JP5314770B2 - Heat source unit power consumption apportioning system - Google Patents

Abstract

Disclosed is a heat source unit power consumption prorating system (10) having a heat quantity usage calculation unit (19a), a corrected heat quantity calculation unit (19b), and an electric power prorating unit (19c). The heat quantity usage unit (19a) calculates a utilization-side heat quantity usage in utilization units (5a, 5b) on the basis of the flow rate and the temperature of a water medium. The corrected heat quantity calculation unit (19b) corrects the utilization-side heat quantity usage in the respective utilization units (5a, 5b) on the basis of the refrigeration cycle characteristics of utilization-side refrigerant circuits (50a, 50b), which are estimated by a heat source-side condensation temperature, or a utilization-side evaporation temperature and a water medium outlet temperature. The electric power prorating unit (19c) prorates the power consumption of a heat source unit (2) in accordance with the corrected utilization-side heat quantity usage.

Description

  The present invention relates to a heat source unit power consumption apportioning system, and more particularly to a heat source unit power apportioning system in a heat pump system configured by connecting a plurality of utilization units that perform heating operation of an aqueous medium to a heat source unit using a dual refrigeration cycle. About.

  Conventionally, there is a heat pump type hot water heater shown in Patent Document 1 (Japanese Patent Laid-Open No. 2003-314838). This heat pump type hot water heating apparatus (heat pump system) can perform heating operation (heating operation) by heating water using a heat pump cycle and supplying the obtained hot water to a floor heating panel. . More specifically, this heat pump system supplies hot water having a refrigerant-to-water heat exchanger (use side heat exchanger) to an outdoor unit (heat source unit) having a compressor and an evaporator (heat source side heat exchanger). In this heat pump system, it is possible to obtain hot water by heating water by the heat radiation of the refrigerant in the use side heat exchanger.

Since the conventional heat pump system has high environmental performance as compared with a combustion type hot water heater such as a boiler, its wide use is attracting attention. For example, in terms of function, it is desirable to provide a system that can obtain a high-temperature aqueous medium, or a system that can perform heating operation for each user by connecting a plurality of usage units to a heat source unit in an apartment house or the like. It is rare.
On the other hand, it is conceivable that a plurality of utilization units are connected to the heat source unit and the utilization unit is configured to perform a heating operation of the aqueous medium using a dual refrigeration cycle.
However, in collective housing, buildings, and the like, it is necessary to jointly share the power consumption of the heat source unit that is provided in common among a plurality of utilization units. However, since the capacity, usage frequency, set temperature, etc. of the utilization unit differ depending on the user, a dedicated heat source unit power consumption apportioning system is required for each user to share the power consumption of the heat source unit fairly.

As such a heat source unit power consumption apportioning system, the use heat amount in each use unit is calculated from the flow rate and temperature of the aqueous medium in each use unit, and the power consumption of the heat source unit is apportioned according to the use heat amount of each use unit. A method can be considered.
However, another refrigerant circuit (use side refrigerant circuit) constituting the binary refrigeration cycle is provided in the utilization unit that performs the heating operation of the aqueous medium using the binary refrigeration cycle. For this reason, the effect of the amount of heat borne by the use side refrigerant circuit of each use unit is taken into account only by apportioning the power consumption of the heat source unit according to the amount of heat used calculated from the flow rate and temperature of the aqueous medium in each use unit. It is difficult to appropriately apportion the power consumption of the heat source unit.
An object of the present invention is to appropriately apportion power consumption of a heat source unit in a heat pump system configured by connecting a plurality of utilization units that perform heating operation of an aqueous medium using a dual refrigeration cycle to the heat source unit. There is to do.

  The heat source unit power consumption apportioning system according to the first aspect of the present invention is applied to a heat pump system configured by connecting a heat source unit and a plurality of utilization units. The heat source unit includes a heat source side compressor that compresses the heat source side refrigerant and a heat source side heat exchanger. The usage unit has a first usage-side heat exchanger. A heat source side refrigerant circuit is configured by connecting a plurality of utilization units to the heat source unit. Further, the usage unit is provided with a usage-side compressor that compresses the usage-side refrigerant, and a refrigerant-water heat exchanger that functions as a radiator for the usage-side refrigerant and that can perform a heating operation to heat the aqueous medium. It has been. And the utilization side refrigerant circuit is comprised by the utilization side compressor, the refrigerant | coolant-water heat exchanger, and the 1st utilization side heat exchanger. And the heat-source unit power consumption apportioning system has a use calorie | heat amount calculating part, a correction | amendment calorie | heat amount calculating part, and an electric power apportioning part. The use heat amount calculation unit calculates the use side use heat amount in each use unit from the flow rate and temperature of the aqueous medium. The correction calorific value calculation unit corrects the use side use heat amount in each use unit based on the refrigeration cycle characteristics of each use side refrigerant circuit assumed from the heat source side condensation temperature or use side evaporation temperature and the aqueous medium outlet temperature. To do. Here, the heat source side condensing temperature is a temperature corresponding to the saturation temperature of the heat source side refrigerant in the first usage side heat exchanger functioning as a radiator of the heat source side refrigerant and an evaporator of the usage side refrigerant. The use side evaporation temperature is a temperature corresponding to the saturation temperature of the use side refrigerant in the first use side heat exchanger. The aqueous medium outlet temperature is the temperature of the aqueous medium at the outlet of the refrigerant-water heat exchanger. The power apportioning unit apportions the power consumption of the heat source unit according to the corrected usage-side use heat amount.

In this heat source unit power consumption apportioning system, each use side refrigerant assumed from the state quantities corresponding to the low pressure and high pressure in the refrigeration cycle of the use side refrigerant circuit, that is, the heat source side condensation temperature or use side evaporation temperature, and the aqueous medium outlet temperature. Based on the refrigeration cycle characteristics of the circuit, the usage-side heat consumption is corrected. For this reason, it is possible to obtain the corrected usage side usage heat amount in consideration of the influence of the heat amount borne in the usage side refrigerant circuit mainly composed of the work of the usage side compressor.
As a result, in this heat source unit power consumption apportioning system, the use side heat amount calculated from the flow rate and temperature of the aqueous medium in each use unit is used, but the influence of the heat amount borne by the use side refrigerant circuit is not affected. Can be considered. Therefore, in this heat source unit power consumption apportioning system, the power consumption of the heat source unit can be apportioned appropriately.

The heat source unit power consumption apportioning system according to the second aspect of the present invention is the heat source unit power apportioning system according to the first aspect, wherein the correction calorific value calculation unit is obtained based on the heat source side condensation temperature or the use side evaporation temperature. Correction is performed by multiplying the use-side use heat amount by the first correction coefficient and the second correction coefficient obtained based on the aqueous medium outlet temperature.
In this heat source unit power consumption apportioning system, the correction coefficients relating to the low pressure and high pressure states in the refrigeration cycle of the use side refrigerant circuit are prepared as two correction coefficients, the first correction coefficient and the second correction coefficient. Accurate apportioning in consideration of the refrigeration cycle characteristics of the refrigerant circuit can be performed.

The heat source unit power consumption apportioning system according to the third aspect of the present invention is the heat source unit power consumption apportioning system according to the first or second aspect, in which the heat pump system has a control unit for performing operation control. The control unit controls the operating capacity of the heat source side compressor so that the heat source side condensation temperature becomes a predetermined target heat source side condensation temperature.
In this heat source unit power consumption apportioning system, the control unit controls the operating capacity of the heat source side compressor so that the heat source side condensation temperature becomes a predetermined target heat source side condensation temperature. Evaporation temperature is stable. For this reason, since the use side use calorie | heat amount can be correct | amended in the state where the low pressure state in the refrigerating cycle of the use side refrigerant circuit was stabilized, accurate apportioning can be performed.

