The second refrigerant pipe P2 and the third refrigerant pipe P3 are connected via the seventh refrigerant pipe P7 branched from the downstream side in the forward direction of the check valve 13 in the third refrigerant pipe P3. In the seventh refrigerant pipe P7, an on / off valve 14 for selectively allowing the refrigerant to flow through the seventh refrigerant pipe P7 according to the operation mode is disposed.

The shut-off valve 14 includes an anisotropic solenoid valve for opening and closing the inner flow path in accordance with the application of power to selectively pass the refrigerant.

The outdoor heat exchanger 15 allows outdoor air supplied by the blower fan 16 to exchange heat with the refrigerant. The outdoor heat exchanger 15 is connected to the cooling heat exchanger 21 and the heating heat exchanger 22 which will be described later.

The outdoor heat exchanger 15 operates as a condenser for cooling the refrigerant when the cooling mode and the cooling center mode, which are cooling operations, are performed. That is, in the cooling operation, the refrigerant passing through the outdoor heat exchanger 15 is condensed by dissipating heat.

In addition, the outdoor heat exchanger 15 operates as an evaporator for allowing the refrigerant to absorb heat when the heating mode and the heating center mode, which are heating operations, are performed. That is, in the heating operation, the refrigerant passing through the outdoor heat exchanger 15 absorbs heat and evaporates.

The sixth refrigerant pipe P6 is connected to the outdoor heat exchanger 15 together with the second refrigerant pipe P2 described above. The sixth refrigerant pipe (P6) is divided into two to form a cooling refrigerant pipe (P6-1), one of which is connected to the cooling heat exchanger 21, the other is a heating refrigerant connected to the heating heat exchanger (22) The tube P6-2 is formed.

The blowing fan 16 includes an axial fan for blowing air in the axial direction. The blowing fan includes a hub portion to which the rotating shaft of the motor is connected and a plurality of wings extending radially from the hub portion. As the blowing fan rotates, the air flows in the axial direction, passes through the outdoor heat exchanger 15, and the air passing through the outdoor heat exchanger 15 exchanges heat with the refrigerant passing through the outdoor heat exchanger 15.

The accumulator 17 is connected to the suction side of the compressor 11 via an eighth refrigerant pipe P8. The accumulator 17 stores the excess refrigerant generated by the difference in the amount of the refrigerant required during the heating operation and the cooling operation and the excess refrigerant due to the excessive operation method change. In addition, the accumulator 17 is connected to the four-way refrigerant pipe P8 and the fourth refrigerant pipe P4 and the fifth refrigerant pipe P5 in addition to the eight-way refrigerant pipe P8 and connected to the four-way valve 12 through the fourth refrigerant pipe P4. It is connected to the cooling heat exchanger 21 through the fifth refrigerant pipe (P5). The fifth refrigerant pipe P5 guides the refrigerant passing through the cooling heat exchanger 21 to the suction side of the compressor 11.

The outdoor expansion valve 18 includes an electronic expansion valve that can adjust the opening degree.

The outdoor expansion valve 18 is disposed in the section before branching of the sixth refrigerant pipe P6. That is, the outdoor expansion valve 18 is installed at the outlet side of the outdoor heat exchanger 15 when the refrigerant proceeds from the outdoor heat exchanger 15 to the cooling heat exchanger 21.

The outdoor heat exchanger 15 is connected to the refrigerant outlet side (at the heating operation) of the heating heat exchanger 22 and the refrigerant inlet side (at the cooling operation) of the cooling heat exchanger 21 via the outdoor expansion valve 18. In addition, the outdoor heat exchanger 15 is connected to the inlet side (at the heating operation) of the heating heat exchanger 22 through the on-off valve 14.

The outdoor unit 10 includes an outdoor processor C1 that controls the components of the outdoor unit 10 such as the compressor 11, the blower fan 16, the operation of the outdoor expansion valve 18, the four-way valve 12, and the like. do. The outdoor processor C1 includes a read only memory (ROM), a random access memory (RAM), and a central processing unit (CPU). Therefore, the various programs stored in the ROM of the outdoor processor C1 are read into the RAM and executed by the CPU, whereby the configurations of the outdoor unit 10 are controlled.

Hereinafter, the intermediate unit 20 will be described in more detail with reference to FIG. 1.

The intermediate unit 20 includes a cooling heat exchanger 21 for transmitting cold air to the heat medium and a heating heat exchanger 22 for transferring warmth to the heat medium. Here, the heat medium may be a liquid such as water or antifreeze.

The cooling heat exchanger 21 transfers cold air to the heat medium by causing the low temperature refrigerant and the heat medium to exchange heat with the low temperature refrigerant transferred from the outdoor unit 10. The cooling heat exchanger 21 operates as an evaporator when the cooling mode, the cooling center mode and the heating center mode are performed. That is, the cooling heat exchanger 21 absorbs heat from the heat medium when the cooling mode, the cooling center mode, and the heating center mode is performed so that the heat medium is cooled.

The heat exchanger 22 transmits warmth to the heat medium by allowing the high temperature refrigerant and the heat medium to be thermally effected from the outdoor unit 10. The heating heat exchanger 22 operates as a condenser when the heating mode, the cooling center mode and the heating center mode are performed. That is, the heating heat exchanger 22 supplies heat to the heating medium when the heating mode, the cooling center mode, and the heating center mode are performed so that the heating medium is heated.

The intermediate unit 20 includes a cooling pump 23 for circulating the heat medium through the cooling heat medium pipes L1 and L2 and a heat pump 24 for circulating the heat medium through the heating heat medium pipes H1 and H2. do.

The intermediate unit 20 includes an intermediate expansion valve 25 for expanding the refrigerant under reduced pressure. The intermediate expansion valve 25 is made up of an electromagnetic expansion valve like the outdoor expansion valve 18. The intermediate expansion valve 25 is provided at the inlet side (at the time of cooling operation) of the cooling heat exchanger 21.

The intermediate unit 20 includes an intermediate processor C2 which controls the components of the intermediate unit 20, such as the intermediate expansion valve 25, the cooling pump 23 and the heat pump 24. The intermediate processor C2 includes a read only memory (ROM), a random access memory (RAM), and a central processing unit (CPU). Therefore, various programs stored in the ROM of the intermediate processor C2 are read into the RAM and executed by the CPU, whereby the configurations of the intermediate processor C2 are controlled.

The outdoor processor C1 and the intermediate processor C2 are configured to be communicable and control the operation of the heat pump system 1 while transmitting and receiving signals with each other.

The intermediate unit 20 is disposed at the cooling medium pressure sensor PS1 for detecting the refrigerant pressure at the refrigerant outlet side of the cooling heat exchanger 21, and at the heat medium outlet side of the cooling heat exchanger 21 to provide the cooling heat exchanger 21. Cooling temperature sensor (T1) for detecting the temperature of the heat medium cooled through the heating temperature sensor (T2) disposed on the heat medium outlet side of the heat exchanger to detect the temperature of the heat medium heated through the heat exchanger (22) do.

The information detected by the cooling refrigerant pressure sensor PS1 and the information detected by the cooling temperature sensor T1 and the heating temperature sensor T2 are transferred to the intermediate processor C2 to use the operation of the heat pump system 1 for control. do.