  The heat source unit power consumption apportioning system according to the fourth aspect of the present invention is the heat source unit power apportioning system according to any of the first to third aspects, wherein at least one of the plurality of utilization units is evaporation of the heat source side refrigerant. The second utilization side heat exchanger that can perform the cooling operation for cooling the aqueous medium is further provided. When the cooling operation and the heating operation are performed simultaneously in the usage unit having the second usage side heat exchanger, the corrected usage side usage heat amount in the usage unit is calculated as follows. First, when the cooling operation and the heating operation are simultaneously performed in the usage unit having the second usage side heat exchanger, the usage heat amount calculation unit calculates the usage side usage heat amount and heating of the cooling operation from the flow rate and temperature of the aqueous medium. Calculate the amount of heat used on the usage side of operation. Next, the corrected calorific value calculation unit corrects the usage-side usage heat amount of the heating operation based on the refrigeration cycle characteristics of each usage-side refrigerant circuit assumed from the heat source side condensation temperature or the usage-side evaporation temperature and the aqueous medium outlet temperature. To do. And a correction | amendment calorie | heat amount calculating part further correct | amends utilization side use calorie | heat amount based on the performance expected value of the heat source side refrigerant circuit at the time of assuming that only the cooling operation or the heating operation was performed. Further, the corrected calorific value calculation unit compares the usage-side usage heat amount of the cooling operation with the usage-side usage heat amount of the heating operation after correcting the usage-side usage heat amount based on the expected performance value, and the cooling operation obtained by this comparison. The larger one of the use side use heat amount and the use side use heat amount of the heating operation is set as the use side use heat amount in the use unit having the second use side heat exchanger.

When a utilization unit that can be operated simultaneously with the cooling operation and the heating operation by having the second utilization side heat exchanger is used, the utilization side use heat amount of the utilization operation and the utilization side use heat amount of the heating operation are used. Need to be considered.
However, when the utilization unit enters an operation state in which the cooling operation and the heating operation are performed at the same time, there is an effect of exhaust heat recovery between the utilization unit performing the cooling operation and the utilization unit performing the heating operation. For this reason, it is necessary for the heat source unit power consumption apportioning system to consider the influence of such exhaust heat recovery, otherwise it is difficult to apportion the power consumption of the heat source unit appropriately.
Therefore, in this heat source unit power consumption apportioning system, each of the use side use heat amount of the heating operation calculated from the flow rate and temperature of the aqueous medium is assumed from the heat source side condensation temperature or the use side evaporation temperature and the aqueous medium outlet temperature. Based on the refrigeration cycle characteristics of the use side refrigerant circuit, the use side use heat amount of the heating operation is corrected. Thereby, the influence of the calorie | heat amount burdened in a utilization side refrigerant circuit can be considered. And based on the performance expectation value when it is assumed that only the cooling operation or the heating operation is performed, the use side use heat amount is corrected. As a result, the usage-side heat consumption of the heating operation can take into account the effects when the cooling operation is performed at the same time, and the heating operation is performed simultaneously for the usage-side heat consumption of the cooling operation. You can consider the impact of Then, the usage-side usage heat amount of the cooling operation is compared with the usage-side usage heat amount of the heating operation, and the larger one is set as the usage-side usage heat amount. For this reason, the utilization side use heat amount in this utilization unit can be obtained as a value in consideration of the effect of exhaust heat recovery.

  As a result, in this heat source unit power consumption apportioning system, even if a utilization unit capable of operating the cooling operation and the heating operation simultaneously by adopting the second utilization side heat exchanger is employed, Considering the effect of recovery, the power consumption of the heat source unit can be apportioned.

1 is a schematic configuration diagram of a heat pump system to which a heat source unit power consumption apportioning system according to a first embodiment of the present invention is applied. It is a system configuration figure of the heat source unit power consumption apportioning system of a 1st embodiment concerning the present invention. It is a schematic block diagram of the heat medium measuring aqueous medium sensor. It is a cycle diagram of a use side refrigerant circuit and a heat source side refrigerant circuit. It is a schematic block diagram of the heat pump system to which the heat source unit power consumption apportioning system concerning 2nd Embodiment of this invention was applied. It is a system block diagram of the heat-source unit power consumption apportioning system of 2nd Embodiment concerning this invention. It is a figure which shows the expected value of a coefficient of performance at the time of assuming that only the cooling operation or the heating operation was performed. It is a cycle diagram of the heat source side refrigerant circuit when the utilization unit which is performing cooling operation and heating operation simultaneously in one utilization unit, and the utilization unit which is performing cooling operation are mixed. It is a cycle diagram of the heat source side refrigerant circuit when it is assumed that the utilization unit performing the heating operation alone performs only the heating operation. It is a cycle diagram of the heat source side refrigerant circuit when it is assumed that the utilization unit performing the cooling operation alone performs only the cooling operation.

Hereinafter, an embodiment of a heat pump system to which a heat source unit power consumption apportioning system according to the present invention is applied will be described with reference to the drawings.
(1) First Embodiment <Configuration of Heat Pump System>
-Overall-
FIG. 1 is a schematic configuration diagram of a heat pump system 1 to which a heat source unit power consumption apportioning system according to a first embodiment of the present invention is applied. The heat pump system 1 is a device capable of performing a heating operation (heating operation) using a vapor compression heat pump cycle.
The heat pump system 1 mainly includes a heat source unit 2, a plurality of (two in FIG. 1) use units 5a and 5b, a liquid refrigerant communication pipe 13, a gas refrigerant communication pipe 14, and aqueous medium heating units 75a and 75b. (Aqueous medium utilization device) and aqueous medium communication pipes 15a, 16a, 15b, and 16b. The heat source unit 2 and the utilization units 5a and 5b are connected via the refrigerant communication tubes 13 and 14 to constitute the heat source side refrigerant circuit 20. The usage units 5a and 5b constitute usage-side refrigerant circuits 50a and 50b. The utilization units 5a and 5b and the aqueous medium heating units 75a and 75b are connected via aqueous medium communication pipes 15a, 16a, 15b, and 16b to constitute aqueous medium circuits 70a and 70b. In the heat source side refrigerant circuit 20, HFC-410A which is a kind of HFC type refrigerant is sealed as a heat source side refrigerant. Further, HFC-134a, which is a kind of HFC refrigerant, is sealed in the use side refrigerant circuits 50a and 50b as the use side refrigerant. In addition, as a use side refrigerant | coolant, from a viewpoint that the refrigerant | coolant advantageous to a high temperature refrigerating cycle is used, the pressure corresponding to saturation gas temperature 65 degreeC is 2.8 Mpa or less at the maximum at a gauge pressure, Preferably, it is 2.0 Mpa. The following refrigerants are preferably used. HFC-134a is a kind of refrigerant having such saturation pressure characteristics. Further, water as an aqueous medium circulates in the aqueous medium circuits 70a and 70b.

-Heat source unit-
The heat source unit 2 is installed outdoors (for example, an apartment house or a rooftop of a building). The heat source unit 2 is connected to the utilization units 5 a and 5 b via the refrigerant communication tubes 13 and 14 and constitutes a part of the heat source side refrigerant circuit 20.
The heat source unit 2 mainly includes a heat source side compressor 21, an oil separation mechanism 22, a heat source side switching mechanism 23, a heat source side heat exchanger 26, a heat source side expansion valve 28, a suction return pipe 29, and a supercooling. A heat source side accumulator 32, a liquid side closing valve 33, and a gas side closing valve 34.
The heat source side compressor 21 is a mechanism that compresses the heat source side refrigerant. Here, as the heat source side compressor 21, a rotary type or scroll type positive displacement compression element (not shown) accommodated in a casing (not shown) is also used. A hermetic compressor driven by a machine motor 21a is employed. The heat source side compressor motor 21a can change the rotation speed (that is, the operating frequency) by an inverter device (not shown), thereby enabling capacity control of the heat source side compressor 21.

The oil separation mechanism 22 is a mechanism for separating the refrigerating machine oil contained in the heat source side refrigerant discharged from the heat source side compressor 21 and returning it to the suction of the heat source side compressor 21. The oil separation mechanism 22 mainly includes an oil separator 22a provided in the heat source side discharge pipe 21b of the heat source side compressor 21, and an oil that connects the oil separator 22a and the heat source side suction pipe 21c of the heat source side compressor 21. And a return pipe 22b. The oil separator 22a is a device that separates refrigeration oil contained in the heat source side refrigerant discharged from the heat source side compressor 21. The oil return pipe 22 b has a capillary tube, and is a refrigerant pipe that returns the refrigeration oil separated from the heat source side refrigerant in the oil separator 22 a to the heat source side suction pipe 21 c of the heat source side compressor 21.
The heat source side switching mechanism 23 is a heat source side heat radiation operation state in which the heat source side heat exchanger 26 functions as a heat source side refrigerant radiator, and a heat source side evaporation operation state in which the heat source side heat exchanger 26 functions as an evaporator of the heat source side refrigerant. It is a four-way switching valve that can be switched between. The heat source side switching mechanism 23 is connected to the heat source side discharge pipe 21b, the heat source side suction pipe 21c, the heat source side gas refrigerant pipe 24 connected to the gas side of the heat source side heat exchanger 26, and the gas side closing valve 34. The heat source side gas refrigerant pipe 25 is connected. The heat source side switching mechanism 23 can perform switching (corresponding to the heat source side heat radiation operation state, refer to the solid line of the heat source side switching mechanism 23 in FIG. 1) for communicating the heat source side discharge pipe 21b and the heat source side gas refrigerant pipe 24. Is possible. Further, the heat source side switching mechanism 23 performs switching (corresponding to the heat source side evaporation operation state, refer to the broken line of the heat source side switching mechanism 23 in FIG. 1) for communicating the heat source side gas refrigerant pipe 24 and the heat source side suction pipe 21c. It is possible. The heat source side switching mechanism 23 is not limited to the four-way switching valve, and has a function of switching the flow direction of the heat source side refrigerant as described above, for example, by using a combination of a plurality of electromagnetic valves. You may comprise so that it may have.

  The heat source side heat exchanger 26 is a heat exchanger functioning as a heat source side refrigerant radiator or an evaporator by exchanging heat between the heat source side refrigerant and outdoor air, and a heat source side liquid refrigerant tube 27 is provided on the liquid side thereof. Are connected, and the heat source side gas refrigerant pipe 24 is connected to the gas side thereof. The heat source side liquid refrigerant pipe 27 guides the heat source side refrigerant out of the heat source unit 2 (more specifically, the liquid refrigerant communication pipe 13) from the outlet of the heat source side heat exchanger 26 that functions as a heat source side refrigerant radiator. It is a refrigerant pipe for. The heat source side liquid refrigerant tube 27 is also a refrigerant tube for introducing the heat source side refrigerant from the outside of the heat source unit 2 to the inlet of the heat source side heat exchanger 26 that functions as an evaporator of the heat source side refrigerant. The outdoor air that exchanges heat with the heat source side refrigerant in the heat source side heat exchanger 26 is supplied by a heat source side fan 36 driven by a heat source side fan motor 37. The heat source side fan motor 37 can change the rotation speed (that is, the operating frequency) by an inverter device (not shown), and thereby the air volume control of the heat source side fan 36 is possible.

The heat source side expansion valve 28 is an electric expansion valve that depressurizes the heat source side refrigerant flowing through the heat source side heat exchanger 26, and is provided in the heat source side liquid refrigerant pipe 27.
The suction return pipe 29 is a refrigerant pipe that branches a part of the heat source side refrigerant flowing through the heat source side liquid refrigerant pipe 27 and returns it to the suction of the heat source side compressor 21, and here, one end thereof is the heat source side liquid refrigerant pipe 27. The other end is connected to the heat source side suction pipe 21c. The suction return pipe 29 is provided with a suction return expansion valve 30 whose opening degree can be controlled. The suction return expansion valve 30 is an electric expansion valve.
The subcooler 31 heats the refrigerant flowing through the heat source side liquid refrigerant pipe 27 and the heat source side refrigerant flowing through the suction return pipe 29 (more specifically, the heat source side refrigerant after being decompressed by the suction return expansion valve 30). It is a heat exchanger that performs exchange.

The heat source side accumulator 32 is provided in the heat source side suction pipe 21c, and temporarily accumulates the refrigerant circulating in the heat source side refrigerant circuit 20 before being sucked into the heat source side compressor 21 from the heat source side suction pipe 21c. It is a container.
The liquid side closing valve 33 is a valve provided at a connection portion between the heat source side liquid refrigerant pipe 27 and the liquid refrigerant communication pipe 13. The gas side shut-off valve 34 is a valve provided at a connection portion between the heat source side gas refrigerant pipe 25 and the gas refrigerant communication pipe 14.
The heat source unit 2 is provided with various sensors. Specifically, the heat source unit 2 includes a heat source side suction pressure sensor 41, a heat source side discharge pressure sensor 42, a heat source side suction temperature sensor 43, a heat source side discharge temperature sensor 44, and a heat source side heat exchange gas side temperature. A sensor 45, a heat source side heat exchange liquid side temperature sensor 46, and an outside air temperature sensor 47 are provided. The heat source side suction pressure sensor 41 is a pressure sensor that detects the heat source side suction pressure Ps1 that is the pressure of the heat source side refrigerant in the suction of the heat source side compressor 21. The heat source side discharge pressure sensor 42 is a pressure sensor that detects the heat source side discharge pressure Pd <b> 1 that is the pressure of the heat source side refrigerant in the discharge of the heat source side compressor 21. The heat source side suction temperature sensor 43 is a temperature sensor that detects a heat source side suction temperature Ts1 that is the temperature of the heat source side refrigerant in the suction of the heat source side compressor 21. The heat source side discharge temperature sensor 44 is a temperature sensor that detects the heat source side discharge temperature Td <b> 1 that is the temperature of the heat source side refrigerant in the discharge of the heat source side compressor 21. The heat source side heat exchange gas side temperature sensor 45 is a temperature sensor that detects a heat source side heat exchange gas side temperature Thg that is the temperature of the refrigerant on the gas side of the heat source side heat exchanger 26. The heat source side heat exchange liquid side temperature sensor 46 is a temperature sensor that detects a heat source side heat exchange liquid side temperature Thl that is the temperature of the heat source side refrigerant on the liquid side of the heat source side heat exchanger 26. The outside air temperature sensor 47 is a temperature sensor that detects the outside air temperature To. Further, the heat source unit 2 includes a heat source side control unit 49 that controls the operation of each unit constituting the heat source unit 2. The heat source side control unit 49 includes a microcomputer and a memory for controlling the heat source unit 2. The heat source side control unit 49 can exchange control signals and the like with use side control units 69a and 69b of use units 5a and 5b described later.

−Liquid refrigerant connection tube−
The liquid refrigerant communication tube 13 is connected to the heat source side liquid refrigerant tube 27 via a liquid side closing valve 33. The liquid refrigerant communication tube 13 may lead the heat source side refrigerant out of the heat source unit 2 from the outlet of the heat source side heat exchanger 26 that functions as a heat source side refrigerant radiator when the heat source side switching mechanism 23 is in the heat source side heat radiation operation state. Possible refrigerant pipe. Further, the liquid refrigerant communication tube 13 introduces the heat source side refrigerant from the outside of the heat source unit 2 to the inlet of the heat source side heat exchanger 26 that functions as an evaporator of the heat source side refrigerant when the heat source side switching mechanism 23 is in the heat source side evaporation operation state. It is also a possible refrigerant pipe.
-Gas refrigerant communication tube-
The gas refrigerant communication pipe 14 is connected to the heat source side gas refrigerant pipe 25 via a gas side closing valve 34. The gas refrigerant communication pipe 14 is a refrigerant pipe through which the heat source side switching mechanism 23 can introduce the heat source side refrigerant from outside the heat source unit 2 to the suction of the heat source side compressor 21 in the heat source side heat radiation operation state. The gas refrigerant communication tube 14 is also a refrigerant tube capable of leading the heat source side refrigerant out of the heat source unit 2 from the discharge of the heat source side compressor 21 when the heat source side switching mechanism 23 is in the heat source side evaporation operation state.