The components forming the intermediate unit 20 are all accommodated in one housing, but this is only an example and the present disclosure is not limited thereto. That is, the cooling heat exchanger 21, the cooling pump 23 and the cooling temperature sensor T1 is accommodated in one housing, and the heating heat exchanger 22, the heating pump 24 and the heating temperature sensor T2 are It is also possible to be housed in another housing.

Hereinafter, a case in which the heat pump system according to an aspect of the present invention performs the cooling mode will be described with reference to FIG. 2. In FIG. 2, the flow of the refrigerant is indicated by a solid arrow, and the flow of the heat medium is indicated by a dotted arrow.

First, the flow of the refrigerant in the cooling mode will be described.

In the cooling mode, the four-way valve 12 guides the refrigerant to the second flow path. That is, the four-way valve 12 allows the refrigerant to flow in the direction of arrow A1. At this time, the open / close valve 14 closes the flow path, and the outdoor expansion valve 18 opens all the flow paths.

The opening degree of the intermediate expansion valve 25 is controlled to correspond to the outlet superheat degree of the cooling heat exchanger 21. In more detail, when the opening degree of the intermediate expansion valve 25 is increased in the cooling mode, the amount of the refrigerant that is expanded under reduced pressure is increased to lower the refrigerant outlet temperature of the cooling heat exchanger 21. On the contrary, if the opening degree of the intermediate expansion valve 25 is made small, the amount of refrigerant decompressed under pressure decreases, and the refrigerant outlet side temperature of the cooling heat exchanger 21 becomes high. Therefore, by controlling the opening degree of the intermediate expansion valve 25, the outlet superheat degree of the cooling heat exchanger 21, that is, the temperature difference between the refrigerant inlet side and the outlet side of the cooling heat exchanger 21 can be controlled to a set value.

The refrigerant is compressed by the compressor 11 into a gaseous state of high temperature and high pressure, and is delivered to the outdoor heat exchanger 15 operating as a condenser through the four-way valve 12. The refrigerant is cooled by heat exchange with outdoor air in the outdoor heat exchanger 15 to condense. The condensed refrigerant passes through the outdoor expansion valve 18 to the intermediate expansion valve 25, and is expanded under reduced pressure by the intermediate expansion valve 25. The refrigerant is then delivered to a cooling heat exchanger 21 which acts as an evaporator. In the cooling heat exchanger 21, since the refrigerant absorbs heat from the heat medium, the heat medium is cooled. The refrigerant passing through the cooling heat exchanger 21 is sucked back into the compressor 11 after passing through the accumulator 17.

In the cooling mode, the refrigerant is thus compressed in the compressor (11), the four-way valve (12), the outdoor heat exchanger (15), the outdoor expansion valve (18), the intermediate expansion valve (25), the cooling heat exchanger (21), and the accumulator (17). A refrigerant circuit is configured to cycle through the circuits.

Next, the flow of the heat medium in the cooling mode will be described.

In accordance with the operation of the cooling pump 23, the heat medium flows from the cooling unit 30L to the cooling pump 23, and is then transferred from the cooling pump 23 to the cooling heat exchanger 21. In the cooling heat exchanger 21, since the refrigerant absorbs heat of the heat medium, the heat medium is cooled. Since the cooled heat medium is delivered back to the cooling unit 30L, cold air is supplied to the cooling unit 30L through the heat medium.

In this way, in the cooling mode, the heat medium is configured so that the heat medium circulates through the cooling unit 30L, the cooling pump 23, and the cooling heat exchanger 21 in sequence.

Hereinafter, a case in which the heat pump system according to an aspect of the present invention performs the heating mode will be described with reference to FIG. 3. In FIG. 3, the flow of the refrigerant is indicated by a solid arrow, and the flow of the heat medium is indicated by a dotted arrow.

First, the flow of the refrigerant in the heating mode will be described.

In the heating mode, the four-way valve 12 guides the refrigerant to the first flow path. That is, the four-way valve 12 allows the refrigerant to flow in the direction of arrow A2. At this time, the on-off valve 14 and the intermediate expansion valve 25 closes the flow path.

In addition, the opening degree of the outdoor expansion valve 18 is controlled in accordance with the outlet superheat degree of the outdoor heat exchanger 15 similarly to the opening degree of the intermediate expansion valve 25 in the cooling mode described above.

The refrigerant is compressed by the compressor 11 into a gaseous state of high temperature and high pressure, and is sequentially passed through the four-way valve 12 and the check valve 13 to a heating heat exchanger 22 operating as a condenser. In the heat exchanger 22, the refrigerant is heat-exchanged with the heat medium, cooled and condensed, and the heat medium absorbs heat from the refrigerant and is heated.

The refrigerant condensed in the heat exchanger 22 is delivered to the outdoor expansion valve 18 and expanded under reduced pressure by the outdoor expansion valve 18. The expanded pressure refrigerant is transferred to an outdoor heat exchanger (15) that operates as an evaporator, and heat exchanges with outdoor air in the outdoor heat exchanger (15) to absorb heat and evaporate. Subsequently, the refrigerant is sucked back into the compressor 11 through the four-way valve 12 and the accumulator 17.

Thus, in the heating mode, the refrigerant is the compressor 11, the four-way valve 12, the check valve 13, the heat exchanger 22, the outdoor expansion valve 18, the outdoor heat exchanger 15, the four-way valve 12 And a refrigerant circuit for circulating the accumulator 17 in turn.

Next, the flow of the heat medium in the heating mode will be described.

As the heat pump 24 is driven, the heat medium flows from the heating unit 30H to the heat pump 24, and is then transferred from the heat pump 24 to the heat heat exchanger 22. In the heat exchanger 22, since the heat medium absorbs heat of the refrigerant, the heat medium is heated. Since the heated heating medium is transferred back to the heating unit 30H, warmth is supplied to the heating unit 30H through the heating medium.

In this manner, in the heating mode, the heat medium is configured so that the heat medium circulates through the heating unit 30H, the heat pump 24, and the heat exchanger 22 in sequence.

Hereinafter, a case in which the heat pump system according to an aspect of the present invention performs the cooling center mode will be described with reference to FIG. 4. In FIG. 4, the flow of the refrigerant is indicated by a solid arrow, and the flow of the heat medium is indicated by a dotted arrow.

First, the flow of the refrigerant in the cooling center mode will be described.

In the cooling center mode, the four-way valve 12 guides the refrigerant to the second flow path. That is, the four-way valve 12 guides the refrigerant to flow in the direction of arrow A1. At this time, the opening degree of the intermediate expansion valve 25 is controlled to correspond to the outlet superheat degree of the cooling heat exchanger 21 as in the above-described cooling mode.

The opening degree of the outdoor expansion valve 18 is controlled to correspond to the load required by the heating unit 30H. In more detail, when the opening degree of the outdoor expansion valve 18 is made small, the amount of refrigerant delivered to the heat exchanger 22 through the on-off valve 14 increases. Therefore, the larger the required load of the heating unit 30H is, the smaller the opening degree of the outdoor expansion valve 18 is controlled.

The refrigerant is compressed by the compressor 11 to be in a gaseous state of high temperature and high pressure, and is guided to the outdoor heat exchanger 15 and the open / close valve 14 by the four-way valve 12.