-Usage unit-
The usage units 5a and 5b are installed indoors (for example, each door of an apartment house or each section of a building). The utilization units 5 a and 5 b are connected to the heat source unit 2 via the refrigerant communication tubes 13 and 14 and constitute a part of the heat source side refrigerant circuit 20. Further, the use units 5a and 5b constitute use-side refrigerant circuits 50a and 50b. Furthermore, the utilization units 5a and 5b are connected to the aqueous medium heating units 75a and 75b via the aqueous medium communication pipes 15a, 16a, 15b and 16b, and constitute part of the aqueous medium circuits 70a and 70b. . The configuration of the usage unit 5b is the same as the configuration of the usage unit 5a. Therefore, here, only the configuration of the usage unit 5a will be described, and the configuration of the usage unit 5b will be described by adding the subscript “b” instead of the subscript “a” of the reference numeral indicating each part of the usage unit 5a. The description of is omitted.

The use unit 5a mainly includes a first use side heat exchanger 51a, a first use side expansion valve 52a, a use side compressor 55a, a refrigerant-water heat exchanger 57a, and a refrigerant-water heat exchange side expansion valve. 58a, a use-side accumulator 59a, and a circulation pump 71a.
The first usage-side heat exchanger 51a is a heat exchanger that functions as a heat-source-side refrigerant radiator by performing heat exchange between the heat-source-side refrigerant and the usage-side refrigerant. The use side liquid refrigerant pipe 53a is connected to the liquid side of the flow path through which the heat source side refrigerant flows in the first usage side heat exchanger 51a, and the flow path through which the heat source side refrigerant in the first usage side heat exchanger 51a flows. On the gas side, a use side gas refrigerant pipe 54a is connected. Further, a cascade side liquid refrigerant pipe 66a is connected to the liquid side of the flow path through which the usage side refrigerant flows of the first usage side heat exchanger 51a, and the usage side refrigerant of the first usage side heat exchanger 51a flows. A cascade side gas refrigerant pipe 67a is connected to the gas side of the flow path. The use side liquid refrigerant pipe 53a takes the heat source side refrigerant from the outlet of the first use side heat exchanger 51a functioning as a heat source side refrigerant radiator to the outside of the use unit 5a (more specifically, the liquid refrigerant communication pipe 13). This is a refrigerant pipe for deriving. The use side gas refrigerant pipe 54a passes the heat source side refrigerant from the outside of the use unit 5a (more specifically, the gas refrigerant communication pipe 14) to the inlet of the first use side heat exchanger 51a that functions as a heat radiator for the heat source side refrigerant. It is a refrigerant pipe for introducing. A refrigerant-water heat exchanger 57a is connected to the cascade side liquid refrigerant pipe 66a, and a use side compressor 55a is connected to the cascade side gas refrigerant pipe 67a.

The first use side expansion valve 52a is an electric expansion valve capable of changing the flow rate of the heat source side refrigerant flowing through the first use side heat exchanger 51a by performing opening degree control, and the use side liquid refrigerant pipe 53a. Is provided.
The use side compressor 55a is a mechanism that compresses the use side refrigerant. Here, as the use side compressor 55a, a rotary type compression element (not shown) such as a rotary type or a scroll type accommodated in a casing (not shown) is also used. A hermetic compressor driven by a machine motor 56a is employed. The use-side compressor motor 56a can change the rotation speed (that is, the operating frequency) by an inverter device (not shown), thereby enabling capacity control of the use-side compressor 55a. Further, a cascade side discharge pipe 60a is connected to the discharge of the use side compressor 55a, and a cascade side gas refrigerant pipe 67a is connected to the suction of the use side compressor 55a.

  The refrigerant-water heat exchanger 57a is a heat exchanger that functions as a heat radiator for the use-side refrigerant by performing heat exchange between the use-side refrigerant and the aqueous medium. A cascade-side liquid refrigerant tube 66a is connected to the liquid side of the flow path through which the use-side refrigerant flows in the refrigerant-water heat exchanger 57a, and the gas in the flow path through which the use-side refrigerant in the refrigerant-water heat exchanger 57a flows. The cascade side gas refrigerant pipe 67a is connected to the side. Further, a use side water inlet pipe 73a is connected to the inlet side of the flow path through which the aqueous medium of the refrigerant-water heat exchanger 57a flows, and the outlet of the flow path through which the aqueous medium of the refrigerant-water heat exchanger 57a flows. The use side water outlet pipe 74a is connected to the side. The use side water inlet pipe 73a introduces the aqueous medium from the outside of the usage unit 5a (more specifically, the aqueous medium communication pipe 15a) to the inlet of the refrigerant-water heat exchanger 57a that functions as a heater for the aqueous medium. Is an aqueous medium tube. The usage-side water outlet pipe 74a leads the aqueous medium out of the utilization unit 5a (more specifically, the aqueous medium communication pipe 16a) from the outlet of the refrigerant-water heat exchanger 57a that functions as an aqueous medium heater. Is an aqueous medium tube.

The refrigerant-water heat exchange side expansion valve 58a is an electric expansion valve capable of changing the flow rate of the use-side refrigerant flowing through the refrigerant-water heat exchanger 57a by performing opening degree control, and is a cascade-side liquid refrigerant pipe. 66a.
The use-side accumulator 59a is provided in the cascade-side gas refrigerant pipe 67a, and temporarily uses the use-side refrigerant circulating in the use-side refrigerant circuit 50a before being drawn into the use-side compressor 55a from the cascade-side intake pipe 67a. It is a container for storing.
Thus, the use side compressor 55a, the refrigerant-water heat exchanger 57a, the refrigerant-water heat exchange side expansion valve 58a, the first use side heat exchanger 51a, and the use side accumulator 59a are connected via the refrigerant pipes 60a, 66a. By being connected, the use-side refrigerant circuit 50a is configured.
The first circulation pump 71a is a mechanism for boosting the aqueous medium. Here, a pump in which a centrifugal or positive displacement pump element (not shown) is driven by the first circulation pump motor 72a is employed. . The first circulation pump 71a is provided in the use side water outlet pipe 74a. Circulation pump motor 72a can change the rotation speed (namely, operation frequency) with an inverter device (not shown), and capacity control of the 1st circulation pump 71a is attained by this.

  The utilization unit 5a is provided with various sensors. Specifically, the usage unit 5a includes a usage-side heat exchanger side temperature sensor 61a, an aqueous medium inlet temperature sensor 63a, an aqueous medium outlet temperature sensor 64a, a usage-side suction pressure sensor 68a, and a usage-side discharge pressure. A sensor 69a, a use side discharge temperature sensor 157a, a refrigerant-hydrothermal temperature sensor 158a, and a cascade side liquid refrigerant pipe temperature sensor 160a are provided. The use side heat exchange liquid side temperature sensor 61a is a temperature sensor that detects the use side heat exchange liquid side temperature Tula, which is the temperature of the heat source side refrigerant on the liquid side of the first use side heat exchanger 51a. The aqueous medium inlet temperature sensor 63a is a temperature sensor that detects an aqueous medium inlet temperature Twr that is the temperature of the aqueous medium at the inlet of the refrigerant-water heat exchanger 57a. The aqueous medium outlet temperature sensor 64a is a temperature sensor that detects an aqueous medium outlet temperature Twla that is the temperature of the aqueous medium at the outlet of the refrigerant-water heat exchanger 57a. The use side suction pressure sensor 68a is a pressure sensor that detects the use side suction pressure Ps2a that is the pressure of the use side refrigerant in the suction of the use side compressor 55a. The use side discharge pressure sensor 69a is a pressure sensor that detects the use side discharge pressure Pd2a that is the pressure of the use side refrigerant in the discharge of the use side compressor 55a. The use side discharge temperature sensor 157a is a temperature sensor that detects a use side discharge temperature Td2a that is the temperature of the use side refrigerant in the discharge of the use side compressor 55a. The refrigerant-water heat exchanger temperature sensor 158a is a temperature sensor that detects the cascade-side refrigerant temperature Tpl1a that is the temperature of the use-side refrigerant on the liquid side of the refrigerant-water heat exchanger 57a. The cascade side liquid refrigerant pipe temperature sensor 160a is a temperature sensor that detects the temperature Tpl2a of the usage side refrigerant on the liquid side of the first usage side heat exchanger 51a. This temperature is a use side refrigerant evaporation temperature corresponding to the saturation temperature of the use side refrigerant in the first use side heat exchanger 51a. In addition, the usage unit 5a includes a usage-side control unit 69a that controls the operation of each unit constituting the usage unit 5a. The use side control unit 69a has a microcomputer, a memory, and the like for controlling the use unit 5a. The use side control unit 69a can exchange control signals and the like with a remote controller (not shown), and exchange control signals and the like with the heat source side control unit 49 of the heat source unit 2. It has become.

-Aqueous medium heating unit-
The aqueous medium heating units 75a and 75b (aqueous medium utilization devices) are installed indoors (for example, each door of an apartment house, each section of a building, etc.). The aqueous medium heating units 75a and 75b are connected to the utilization units 5a and 5b via the aqueous medium communication pipes 15a and 16a, and constitute a part of the aqueous medium circuits 70a and 70b. The configuration of the aqueous medium heating unit 75b is the same as the configuration of the aqueous medium heating unit 75a. Therefore, here, only the configuration of the aqueous medium heating unit 75a will be described, and the configuration of the aqueous medium heating unit 75b will be described with the subscript “b” instead of the subscript “a” indicating the respective parts of the aqueous medium heating unit 75a. The description of each part is omitted.
The aqueous medium heating unit 75a mainly has a heat exchange panel 76a, and constitutes a radiator, a floor heating panel, and the like.

In the case of a radiator, the heat exchange panel 76a is provided near the wall of the room, and in the case of a floor heating panel, the heat exchange panel 76a is provided under the floor of the room. The heat exchange panel 76a is a heat exchanger that functions as a radiator for the aqueous medium circulating in the aqueous medium circuit 70a. The aqueous medium communication pipe 16a is connected to the inlet, and the aqueous medium is connected to the outlet. A communication pipe 15a is connected.
-Aqueous medium connection pipe-
The aqueous medium communication pipe 15a is connected to the use side water inlet pipe 73a. The aqueous medium communication pipe 15a introduces the aqueous medium from the outside of the usage unit 5a (more specifically, the aqueous medium heating unit 75a) to the inlet of the first usage-side heat exchanger 51a that functions as an aqueous medium heater. This is an aqueous medium tube that can be used.
The aqueous medium communication pipe 16a is connected to the use side water outlet pipe 74a. The aqueous medium communication pipe 16a leads the aqueous medium out of the utilization unit 5a (more specifically, the aqueous medium heating unit 75a) from the outlet of the first utilization side heat exchanger 51a that functions as an aqueous medium heater. This is an aqueous medium tube that can be used.
And the control part 1a which performs operation control of the heat pump system 1 is comprised by the use side control parts 69a and 69b and the heat source side control part 49, and the following driving | operations and various control are performed.

<Operation>
Next, the operation of the heat pump system 1 will be described.
The operation of the heat pump system 1 includes a heating operation mode in which the heating operation (heating operation) of the utilization units 5a and 5b is performed.
−Heating operation mode−
When the heating operation of the utilization units 5a and 5b is performed, in the heat source side refrigerant circuit 20, the heat source side switching mechanism 23 is in the heat source side evaporation operation state (the state indicated by the broken line of the heat source side switching mechanism 23 in FIG. 1). Can be switched. Further, the suction return expansion valve 30 is closed. Here, description will be made assuming that all of the usage units 5a and 5b are set to the heating operation.

In the heat source side refrigerant circuit 20 in such a state, the low pressure heat source side refrigerant in the refrigeration cycle is sucked into the heat source side compressor 21 through the heat source side suction pipe 21c and compressed to a high pressure in the refrigeration cycle, and then the heat source side refrigerant circuit 20 is cooled. It is discharged to the discharge pipe 21b. The high pressure heat source side refrigerant discharged to the heat source side discharge pipe 21b is separated from the refrigerating machine oil in the oil separator 22a. The refrigerating machine oil separated from the heat source side refrigerant in the oil separator 22a is returned to the heat source side suction pipe 21c through the oil return pipe 22b. The high-pressure heat source side refrigerant from which the refrigeration oil is separated is sent from the heat source unit 2 to the gas refrigerant communication tube 14 through the heat source side switching mechanism 23, the heat source side gas refrigerant tube 25 and the gas side shut-off valve 34.
The high-pressure heat-source-side refrigerant sent to the gas refrigerant communication tube 14 is branched into two and sent to the use units 5a and 5b.

The high-pressure heat-source-side refrigerant sent to the usage units 5a and 5b is sent to the first usage-side heat exchangers 51a and 51b through the usage-side gas refrigerant tubes 54a and 54b. The high-pressure heat-source-side refrigerant sent to the first usage-side heat exchangers 51a, 51b is the low-pressure usage-side in the refrigeration cycle circulating in the usage-side refrigerant circuits 50a, 50b in the first usage-side heat exchangers 51a, 51b. Heat is exchanged with the refrigerant to dissipate heat. The high-pressure heat-source-side refrigerant radiated in the first usage-side heat exchangers 51a and 51b is transferred from the usage units 5a and 5b through the first usage-side expansion valves 52a and 52b and the usage-side liquid refrigerant tubes 53a and 53b. 13 to join.
The heat source side refrigerant sent to the liquid refrigerant communication tube 13 is sent to the heat source unit 2. The heat source side refrigerant sent to the heat source unit 2 is sent to the supercooler 31 through the liquid side shut-off valve 33. The heat source side refrigerant sent to the subcooler 31 is sent to the heat source side expansion valve 28 without performing heat exchange because the heat source side refrigerant does not flow through the suction return pipe 29. The heat source side refrigerant sent to the heat source side expansion valve 28 is depressurized by the heat source side expansion valve 28 to be in a low-pressure gas-liquid two-phase state, and is sent to the heat source side heat exchanger 26 through the heat source side liquid refrigerant tube 27. It is done. The low-pressure heat source side refrigerant sent to the heat source side heat exchanger 26 evaporates by exchanging heat with outdoor air supplied by the heat source side fan 36 in the heat source side heat exchanger 26. The low-pressure heat source side refrigerant evaporated in the heat source side heat exchanger 26 is sent to the heat source side accumulator 32 through the heat source side gas refrigerant tube 24 and the heat source side switching mechanism 23. The low-pressure heat source side refrigerant sent to the heat source side accumulator 32 is again sucked into the heat source side compressor 21 through the heat source side suction pipe 21c.