A portion of the refrigerant discharged from the compressor is delivered to the outdoor heat exchanger 15 that operates as a condenser, and the refrigerant delivered to the outdoor heat exchanger 15 is cooled by heat exchange with outdoor air in the outdoor heat exchanger 15 to be condensed. The condensed refrigerant passes through the outdoor expansion valve 18 and is delivered to the intermediate expansion valve 25.

On the other hand, the remaining refrigerant is delivered to the on-off valve 14, the refrigerant delivered to the on-off valve 14 passes through the on-off valve 14, it is delivered to the heating heat exchanger 22 acting as a condenser. In the heat exchanger 22, the refrigerant condenses while heating the heat medium. Here, the heat medium absorbs heat from the refrigerant and is heated. The refrigerant condensed through the heat exchanger 22 is joined with the refrigerant passed through the outdoor heat exchanger 15 and the outdoor expansion valve 18.

The combined refrigerant is expanded under reduced pressure by the intermediate expansion valve 25 to be in a gas-liquid mixed state of low temperature and low pressure. The refrigerant is then delivered to a cooling heat exchanger 21 which acts as an evaporator. In the cooling heat exchanger (21), the refrigerant absorbs heat from the heat medium and becomes a low temperature low pressure gas refrigerant. The refrigerant passing through the cooling heat exchanger 21 passes through the accumulator 17 and is sucked back into the compressor 11.

As described above, in the cooling center mode, after the refrigerant passes through the compressor 11 and the four-way valve 12, a part of the refrigerant passes through the outdoor heat exchanger 15 and the outdoor expansion valve 18, and the rest of the refrigerant opens and closes the valve. After passing through the heat exchanger (14) and the heat exchanger (22), it joins again. The joined refrigerant is configured to pass through the intermediate expansion valve (25), the cooling heat exchanger (21), and the accumulator (17) in order to be sucked back into the compressor.

The flow of the heat medium in the cooling center mode is the same as the cooling mode and the heating mode. That is, the heat medium circuit for supplying cold air to the cooling unit 30L is configured by causing the heat medium to circulate through the cooling unit 30L, the cooling pump 23 and the cooling heat exchanger 21 in sequence, and to the heating unit 30H. The heat medium circuit for supplying warmth is configured by causing the refrigerant to cycle through the heating unit 30H, the heat pump 24 and the heat exchanger 22 in sequence.

Hereinafter, a case in which the heat pump system according to an aspect of the present invention performs the heating center mode will be described with reference to FIG. 5. In FIG. 5, the flow of the refrigerant is indicated by a solid arrow, and the flow of the heat medium is indicated by a dotted arrow.

First, the flow of the refrigerant in the heating center mode will be described.

In the heating center mode, the four-way valve 12 guides the refrigerant to the first flow path. That is, the four-way valve 12 allows the refrigerant to flow in the direction of arrow A2. The on-off valve 14 closes the flow path, and the opening degree of the intermediate expansion valve 25 is controlled to correspond to the outlet superheat degree of the cooling heat exchanger 21 similarly to the cooling mode described above. In addition, the opening degree of the outdoor expansion valve 18 is controlled to correspond to the load required by the cooling unit 30L. In more detail, when the opening degree of the outdoor expansion valve 18 is made small, the amount of the refrigerant delivered to the cooling heat exchanger 21 increases. Therefore, the larger the required load of the cooling unit 30L, the smaller the opening degree of the outdoor expansion valve 18 is controlled.

The refrigerant is compressed by the compressor 11 to be in a gaseous state of high temperature and high pressure, and after passing through the four-way valve 12 and the check valve 13 in sequence, the refrigerant is transferred to a heat exchanger 22 operating as a condenser. In the heat exchanger 22, the refrigerant heats and heats the heating medium to condense.

Some of the refrigerant condensed in the heat exchanger 22 is delivered to the intermediate expansion valve 25 and the rest to the outdoor expansion valve 18.

The refrigerant delivered to the intermediate expansion valve 25 is expanded under reduced pressure by the intermediate expansion valve 25 to become a gas-liquid mixed refrigerant of low temperature and low pressure, and then is delivered to the cooling heat exchanger 21 operating as an evaporator. In the cooling heat exchanger 21, the refrigerant absorbs heat from the heat medium and becomes a low temperature low pressure gas state. At this time, since the refrigerant absorbs heat from the heat medium, the heat medium is cooled. The refrigerant passing through the cooling heat exchanger 21 is sucked back into the compressor 11 after passing through the accumulator 17.

On the other hand, the refrigerant delivered to the outdoor expansion valve 18 is expanded under reduced pressure by the outdoor expansion valve 18 is a gas-liquid mixed state of low temperature and low pressure. The refrigerant is then delivered to an outdoor heat exchanger 15 which acts as an evaporator. In the outdoor heat exchanger (15), the refrigerant exchanges heat with outdoor air, absorbs heat, becomes a low-temperature low-pressure gas state, passes through the four-way valve (12) and the accumulator (17), and is sucked back into the compressor (11).

Thus, in the heating center mode, after the refrigerant passes through the compressor 11, the four-way valve 12, the check valve 13, the heat exchanger 22, a part of the refrigerant is intermediate expansion valve 25 and the cooling heat exchange After passing through the group 21, the remainder is passed through the outdoor expansion valve 18, the outdoor heat exchanger 15, the four-way valve 12 in order and then joined. Subsequently, the joined refrigerant passes through the accumulator 17 and is then sucked back into the compressor 11 to form a refrigerant circuit.

The flow of the heat medium in the heating center mode is the same as the cooling mode and the heating mode. That is, the heat medium circuit for supplying cold air to the cooling unit 30L is configured by causing the heat medium to circulate through the cooling unit 30L, the cooling pump 23 and the cooling heat exchanger 21 in sequence, and to the heating unit 30H. The heat medium circuit for supplying warmth is configured by causing the refrigerant to cycle through the heating unit 30H, the heat pump 24 and the heat exchanger 22 in sequence.

Hereinafter, the low pressure pressure retention control of the heat pump system 1 according to the present embodiment will be described with reference to FIG. 6. The low pressure pressure maintaining control is performed in the cooling mode, the cooling center mode and the heating center mode.

FIG. 6 shows a heat pump system 1 in which a refrigerant flow control valve 26 is added to the intermediate unit 20 shown in FIG. 1.

The refrigerant flow rate regulating valve 26 is disposed on the fifth refrigerant pipe P5 between the cooling heat exchanger 21 and the accumulator 17, that is, on the refrigerant outlet side of the cooling heat exchanger 21.

The low pressure pressure retention control is performed by controlling the opening degree of the refrigerant flow rate regulating valve 26 so that the pressure at the refrigerant outlet side of the cooling heat exchanger 21 becomes a value within a setting range. In other words, the low pressure pressure maintaining control controls the opening degree of the refrigerant flow rate control valve 26 such that the internal refrigerant evaporation pressure of the cooling heat exchanger 21 is a value within a setting range. If it demonstrates further, the opening degree of the refrigerant flow volume control valve 26 is controlled so that the evaporation temperature computed from the refrigerant pressure of the exit side of the cooling heat exchanger 21 may not be below the freezing temperature of a heat medium.