  On the other hand, in the usage-side refrigerant circuits 50a and 50b, the low-pressure usage-side refrigerant in the refrigeration cycle circulating through the usage-side refrigerant circuits 50a and 50b is heated by the heat radiation of the heat source-side refrigerant in the first usage-side heat exchangers 51a and 51b. Evaporate. The low-pressure use-side refrigerant evaporated in the first use-side heat exchangers 51a and 51b is sent to the use-side accumulators 59a and 59b through the cascade-side gas refrigerant tubes 67a and 67b. The low-pressure use-side refrigerant sent to the use-side accumulators 59a and 59b is sucked into the use-side compressors 55a and 55b, compressed to a high pressure in the refrigeration cycle, and then discharged to the cascade-side discharge pipes 60a and 60b. The high-pressure use-side refrigerant discharged to the cascade-side discharge pipes 60a and 60b is sent to the refrigerant-water heat exchangers 57a and 57b. The high-pressure use-side refrigerant sent to the refrigerant-water heat exchangers 57a, 57b is the heat and water medium circulating in the aqueous medium circuits 70a, 70b by the circulation pumps 71a, 71b in the refrigerant-water heat exchangers 57a, 57b. Replace and dissipate heat. The high-pressure use-side refrigerant radiated in the refrigerant-water heat exchangers 57a, 57b is decompressed in the refrigerant-water heat exchange side expansion valves 58a, 58b to be in a low-pressure gas-liquid two-phase state, and the cascade-side liquid refrigerant pipe It is again sent to the 1st utilization side heat exchanger 51a, 51b through 66a, 66b.

In the aqueous medium circuits 70a and 70b, the aqueous medium circulating through the aqueous medium circuits 70a and 70b is heated by the heat radiation of the heat source side refrigerant in the refrigerant-water heat exchangers 57a and 57b. The aqueous medium heated in the refrigerant-water heat exchangers 57a and 57b is sucked into the circulation pumps 71a and 71b through the use-side water outlet pipes 74a and 74b, and is pressurized, and then communicated with the aqueous medium from the use units 5a and 5b. Sent to the tubes 16a, 16b. The aqueous medium sent to the aqueous medium communication pipes 16a and 16b is sent to the aqueous medium heating units 75a and 75b. The aqueous medium sent to the aqueous medium heating units 75a and 75b dissipates heat in the heat exchange panels 76a and 76b, thereby heating indoor walls and the like and heating the indoor floor.
Thus, the operation | movement in the heating operation mode which performs heating operation of utilization unit 5a, 5b is performed.

-Condensation temperature control of each refrigerant circuit-
In the heat pump system 1, as described above, in the first usage-side heat exchangers 51 a and 51 b, the usage-side refrigerant that circulates in the usage-side refrigerant circuits 50 a and 50 b radiates heat from the heat-source-side refrigerant that circulates in the heat source side refrigerant circuit 20. It is supposed to be heated. And use side refrigerant circuit 50a, 50b can obtain a refrigerating cycle higher temperature than the refrigerating cycle in heat source side refrigerant circuit 20 using the heat obtained from this heat source side refrigerant. Thereby, a high temperature aqueous medium can be obtained now by the heat radiation of the utilization side refrigerant | coolant in the refrigerant | coolant-water heat exchangers 57a and 57b. At this time, in order to stably obtain a high-temperature aqueous medium, it is preferable to control so that both the refrigeration cycle in the heat source side refrigerant circuit 20 and the refrigeration cycle in the use side refrigerant circuits 50a and 50b are stabilized.

  Therefore, the control unit 1a operates the heat source side compressor 21 so that the heat source side condensation temperature Tc1 corresponding to the saturation temperature of the heat source side refrigerant in the discharge of the heat source side compressor 21 becomes the predetermined target heat source side condensation temperature Tc1s. The capacity is controlled. In addition, the control unit 1a controls the operation capacity of the heat source side compressor 21 and uses the use side condensation temperatures Tc2a and Tc2b corresponding to the saturation temperature of the use side refrigerant in the discharge of the use side compressors 50a and 50b. The operation capacities of the use side compressors 55a and 55b are controlled so as to be the target use side condensation temperatures Tc2as and Tc2bs. More specifically, when the heat source side condensing temperature Tc1 is lower than the target heat source side condensing temperature Tc1s, the control unit 1a increases the rotation speed (that is, the operating frequency) of the heat source side compressor 21 to increase the heat source side condensing temperature Tc1s. Control is performed so that the operating capacity of the compressor 21 is increased. Further, when the heat source side condensing temperature Tc1 is higher than the target heat source side condensing temperature Tc1s, the control unit 1a reduces the rotation speed (that is, the operating frequency) of the heat source side compressor 21 to reduce the heat source side condensing temperature Tc1s. Control to reduce the operating capacity. Moreover, when the use side condensation temperatures Tc2a and Tc2b are lower than the target use side condensation temperatures Tc2as and Tc2bs, the control unit 1a increases the rotation speed (that is, the operating frequency) of the use side compressors 55a and 55b. Control is performed so that the operating capacity of the use-side compressors 55a and 55b is increased. In addition, when the use side condensation temperatures Tc2a and Tc2b are higher than the target use side condensation temperatures Tc2as and Tc2bs, the control unit 1a reduces the rotation speed (that is, the operation frequency) of the use side compressors 55a and 55b. Control is performed so that the operating capacity of the use side compressors 55a and 55b is reduced. Thereby, in the heat source side refrigerant circuit 20, the pressure of the heat source side refrigerant flowing through the use side refrigerant circuits 50a and 50b is stabilized, and in the use side refrigerant circuits 50a and 50b, the refrigerant-water heat exchangers 57a and 57b. The pressure of the use-side refrigerant flowing through is stabilized. And the state of the refrigerating cycle in refrigerant circuit 20, 50a, 50b can be stabilized, and a high temperature aqueous medium can be obtained stably. The heat source side condensation temperature Tc1 is a value obtained by converting the heat source side discharge pressure Pd1, which is the pressure of the heat source side refrigerant in the discharge of the heat source side compressor 21, into a saturation temperature corresponding to this pressure value. The heat source side condensing temperature Tc1 is a value obtained by converting the high pressure in the refrigeration cycle of the heat source side refrigerant circuit 20 into a saturation temperature, that is, the first usage side heat that performs the heating operation in the first usage side heat exchangers 51a and 51b. This corresponds to the saturation temperature (condensation temperature) of the heat source side refrigerant in the exchanger. The use-side condensation temperatures Tc2a and Tc2b are values obtained by converting the use-side discharge pressures Pd2a and Pd2b, which are the pressures of the use-side refrigerant in the discharge of the use-side compressors 55a and 55b, into saturation temperatures corresponding to the pressure values. is there. The use-side condensation temperatures Tc2a and Tc2b are values obtained by converting the high pressure in the refrigeration cycle of the use-side refrigerant circuits 50a and 50b into the saturation temperature, that is, the refrigerant that performs heating operation among the refrigerant-water heat exchangers 57a and 57b. This corresponds to the saturation temperature (condensation temperature) of the use-side refrigerant in the water heat exchanger.

<Heat source unit power consumption apportioning system>
Since the heat pump system 1 is installed in an apartment house, a building, or the like, the users who use the usage units 5a and 5b may not be the same. In this case, it is necessary to jointly bear the power consumption Wr of the heat source unit 2 provided in common in the utilization units 5a and 5b. However, since the use units 5a and 5b have different capacities, usage frequencies, set temperatures, etc. depending on the user, a dedicated heat source unit power consumption apportioning system is necessary for each user to share the power consumption of the heat source unit 2 fairly. It becomes.
Therefore, here, the following heat source unit power consumption apportioning system 10 is applied to the heat pump system 1.