In more detail, the pressure at the refrigerant outlet side of the cooling heat exchanger 21 is detected by the cooling refrigerant pressure sensor PS1. When the detected pressure of the coolant is lower than the set range, the coolant flow control valve 26 is controlled to reduce the opening degree of the coolant flow control valve 26. When the opening degree of the refrigerant flow rate control valve 26 decreases, the refrigerant outlet side pressure of the cooling heat exchanger 21 increases. In addition, when the detected pressure of the refrigerant exceeds the set range, the refrigerant flow rate control valve 26 is controlled to increase the opening degree of the refrigerant flow rate control valve 26. As the opening degree of the refrigerant flow rate control valve 26 increases, the refrigerant outlet side pressure of the cooling heat exchanger 21 decreases. As described above, the opening degree of the refrigerant flow rate control valve 26 is controlled so that the outlet refrigerant pressure of the cooling heat exchanger 21 is maintained within the set range.

Further, when the heat pump system 1 is operated in the heating center mode in the winter when the ambient temperature of the outdoor heat exchanger 15 is low, the evaporation pressure of the outdoor heat exchanger 15 is lowered and the cooling heat exchanger ( The evaporation pressure of 21 can be lowered. In this case, when the evaporation pressure of the cooling heat exchanger 21 is abnormally lowered, the flow rate of the refrigerant passing through the cooling heat exchanger 21 is increased, so that the heat medium can be cooled to an appropriate level or higher, and as a result, the cooling heat medium pipe L1. , The heat medium passing through L2) may be frozen.

Accordingly, the low pressure pressure maintaining control controls the refrigerant flow rate regulating valve 26 to open the refrigerant flow rate regulating valve 26 when the pressure of the refrigerant detected by the cooling refrigerant pressure sensor PS1 is abnormally lowered to be out of the setting range. To be reduced. As the opening degree of the refrigerant flow rate control valve 26 decreases, the pressure of the refrigerant passing through the cooling heat exchanger 21 increases so that the freezing of the heat medium of the cooling heat medium tubes L1 and L2 can be suppressed. In addition, cold air can also be stably supplied to the cooling unit 30L.

Next, cold water temperature fall prevention control of the heat pump system 1 which concerns on a present Example is demonstrated with reference to FIG. Cold water temperature fall prevention control is performed in the cooling mode, the cooling center mode and the heating center mode.

7 shows a heat pump system 1 in which a refrigerant bypass pipe B1 and a bypass expansion valve 27 are added to the intermediate unit 20 shown in FIG. 1.

The refrigerant bypass pipe B1 is branched from the cooling refrigerant pipe P6-1 traveling from the outdoor expansion valve 18 to the intermediate expansion valve 25, and connects the cooling heat exchanger 21 and the accumulator 17. It is connected to the fifth refrigerant pipe (P5), so that the refrigerant can be delivered to the compressor (11) by bypassing the cooling heat exchanger (21).

The bypass expansion valve 27 is formed as a solenoid valve that can adjust the opening degree, and is disposed in the refrigerant bypass pipe B1 to open and close the flow path of the refrigerant bypass pipe B1. In general, the bypass expansion valve 27 closes the flow path of the refrigerant bypass pipe B1 to prevent the flow of the refrigerant through the refrigerant bypass pipe B1.

The cold water temperature reduction prevention control controls the intermediate expansion valve 25 when the temperature of the heat medium detected by the cooling temperature sensor T1 is lower than the set threshold, thereby controlling the cooling refrigerant pipe P6-1 at the inlet side of the cooling heat exchanger. ) And the bypass expansion valve 27 is controlled to open the flow path of the refrigerant bypass pipe B1.

When the flow path of the inlet refrigerant pipe of the cooling heat exchanger 21 is closed through the intermediate expansion valve 25, the refrigerant transfer to the cooling heat exchanger 21 is blocked. In addition, as the flow path of the refrigerant bypass pipe B1 is opened through the bypass expansion valve 27, the refrigerant is transferred to the bypass expansion valve 27, as indicated by the arrow in the figure. Subsequently, when the temperature of the heat medium detected by the cooling temperature sensor T1 becomes equal to or greater than the set threshold value, the intermediate expansion valve 25 is controlled to control the inlet side of the cooling heat exchanger 21, that is, the cooling refrigerant pipe P6. When the flow path of -1) is opened and the flow path of the refrigerant bypass pipe B1 is closed by controlling the bypass expansion valve 27, the refrigerant is again transferred to the cooling heat exchanger 21.

In further detail, when the temperature of the heat medium becomes very low, the heat medium may be frozen. Therefore, when the temperature of the cold water lowering prevention control is lower than the set threshold value, the intermediate expansion valve 25 is closed to block the inflow of the refrigerant to the cooling heat exchanger 21. Since the heat medium is not cooled when the inflow of the refrigerant to the cooling heat exchanger 21 is blocked, the heat medium passing through the cooling heat medium tubes L1 and L2 is prevented from being frozen. The threshold set here is preferably set to a temperature slightly higher than the freezing temperature of the heat medium. For example, when the heat medium is water, it is preferable that the set threshold value is set to 2 ° C., which is slightly higher than 0 ° C. which is the freezing temperature.

In addition, the refrigerant bypass pipe B1 and the bypass expansion valve 27 are installed to allow the refrigerant to circulate even when the flow path of the cooling refrigerant pipe P6-2 is closed by the intermediate expansion valve 25. Therefore, the refrigerant delivered from the outdoor expansion valve 18 by closing the intermediate expansion valve 25 and opening the bypass expansion valve 27 is transferred to the compressor 11 side through the refrigerant bypass pipe B1.

Next, defrost control of the heat pump system 1 which concerns on a present Example is demonstrated with reference to FIG. Defrost control includes a first defrost mode, a second defrost mode, and a third defrost mode.

8 shows a heat pump system 1 in which a defrost bypass pipe B2 and a refrigerant flow path switching valve 28 are added to the intermediate unit 20 shown in FIG. 7.

The defrost bypass pipe B2 is connected at one end to the third refrigerant pipe P3 connecting the four-way valve 12 and the heating heat exchanger 22, and the other end thereof is the cooling heat exchanger 21 and the accumulator 17. It is connected to the fifth refrigerant pipe (P5) for connecting. That is, the defrost bypass pipe B2 connects the refrigerant inlet side of the heating heat exchanger 22 and the refrigerant outlet side passage of the cooling heat exchanger 21.

The coolant flow path switching valve 28 is disposed in the defrost bypass pipe B2 to selectively allow the flow of the coolant through the defrost bypass pipe B2. In a general state, the refrigerant flow path switching valve 28 maintains the state in which the flow path is closed to block the flow of the refrigerant through the defrost bypass pipe B2.

First, the first defrost mode will be described.

When the defrost request in the outdoor heat exchanger 15 occurs while the heating mode is being performed, the heating mode is switched to the first defrost mode. Here, the defrost request in the outdoor heat exchanger 15 is confirmed by the temperature, pressure or ambient temperature of the refrigerant delivered to the outdoor heat exchanger 15 or the refrigerant discharged from the outdoor heat exchanger 15. The case where the defrost request occurs in the outdoor heat exchanger 15 is, in other words, a case where a set condition for performing the defrost of the outdoor heat exchanger 15 is satisfied. More specifically, for example, the case where the outlet side refrigerant temperature of the outdoor heat exchanger 15 is lower than the set temperature while the heating mode is being performed may correspond to this.

In further detail, while the heating mode is being performed, the temperature of the heat medium detected by the heating temperature sensor T2 is greater than or equal to the predetermined threshold while the refrigerant temperature at the outlet side of the outdoor heat exchanger 15 is lower than the set threshold. Is confirmed, the heating mode is switched to the first defrost mode.

Meanwhile, while the heating mode is being performed, it is confirmed that the temperature of the heat medium detected by the heating temperature sensor T2 is lower than the set threshold while the temperature of the outlet refrigerant of the outdoor heat exchanger 15 is lower than the set threshold. In this case, it is switched to the second defrost mode to be described later in the heating mode.

9 is a view showing the flow of the refrigerant and the heat medium in the first defrost mode. In FIG. 9, the flow of the refrigerant is indicated by a solid arrow, and the flow of the heat medium is indicated by a dotted arrow.

In the first defrost mode, the four-way valve 12 guides the refrigerant to the outdoor heat exchanger 15. That is, the four-way valve 12 guides the refrigerant to flow in the direction of arrow A1. In addition, the open / close valve 14, the intermediate expansion valve 25, and the bypass expansion valve 27 all close the flow path, and the refrigerant flow path switching valve 28 opens the flow path. On the other hand, the opening degree of the outdoor expansion valve 18 is controlled to correspond to the outlet superheat degree of the heat exchanger 22 similarly to the opening degree of the intermediate expansion valve 25 in the cooling mode described above.

The refrigerant is compressed by the compressor 11 to become a gas state of high temperature and high pressure, and is delivered to the outdoor heat exchanger 15 through the four-way valve 12. Since the refrigerant in the outdoor heat exchanger 15 emits heat, the castle generated on the surface of the outdoor heat exchanger 15 is removed. The refrigerant passing through the outdoor heat exchanger (15) is expanded under reduced pressure by the outdoor expansion valve (18) to be a gas-liquid mixed state of low temperature and low pressure, and is delivered to a heat exchanger (22) operating as an evaporator. In the heat exchanger 22, the refrigerant absorbs heat from the heat medium and is heated. The refrigerant passing through the heat exchanger (22) passes through the refrigerant flow path switching valve (28) and the accumulator (17) and is sucked back into the compressor (11).

As described above, in the first defrosting mode, the refrigerant is provided in the compressor 11, the four-way valve 12, the outdoor heat exchanger 15, the outdoor expansion valve 18, the heat exchanger 22, the refrigerant flow path switching valve 28, A refrigerant circuit for circulating the accumulator 17 is configured. The refrigerant is heated by heat absorbed by the heat medium, and the heated refrigerant is transferred to the outdoor heat exchanger 15 to perform defrosting of the outdoor heat exchanger 15.

On the other hand, in the 1st defrost mode, the heat medium circulates the heating unit 30H, the heat pump 24, and the heat exchanger 22 to a shield, and the heat medium circuit is comprised. In the first defrost mode, the heat medium circulates along the heating heat medium tubes H1 and H2, so that warming is continuously supplied to the heating unit 30H.

However, since the heat medium cooled while heat-exchanging with the refrigerant in the heat exchanger 22 is transferred to the heating unit 30H, the warmth to be supplied may be reduced as compared with the case in which the heating mode is performed.

In addition, when the lengths of the heating heat medium tubes H1 and H2 are short, the heat capacity of the heat medium may not be sufficiently secured. When the heat capacity of the heat medium is not sufficiently secured, the amount of heat required for defrosting exceeds the heat capacity of the heat medium, so that warmth cannot be supplied to the heating unit 30H, and heat is absorbed from the heating unit 30H. 30H) may be subjected to cooling.

Therefore, before the endotherm is cooled from the heating unit 30H, the heat absorption from the heat medium must be stopped to prevent cooling from the heating unit 30H.

More specifically, when the temperature of the heat medium circulating along the heating heat medium tubes H1 and H2 in the state where the first defrost mode is being performed is lower than the set threshold, the first defrost mode is switched to the second defrost mode. In addition, as described above, the temperature of the refrigerant on the outlet side of the outdoor heat exchanger 15 is lower than the set threshold value in the state where the heating mode is being performed, and the temperature of the heat medium circulating the heating heat medium pipes H1 and H2 is set. If it is lower than the threshold value, the switching from the heating mode to the second defrost mode.

The set threshold value of the heat medium temperature in the case of switching from the first defrost mode or the heating mode to the second defrost mode may be determined by the air temperature in the room where the heating unit 30H is disposed. That is, when the temperature of the heat medium circulating the heating heat medium tubes H1 and H2 in the state where the first defrost mode is being performed is lower than the indoor set air temperature of the heating unit 30H, the second defrost in the first defrost mode. The mode is switched.

10 is a view showing the flow of the refrigerant and the heat medium in the second defrost mode. In FIG. 10, the flow of the refrigerant is indicated by a solid arrow.

In the second defrost mode, the four-way valve 12 guides the refrigerant to the outdoor heat exchanger 15. That is, the four-way valve 12 allows the refrigerant to flow in the direction of arrow A1. In addition, the opening / closing valve 14, the refrigerant flow path switching valve 28, and the outdoor expansion valve 18 open the flow path, and the intermediate expansion valve 25 closes the flow path.

The refrigerant is compressed by the compressor 11 to become a gas state of high temperature and high pressure, and is delivered to the outdoor heat exchanger 15 through the four-way valve 12. In the outdoor heat exchanger (15), the refrigerant releases heat, so that the castle attached to the surface of the outdoor heat exchanger (15) is removed. The refrigerant passing through the outdoor heat exchanger (15) passes through the outdoor expansion valve (18), but is not delivered to the heating heat exchanger (22), and is expanded under reduced pressure by the bypass expansion valve (27) to form a gas-liquid mixed state of low temperature and low pressure. Becomes The refrigerant expanded by the bypass expansion valve 27 is mixed with the high temperature and high pressure refrigerant delivered through the defrost bypass pipe B2 to become a superheated gas, and then sucked into the compressor 11 through the accumulator 17. .

In this manner, in the second defrost mode, the refrigerant sequentially rotates the compressor 11, the four-way valve 12, the outdoor heat exchanger 15, the outdoor expansion valve 18, the bypass expansion valve 27, and the accumulator 17. A refrigerant circuit is configured to circulate through.

Next, the third defrost mode will be described.

The third defrost mode is a mode in which the outdoor heat exchanger 15 is defrosted by switching from the heating center mode to the cooling center mode. That is, when the defrost request of the outdoor heat exchanger 15 occurs (for example, when the refrigerant temperature at the outlet side of the outdoor heat exchanger 15 is lower than the set threshold) while operating in the heating center mode. Switch from center mode to cooling center mode.

In the heating center mode, the refrigerant cooled in the heat exchanger 22 is transferred to the outdoor heat exchanger 15 which operates as an evaporator through the outdoor expansion valve 18. Accordingly, the temperature of the outdoor heat exchanger 15 is lowered, and frost may occur on the surface of the outdoor heat exchanger 15.