-Overall-
FIG. 2 is a system configuration diagram of the heat source unit power consumption apportioning system 10. The heat source unit power consumption apportioning system 10 mainly includes a heat source unit wattmeter 17, heat medium measuring water medium sensors 80 a and 80 b, a control unit 1 a, an interface device 18, and an arithmetic device 19.
The heat source unit power meter 17 is a device that detects the power consumption Wr of the heat source unit 2, and can transmit the detected power consumption Wr to the computing device 19.
The calorie measurement aqueous medium sensors 80a and 80b detect the flow rate and temperature of the aqueous medium exchanged between the utilization units 105a and 105b and the aqueous medium cooling / heating units 75a and 75b in order to calculate the use side use heat quantity described later. This is a sensor unit. The configuration of the calorie measurement aqueous medium sensor 80b is the same as the configuration of the calorie measurement aqueous medium sensor 80a. For this reason, here, only the configuration of the calorie measurement aqueous medium sensor 80a will be described, and the configuration of the calorie measurement aqueous medium sensor 80b is subscripted instead of the subscript “a” indicating the respective parts of the calorie measurement aqueous medium sensor 80a. A description of each part is omitted by attaching “b”. As shown in FIG. 3, the calorific measurement aqueous medium sensor 80a mainly includes a calorific measurement inlet temperature sensor 81a, a calorific measurement outlet temperature sensor 82a, and a calorific measurement flow sensor 83a. The calorie measurement inlet temperature sensor 81a is a temperature sensor that detects the calorie measurement inlet temperature Twi1a, which is the temperature of the aqueous medium flowing through the aqueous medium communication pipe 16a. The calorific value measurement outlet temperature sensor 82a is a temperature sensor that detects the calorific value measurement outlet temperature Twoa that is the temperature of the aqueous medium flowing through the aqueous medium communication pipe 15a. The heat quantity measurement flow sensor 83a is a flow sensor that detects a heat quantity measurement flow Gw1a that is a flow rate of the aqueous medium flowing through the aqueous medium communication pipe 15a. Further, the calorie measurement aqueous medium sensor 80a can transmit the detected aqueous medium flow rate Gw1a and temperatures Twi1a and Two1a to the arithmetic unit 19.

As described above, the control unit 1a includes the heat source side control unit 49 and the use side control units 69a and 69b, and the operation data and equipment of the heat pump system 1 (here, the heat source unit 2 and the use units 5a and 5b). Information or the like can be transmitted to the arithmetic unit 19.
The interface device 18 includes a heat source unit wattmeter 17, a calorific value measurement aqueous medium sensor 80 a, 80 b, and a control unit 1 a to transmit operation data, device information, and the like from the control unit 1 a to the computing device 19. The sensors 80 a and 80 b and the control unit 1 a are interposed between the arithmetic unit 19.
The arithmetic unit 19 is a computer that receives the operation data and device information from the heat source unit wattmeter 17, the calorie measurement water medium sensors 80a and 80b, and the control unit 1a, and performs a process of distributing the power consumption Wr to each user. is there. The calculation device 19 includes a use heat amount calculation unit 19a, a correction heat amount calculation unit 19b, and a power apportioning unit 19c.

-Use calorific value calculation unit, correction calorific value calculation unit-
The use heat amount calculation unit 19a calculates the use side use heat amount which is the use heat amount of the heating operation (heating operation) in each use unit 5a, 5b from the flow rate Gw1a, Gw1b of the aqueous medium and the temperature Twi1a, Two1a, Two1b, Two1b. Based on the refrigeration cycle characteristics of the respective use-side refrigerant circuits 50a and 50b assumed from the heat-source-side condensation temperature Tc1 or the use-side evaporation temperatures Tpl2a and Tpl2b and the aqueous medium outlet temperatures Twla and Twlb, The usage-side usage heat amount in the usage units 5a and 5b is corrected.
The calculation of the usage-side usage heat amount and the correction process in the usage heat amount calculation unit 19a and the correction heat amount calculation unit 19b are performed as follows.
First, the used heat amount calculation unit 19a obtains operation data, device information, and the like of the heat pump system 1 transmitted from the heat medium measuring water medium sensors 80a and 80b and the control unit 1a to the calculation device 19 via the interface device 18.

Next, the usage heat amount calculation unit 19a uses the data of the aqueous medium flow rates Gw1a and Gw1b and the temperatures Twi1a, Two1a, Twi1b, and Two1b of the aqueous medium sensors for heat quantity measurement 80a and 80b. The usage-side usage heat quantity qh is calculated. In addition, whether each utilization unit is performing the heating operation, for example, the operation state of each utilization unit such as the open / close state of the first utilization side expansion valves 52a, 52b, the operation state of the utilization side compressors 55a, 55b, etc. It is determined based on operation data, device information, and the like.
The usage-side usage calorie qh of the utilization unit performing the heating operation is the water medium flow rate Gw1a, Gw1b (heat quantity measurement flow rate) detected by the calorie measurement aqueous medium sensors 80a, 80b, and the temperatures Twi1a, Two1a, Twi1b, Two1b. Is calculated based on That is, the use side use heat quantity qh can be calculated according to the following equation.

qh = Gw1 × (Twi1-Two1)
Here, Gw1 is a flow rate of the aqueous medium that passes through the aqueous medium heating units 75a and 75b during the heating operation (flow rate for calorific value measurement). Twi1 is the temperature of the aqueous medium supplied to the aqueous medium heating units 75a and 75b during the heating operation (the aqueous medium inlet temperature for calorimetric measurement). Two1 is the temperature of the aqueous medium (heat medium measurement aqueous medium outlet temperature) returned from the aqueous medium heating units 75a and 75b to the utilization units 5a and 5b during the heating operation.
Next, the corrected calorific value calculation unit 19b multiplies the calculated usage side usage calorie qh by the correction coefficients kpl and kwl to obtain the corrected usage side usage calorie qh ''.
That is, for the usage-side usage heat quantity qh of the heating operation, the corrected usage-side usage heat quantity qh ″ is calculated by the following equation. The use side use heat quantity qh '' obtained by this correction corresponds to the exchange heat quantity between the heat source side refrigerant and the use side refrigerant in the first use side heat exchangers 51a and 51b.

qh ″ = qh × kpl × kwl
The correction coefficients kpl and kwl are values obtained based on the refrigeration cycle characteristics of the respective use-side refrigerant circuits 50a and 50b that are assumed from the heat-source-side condensation temperature Tc1 or the use-side evaporation temperature Tpl2 and the aqueous medium outlet temperature Twl.
Here, considering the refrigeration cycle characteristics of the usage-side refrigerant circuits 50a and 50b, first, as shown in FIG. 4, the aqueous medium outlet temperature Twl remains constant while the low pressure in the refrigeration cycle of the usage-side refrigerant circuits 50a and 50b remains constant. When it becomes higher, the high pressure in the refrigeration cycle of the use-side refrigerant circuits 50a and 50b tends to increase. When the high pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b increases, the amount of heat exchanged between the heat source side refrigerant and the use side refrigerant in the first use side heat exchangers 51a and 51b decreases, and the use side compressor 55a, The power consumption of 55b tends to increase. In contrast, when the high pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b remains constant and the heat source side condensation temperature Tc1 or the use side evaporation temperature Tpl2 decreases, the low pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b decreases. It tends to be lower. When the low pressure in the refrigeration cycle of the use side refrigerant circuits 50a, 50b is reduced, the amount of heat exchanged between the heat source side refrigerant and the use side refrigerant in the first use side heat exchangers 51a, 51b is reduced, and the use side compressor 55a, The power consumption of 55b tends to increase. As described above, the use side refrigerant circuits 50a and 50b have the first use side heat exchanger 51a as the aqueous medium outlet temperature Twl, which is a state quantity corresponding to the high pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b, increases. , 51b has a refrigeration cycle characteristic in which the amount of exchange heat between the heat source side refrigerant and the use side refrigerant is small. Further, the use side refrigerant circuits 50a and 50b are configured so that the heat source side condensation temperature Tc1 or the use side evaporation temperature Tpl2, which is a state quantity corresponding to the low pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b, decreases as the first use side. The heat exchangers 51a and 51b have refrigeration cycle characteristics in which the amount of heat exchanged between the heat source side refrigerant and the use side refrigerant is reduced.