On the other hand, in the cooling center mode, the high-temperature, high-pressure gaseous refrigerant compressed by the compressor 11 is transmitted to the outdoor heat exchanger 15 operating as a condenser through the four-way valve 12. Thus, by causing the heat pump system 1 to switch from the heating center mode to the cooling center mode, the refrigerant is allowed to dissipate heat from the outdoor heat exchanger 15, thereby eliminating the castle generated on the surface of the outdoor heat exchanger 15. .

In further detail, in the third defrost mode, the warmth supplied to the heating load may decrease as the switching from the heating center mode to the cooling center mode, but as the cooling center mode is performed, the warmth supply to the heating unit 30H and The supply of cold air to the cooling unit is continued.

Next, freeze protection control of the heat pump system 1 according to the present embodiment will be described with reference to FIG.

When the compressor 11, the cooling pump 23, the heat pump 24, or the like is stopped and the refrigerant and the heat medium do not circulate, the heat medium can be frozen in accordance with the decrease in the outside air temperature. When the heat medium is frozen, the heating heat exchanger 22, the cooling heat exchanger 21, the heating heat medium tubes H1 and H2, and the cooling heat medium tubes L1 and L2 may be damaged. Therefore, freezing prevention control is performed to prevent freezing of the heat medium.

FIG. 11 shows a heat pump system 1 in which an intermediate unit 20 disclosed in FIG. 1 is added with heat medium bypass tubes B3 and B4 and heat medium bypass valves 29L and 29H to prevent freezing. .

In the heat medium bypass pipes B3 and B4, one end thereof is connected to the cooling heat medium supply pipe L1 and the other end thereof is connected to the cooling heat medium recovery pipe L2, and one end thereof is a heated heat medium. The heating heat medium bypass pipe B4 connected to the supply pipe H1 and the other end thereof to the heating heat medium recovery pipe H2 is included.

The heating medium bypass valves 29L and 29H are disposed in the cooling heating medium bypass pipes B3 and B4, and the cooling heating medium bypass valve 29L which opens and closes the flow path of the cooling heating medium bypass pipes B3 and B4, and the heating is performed. The heating heating medium bypass valve 29H which is arrange | positioned in heating medium bypass pipe B3, B4 and opens and closes the flow path of heating heating medium bypass pipe B3, B4 is contained.

In the general state, the heat medium bypass valves 29L and 29H close the flow path to block the flow of the heat medium through the heat medium bypass pipes 29L and 29H.

When the freezing prevention control is performed, the temperature of the heat medium detected by the heating temperature sensor T2 is lower than the set threshold in a state where the compressor 11 and the heat pump 24 are stopped and the refrigerant and the heat medium are not circulated. In this case, the flow path of the heating medium bypass valve 29H is opened and the heat pump 24 is operated. Opening the heat medium bypass valve 41 and operating the heat pump 24 causes the heat medium to heat the heat pump 24 and the heat exchanger 22 through the heat medium tubes H1 and H2 as indicated by the dotted arrows in the figure. ) And the bypass valve 41 in order to circulate. By circulating the heat medium as described above, the temperature of the heat medium passing through the heating heat medium tubes H1 and H2 becomes uniform. Moreover, since the temperature of the heat medium of the part whose temperature fell by the heat which flowed in from the heat pump 24 rises, freezing of the heat medium is suppressed. Here, it is preferable that the set threshold is set to a temperature slightly higher than the freezing temperature of the heat medium. That is, when the heat medium is water, the threshold value can be set to 3 ° C., which is slightly higher than 0 ° C. which is the freezing temperature.

In addition, after the heat medium starts to circulate, it is also possible to stop the operation of the heat pump 24 when the temperature of the heat medium detected by the heating temperature sensor T2 is equal to or higher than the set threshold value. Alternatively, the operation of the heat pump 24 may be stopped when the temperature of the heat medium detected by the heating temperature sensor T2 is equal to or higher than the set threshold value after a set time such as 5 minutes after the heat medium starts to circulate. It is possible.

Freezing prevention control is also performed also about the heat medium passing through the cooling heat medium tubes L1 and L2. When the temperature of the heat medium detected by the cooling temperature sensor T1 is lower than the set threshold value when the compressor 11 and the cooling pump 23 are stopped and the refrigerant and the heat medium do not circulate, the cooling bypass valve 42 The flow path of the gas is opened and the cooling pump 23 is operated. As the flow path of the cooling bypass valve 42 is opened and the cooling pump 23 is operated, as shown by the dotted line arrow in the drawing, the heat medium is cooled along the cooling heat medium pipes L1 and L2, and the cooling pump 23 is cooled. It circulates through the heat exchanger 21 and the freezing prevention bypass valve 42 in order. As the heat medium is circulated, the freezing of the heat medium passing through the cooling heat medium tubes L1 and L2 is suppressed. It is preferable that the threshold value set here is set to a temperature slightly higher than the freezing temperature of the heat medium similarly to the case of the heating heat medium tubes H1 and H2.

Moreover, after the heat medium starts to circulate, it is also possible to stop the cooling pump 23 again when the temperature of the heat medium detected by the cooling temperature sensor T1 becomes equal to or higher than the set threshold value. Alternatively, the cooling pump 23 may be stopped again when the temperature of the heating medium detected by the cooling temperature sensor T1 is equal to or higher than the set threshold value after a set time such as 5 minutes after the heating medium starts to circulate.

Next, water bypass defrost control of the heat pump system 1 according to the present embodiment will be described. Water bypass defrost control is performed in the heating mode, the heating center mode. In the water bypass defrost control, the outdoor heat exchanger 15 is defrosted by circulating the heat medium by bypassing the heating heat medium pipes H1 and H2 and the cooling heat medium pipes L1 and L2.

12 is a diagram when the heat pump system 1 performs water bypass defrost control. FIG. 12 shows a heat pump system 1 in which connecting bypass pipes B5 and B6 and connecting bypass valves 29L1 and 29H1 are added to the intermediate unit 20 shown in FIG. 1.

The connection bypass pipes B5 and B6 have a first connection bypass pipe B5 having one end connected to the heating heat medium supply pipe H1 and the other end connected to the cooling heat medium recovery pipe L2, and one end thereof cooled. A second connection bypass pipe B6 connected to the heat medium supply pipe L1 and the other end connected to the heated heat medium recovery pipe H2 is included.

Connection bypass pipes B5 and B6 have a first connection bypass valve 29L1 disposed in the first connection bypass pipe B5 to open and close a flow path of the first connection bypass pipe B5, and a second connection bypass pipe B5 and B6. Second connection bypass valves 29L1 and 29H1 are disposed in the connection bypass pipe B6 and open and close the flow path of the second connection bypass pipe B6.

The intermediate unit 20 is disposed in the cooling heat medium supply pipe L1 and is arranged in the cooling heat medium supply valve 29a for adjusting the amount of the heat medium supplied to the cooling unit 30L, and in the cooling heat medium recovery pipe L2. A cooling heat medium recovery valve 29b for adjusting the amount of heat medium recovered from 30L is included. In addition, the intermediate unit 20 is disposed in the heating heating medium supply pipe H1 and arranged in the heating heating medium supply valve 29c for adjusting the amount of the heating medium supplied to the heating unit 30H, and the heating heating medium recovery pipe H2. A heating heat medium recovery valve 29d for adjusting the amount of the heat medium recovered from the heating unit 30H is included.

Here, in the general state, the flow paths of the first connecting bypass valve 43 and the second connecting bypass valve 46 are both kept closed, and the cooling heat medium supply valve 29a, the cooling heat medium recovery valve 46, The heating heating medium supply valve 29d and the heating heating medium recovery valve 29c are both kept open.

The water bypass defrost control is a threshold at which the refrigerant temperature at the outlet side of the outdoor heat exchanger 15 is set when a defrost request of the outdoor heat exchanger 15 occurs while the heating mode or the heating center mode is being performed. If it is below the value, it switches to the cooling center mode. That is, the outdoor heat exchanger 15 and the heat exchanger 22 are operated as a condenser, and the cooling heat exchanger 21 is operated as an evaporator. Moreover, the flow path of the 1st connection bypass valve 43 and the 2nd connection bypass valve 46 is opened, and the cooling heat medium supply valve 29a, the cooling heat medium recovery valve 46, and the heating heat medium supply valve 29d are opened. Then, all the flow paths of the heating medium recovery valve 29c are closed.

When the cooling pump 23 and the heat pump 24 operate in this state, the heat medium transferred from the cooling heat exchanger 21 is heated by the second connection bypass valve 46 and the heating as indicated by the dotted arrows in the figure. Passed through the pump 24, it is delivered to the heat exchanger (22). The heat medium transferred to the heat exchanger 22 is heated by the refrigerant passing through the heat exchanger 22 to raise the temperature. The heat medium whose temperature is raised is passed to the cooling heat exchanger 21 through the first connection bypass valve 43 and the cooling pump 23. Cooled by the refrigerant in the cooling heat exchanger (21), the temperature is lowered.

By circulating the heat medium in this manner, the temperature of the heat medium circulating through the cooling heat medium pipes L1 and L2 and the heating heat medium pipes H1 and H2 is adjusted to maintain the set range. In addition, by circulating the heat medium, the amount of heat supplied from the refrigerant to the heat medium in the heating heat exchanger 22 and the amount of heat supplied from the heat medium to the refrigerant in the cooling heat exchanger 21 are controlled to be maintained equal. In this way, when the thermal equilibrium state is reached, the heat amount compressed by the compressor 11 and applied to the refrigerant according to the principle of the heat pump cycle is supplied to the outdoor heat exchanger 15. And the castle which generate | occur | produced on the surface of the outdoor heat exchanger 15 is removed. In addition, when the outdoor heat exchanger 15 is defrosted, there is no restriction on the heat capacity of the heat medium, so that defrosting can be stably performed even in a situation where the piping amount of the cooling heat medium pipes L1 and L2 or the heating heat medium pipes H1 and H2 is small. Can be.

In addition, by circulating the heat medium in this manner, regardless of the amount of the heat medium, defrosting of the outdoor heat exchanger 15 can be performed. In addition, since the temperature change of the heat medium is suppressed, the temperature change of the heating unit 30H and the cooling unit 30L is also suppressed.

Next, the control of the supercooling degree of the heat pump system 1 which concerns on a present Example is demonstrated. Supercooling control is performed in the heating mode.

FIG. 13: is a figure which shows the structural example of the heat pump system 1 in the case of performing supercooling degree control. FIG. 13 shows a heat pump system 1 in which a heating refrigerant temperature sensor T3, a heating refrigerant pressure sensor PS2, and a refrigerant flow rate regulating valve 26 are added to the intermediate unit 20 shown in FIG. 1.

The heating refrigerant temperature sensor T3 and the heating refrigerant pressure sensor PS2 are provided at the refrigerant outlet side of the heating heat exchanger 22, that is, the heating refrigerant pipe P6-2. In addition, a refrigerant flow rate control valve 26 is provided in the fifth refrigerant pipe P5 between the cooling heat exchanger 21 and the accumulator 17 as in FIG. 6.

In the supercooling degree control, the opening degree of the intermediate expansion valve 25 and the refrigerant flow rate control valve 26 are controlled so that the supercooling degree of the refrigerant on the outlet side of the heat exchanger 22 is maintained within a set range. That is, in the subcooling degree control, the opening degree of the intermediate expansion valve 25 and the refrigerant flow rate control valve 26 are controlled so that the subcooling degree becomes the value of the set target subcooling degree.

More specifically, the temperature of the refrigerant is detected by the heating refrigerant temperature sensor T3 arranged in the heating refrigerant pipe P6-2, and the heating refrigerant pressure sensor PS2 arranged in the heating refrigerant pipe P6-2. By this, the pressure of the refrigerant is detected. In addition, the detected pressure of the refrigerant is converted into a saturation temperature corresponding to the condensation temperature of the refrigerant. The subcooling degree is calculated based on the difference between the saturation temperature of the refrigerant and the temperature of the refrigerant detected by the temperature sensor T3. The opening degree of the intermediate expansion valve 25 and the refrigerant flow rate control valve 26 is controlled so that the calculated subcooling degree is within a set range.

In further detail, when the subcooling degree is larger than the set range, the intermediate expansion valve 25 is opened to close the flow path of the refrigerant flow rate control valve 26. In other words, when the subcooling degree is larger than the set range, the opening degree of the intermediate expansion valve 25 is increased and the opening degree of the refrigerant flow rate control valve 26 is controlled to be small.

When the subcooling degree SC is lower than the set range, the flow path of the intermediate expansion valve 25 is closed and the refrigerant flow rate control valve 26 is controlled to open the flow path. In other words, when the subcooling degree is lower than the set range, the opening degree of the intermediate expansion valve 25 is made small, and the opening degree of the refrigerant flow rate regulating valve 26 is controlled to be large.

When the amount of refrigerant charged into the refrigerant circuit in the heating mode is being performed, the degree of overcooling of the refrigerant on the outlet side of the heating heat exchanger 22 increases. Therefore, when the subcooling degree exceeds the set range, the intermediate processor C2 determines that the amount of refrigerant circuit refrigerant is excessive, thereby increasing the opening degree of the intermediate expansion valve 25 and at the same time opening the refrigerant flow rate control valve 26. Make it smaller. Under such control, the refrigerant in the refrigerant circuit is stored in the cooling heat exchanger 21 which is not used as the heat exchanger in the heating mode. When the excess refrigerant in the refrigerant circuit is stored in the cooling heat exchanger 21, the subcooling degree SC is lowered and maintained within the set range.

In addition, when the amount of refrigerant charged into the refrigerant circuit is insufficient while the heating mode is being performed, the supercooling degree of the refrigerant at the outlet side of the heating heat exchanger 22 is lowered. Therefore, when the subcooling degree is lower than the set range, the intermediate processor C2 determines that the amount of refrigerant in the refrigerant circuit is insufficient, thereby reducing the opening degree of the intermediate expansion valve 25 and simultaneously opening the refrigerant flow rate control valve 26. To increase. By such control, the refrigerant stored in the cooling heat exchanger 21 is supplied to the refrigerant circuit. When the refrigerant of the cooling heat exchanger 21 is supplied to the refrigerant circuit, the supercooling degree rises and is maintained within the set range.

As described above, the heat pump system 1 calculates the supercooling degree SC of the outlet refrigerant of the heating heat exchanger 22, and adjusts the intermediate expansion valve 25 and the refrigerant flow rate so that the calculated supercooling degree is maintained within a set range. The opening degree of the valve 26 is controlled. By controlling the opening degree of the intermediate expansion valve 25 and the refrigerant flow rate control valve 26 on the basis of the subcooling degree, the refrigerant flow rate of the refrigerant circuit is adjusted, and the warmth is stably supplied to the heating unit 30H.

In the above embodiments, the outdoor unit 10 and the intermediate unit 20 are housed in separate housings, but it is also possible for the outdoor unit 10 and the intermediate unit 20 to be housed in one housing.

In addition, the program for realizing the embodiments of the present invention can be provided not only by the communication means but also stored and provided in various recording media such as a CD-ROM.

The scope of the present invention is not limited to the specific embodiments described above. Various other embodiments which can be modified or modified by those skilled in the art without departing from the gist of the technical spirit of the present invention specified in the claims will also belong to the scope of the present invention.

Claims (14)

1. An outdoor unit disposed in an outdoor space,

   A plurality of heat load units supplied with cold and warm air,

   An intermediate unit disposed between the outdoor unit and the plurality of thermal load units,

   And the intermediate unit is connected to the outdoor unit through a refrigerant pipe through which a refrigerant passes, and is connected to the plurality of heat load units through a heat medium pipe through which a heat medium passes.
2. The method of claim 1,

   The plurality of heat load units includes a cooling unit that receives and uses cold air and a heating unit that receives and uses warm air.
3. The method of claim 2,

   The outdoor unit includes a compressor for compressing a refrigerant, an outdoor heat exchanger for allowing the refrigerant to heat exchange with outdoor air, a four-way valve for guiding the refrigerant discharged from the compressor to one of the outdoor heat exchanger and the intermediate unit, and the refrigerant to be decompressed and expanded. And an outdoor expansion valve.
4. The method of claim 3, wherein

   The intermediate unit may include a heat exchanger for allowing heat exchange between the heat medium and the refrigerant transferred from the cooling unit, a heat exchanger for heat exchange between the heat medium and the refrigerant transferred from the heating unit, and an intermediate expansion valve for expanding the refrigerant under reduced pressure. Pump system.
5. The method of claim 4, wherein

   A first refrigerant pipe guiding the refrigerant discharged from the compressor to the four-way valve;

   A second refrigerant pipe guiding a refrigerant from the four-way valve to the outdoor heat exchanger;

   A third refrigerant pipe guiding a refrigerant from the four-way valve to the heating heat exchanger;

   A fourth refrigerant pipe from the four-way valve to the suction side of the compressor;

   A fifth refrigerant pipe guiding the refrigerant from the cooling heat exchanger to the suction side of the compressor;

   A sixth refrigerant pipe connected to the outdoor heat exchanger and branched in two to form a cooling refrigerant pipe connected to the cooling heat exchanger and the other to form a heating refrigerant pipe connected to the heating heat exchanger;

   A seventh refrigerant pipe connecting the second refrigerant pipe and the third refrigerant pipe;

   And an opening / closing valve disposed in the seventh refrigerant pipe to selectively flow the refrigerant through the seventh refrigerant pipe.
6. The method of claim 4, wherein

   A fifth refrigerant pipe guiding the refrigerant from the cooling heat exchanger to the suction side of the compressor;

   A pressure sensor for detecting a pressure at a refrigerant outlet side of the cooling heat exchanger;

   And a refrigerant flow rate control valve disposed in the fifth refrigerant pipe and controlled to have an opening degree such that the pressure detected by the pressure sensor becomes a value within a setting range.
7. The method of claim 4, wherein

   A fifth refrigerant pipe guiding the refrigerant from the cooling heat exchanger to the suction side of the compressor;

   A cooling temperature sensor detecting a temperature of the heat medium cooled by the cooling heat exchanger;

   A refrigerant bypass pipe branched from the cooling refrigerant pipe and connected to the fifth refrigerant pipe;

   And a bypass expansion valve disposed in the refrigerant bypass pipe to open a flow path of the refrigerant bypass pipe when the temperature of the heat medium detected by the cooling temperature sensor is lower than a predetermined threshold value.
8. The method of claim 4, wherein

   A defrost bypass tube having one end connected to a third refrigerant pipe guiding the refrigerant from the four-way valve to the heating heat exchanger and the other end connected to a fifth refrigerant pipe at the suction side of the compressor;

   And a refrigerant flow path switching valve disposed in the defrost bypass pipe to open a flow path of the defrost bypass pipe when a defrost demand occurs in the outdoor heat exchanger.
9. The method of claim 4, wherein

   A cooling heat medium supply pipe for supplying the heat medium cooled by the cooling heat exchanger to the cooling unit;

   A cooling heat medium recovery pipe passing through the cooling unit and transferring the heat medium having absorbed heat to the cooling heat exchanger;

   A heating heating medium supply pipe for supplying the heating medium cooled by the heating heat exchanger to the heating unit;

   And a heating heat medium recovery pipe passing through the heating unit and dissipating heat to the heating heat exchanger.
10. The method of claim 9,

    A cooling pump disposed in the cooling heat medium recovery pipe;

    And a heat pump disposed in said heated heat medium recovery pipe.
11. The method of claim 9,

    A cooling heat medium bypass pipe having one end connected to the cooling heat medium supply pipe and the other end connected to the cooling heat medium recovery pipe,

    A heating heat medium bypass pipe having one end connected to the heating heat medium supply pipe and the other end connected to the heating heat medium recovery pipe,

    A cooling heat medium bypass valve disposed in the cooling heat medium bypass pipe to open and close a flow path of the cooling heat medium bypass pipe;

    And a heating heating medium bypass valve disposed in the heating heating medium bypass pipe to open and close a flow path of the heating heating medium bypass pipe.
12. The method of claim 9,

    A first connecting bypass pipe having one end connected to the heating heat medium supply pipe and the other end connected to the cooling heat medium recovery pipe;

    A second connecting bypass pipe having one end connected to the cooling heat medium supply pipe and the other end connected to the heating heat medium recovery pipe;

    A first connection bypass valve disposed in the first connection bypass pipe and configured to open and close a flow path of the first connection bypass pipe;

    And a second connection bypass valve disposed in the second connection bypass pipe to open and close a flow path of the second connection bypass pipe.
13. The method of claim 9,

    A cooling heat medium supply valve disposed in the cooling heat medium supply pipe to adjust an amount of the heat medium supplied to the cooling unit;

    A cooling heat medium recovery valve disposed in the cooling heat medium recovery pipe to adjust an amount of the heat medium recovered from the cooling unit;

    A heating heat medium supply valve disposed in the heating heat medium supply pipe to adjust an amount of the heat medium supplied to the heating unit;

    And a heating heat medium recovery valve disposed in the heating heat medium recovery pipe to adjust an amount of the heat medium recovered from the heating unit.
14. The method of claim 5, wherein

    A heating refrigerant temperature sensor disposed at a refrigerant discharge side of the heating heat exchanger and detecting a temperature of the refrigerant;

    A heating refrigerant pressure sensor disposed at a refrigerant discharge side of the heating heat exchanger to detect a pressure of the refrigerant;

    And a refrigerant flow rate control valve disposed in the fifth refrigerant pipe and configured to adjust an opening degree according to a supercooling degree of the refrigerant outlet side of the heating heat exchanger.

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