  Therefore, here, a characteristic is used in which the amount of heat exchanged between the heat source side refrigerant and the use side refrigerant in the first use side heat exchangers 51a and 51b decreases as the heat source side condensation temperature Tc1 or the use side evaporation temperature Tpl2 decreases. Thus, the first correction coefficient kpl is prepared as a function that decreases as the heat source side condensation temperature Tc1 or the use side evaporation temperature Tpl2 decreases. Further, the aqueous medium outlet temperature Twl is increased by using the characteristic that the amount of heat exchanged between the heat source side refrigerant and the utilization side refrigerant in the first usage-side heat exchangers 51a and 51b decreases as the aqueous medium outlet temperature Twl increases. The second correction coefficient kwl is prepared as a function that decreases as the time increases. The correction coefficients are not limited to the two correction coefficients kpl and kwl described above, but are assumed from the heat source side condensation temperature Tc1 or the use side evaporation temperatures Tpl2a and Tpl2b and the aqueous medium outlet temperatures Twla and Twlb. Any correction coefficient may be used as long as it is obtained based on the refrigeration cycle characteristics of the use-side refrigerant circuits 50a and 50b.

The corrected usage side usage heat quantity qh ″ obtained by the above correction is used as the usage side usage heat quantities Qa and Qb of the usage units 5a and 5b.
-Power apportioning section-
The power apportioning unit 19c determines the power consumption Wr of the heat source unit 2 according to the corrected usage-side usage heat amounts Qa and Qb (in this case, the users of the usage units 5a and 5b are the users A and B). Apportion.
Such a distribution process of the power consumption Wr of the heat source unit 2 in the power distribution unit 19c is performed as follows.
First, the power apportioning unit 19 c obtains the data of the power consumption Wr of the heat source unit 2 transmitted from the heat source unit wattmeter 17 to the arithmetic device 19 via the interface device 18.

Next, the power apportioning unit 19c uses the usage-side usage heat amounts Qa and Qb after the correction of the usage units 5a and 5b obtained in the usage heat amount calculation unit 19a and the correction heat amount calculation unit 19b to use each usage unit 5a. The power consumption Wr of the heat source unit 2 is apportioned to the users A and B of 5b. For example, the apportioned power Wra of the power consumption Wr of the heat source unit 2 for the user A is expressed by the following equation.
Wra = Wr × Qa / Σ (Qa, Qb)
Here, Σ (Qa, Qb) means an integrated value of the use side usage heat amounts Qa, Qb after correction (that is, here, Qa + Qb is meant). Further, the apportioned power Wrb of the power consumption Wr of the heat source unit 2 for the user B can be calculated in the same manner as the apportioned power Wra.

-Specific example-
A specific example in which the heat source unit power consumption apportioning system 10 is used to apportion the power consumption Wr of the heat source unit 2 to the users A and B who use the utilization units 5a and 5b will be described.
Here, the user A (use unit 5a) performs the heating operation with the use side use heat amount qha = 4.0, and the user B (use unit 5b) performs the heating operation with the use side use heat amount qhb = 4.0. And In addition, the heat source side condensation temperature Tc1 or the use side evaporation temperature Tpl2 is 20 ° C. in both the use units 5a and 5b (at this time, kpla and kplb = 0.9), and the aqueous medium outlet temperature Twl is the use unit 5a. 65 ° C. (kwla = 0.75 at this time) and 40 ° C. in the usage unit 5a (kwlb = 1.0 at this time). Here, for convenience of explanation, the usage-side used heat quantities qha and qhb are represented by dimensionless numbers. In this case, the user-side corrected usage-side use heat quantity Qa (qha ″) of the user A is 2.7 (= 4.0 × 0.9 × 0.75), and the user B's corrected usage-side The amount of heat used Qb (qhb ″) becomes 3.6 (= 4.0 × 0.9 × 1.0). For this reason, the apportioned power Wra and Wrb of the power consumption Wr of the heat source unit 2 for the users A and B are 0.43 Wr and 0.57 Wr, respectively. In this case, if the power consumption Wr of the heat source unit 2 is apportioned without correcting the usage-side usage heat quantities qha and qhb, the apportionment of the power consumption Wr of the heat source unit 2 to the users A and B is apportioned. The electric power Wra and Wrb are 0.5 Wr and 0.5 Wr, respectively.

  In this way, under the operating conditions where the utilization units 5a and 5b are different (in the above, the aqueous medium outlet temperature Twl is different), the utilization units 5a and 5b are used even though the utilization side use heat quantities qha and qhb are the same. Among them, the power consumption Wr of the heat source unit 2 is apportioned less with respect to the use unit 5a having a large heat amount to be borne in the use-side refrigerant circuits 50a and 50b. This is because the usage unit 5a increases the operation load of the usage-side refrigerant circuit 50a to increase the aqueous medium outlet temperature Twl to 65 ° C. in order to obtain the same usage-side usage heat amount. This is because the unit 5b increases the aqueous medium outlet temperature Twl to 40 ° C., which is lower than 65 ° C., without increasing the operation load of the use-side refrigerant circuit 50a so much. That is, in the heat source unit power consumption apportioning system 10, each usage unit 5 a calculated from the flow rate and temperature of the aqueous medium in consideration of the difference in operating conditions and the like of the usage-side refrigerant circuits 50 a and 50 b in the usage units 5 a and 5 b. 5b is corrected based on the refrigeration cycle characteristics of the respective use-side refrigerant circuits 50a and 50b, which are assumed from the heat-source-side condensation temperature or the use-side evaporation temperature and the aqueous medium outlet temperature. The power consumption Wr of the heat source unit 2 can be appropriately distributed.

<Features>
The heat source unit power consumption apportioning system 10 has the following characteristics.
-A-
In the heat source unit power consumption apportioning system 10, the heat source side condensing temperature Tc1 or the use side evaporation temperatures Tpl2a and Tpl2b and the aqueous medium outlet temperatures Twla and Twlb correspond to the low pressure and high pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b. Based on the refrigeration cycle characteristics of the use side refrigerant circuits 50a and 50b assumed from the state quantities, the use side use heat quantity qh is corrected. For this reason, it is possible to obtain a corrected usage-side heat quantity qh ′ that takes into account the influence of the heat quantity borne by the usage-side refrigerant circuits 50a and 50b, which is mainly composed of the work of the usage-side compressors 55a and 55b.

As a result, in the heat source unit power consumption apportioning system 10, the use side refrigerant circuits 50a and 50b use the use side use heat amount calculated from the flow rate and temperature of the aqueous medium in each use unit 5a and 5b. The influence of the amount of heat to be borne can be considered. Therefore, in the heat source unit power consumption apportioning system 10, the power consumption Wr of the heat source unit 2 can be apportioned appropriately.
In addition, in the calculation and correction of the usage-side heat consumption, the usage-side heat consumption is basically calculated by measuring the calorific value of the aqueous medium, and the usage-side usage is determined based on the operation data of the minimum heat pump system 1 and the like. Since the amount of heat is corrected, it can be easily retrofitted to an existing heat pump system.
-B-
In the heat source unit power consumption apportioning system 10, the correction coefficients related to the low and high pressure states in the refrigeration cycle of the use-side refrigerant circuits 50a and 50b are prepared as two correction coefficients, a first correction coefficient kpl and a second correction coefficient kwl. Therefore, accurate apportioning can be performed in consideration of the refrigeration cycle characteristics of the use-side refrigerant circuits 50a and 50b.
-C-
In the heat source unit power consumption apportioning system 10, the control unit 1a controls the operating capacity of the heat source side compressor 21 so that the heat source side condensation temperature Tc1 becomes a predetermined target heat source side condensation temperature Tc1s. The temperature Tc1 or the use side evaporation temperatures Tpl2a and Tpl2b are stabilized. For this reason, since the use side use calorie | heat amount qh can be correct | amended in the state where the low pressure state in the refrigerating cycle of use side refrigerant circuit 50a, 50b was stabilized, exact proportional distribution can be performed.

(2) Second Embodiment <Configuration of Heat Pump System>
-Overall-
FIG. 5 is a schematic configuration diagram of a heat pump system 101 to which the heat source unit power consumption apportioning system according to the second embodiment of the present invention is applied. The heat pump system 101 is an apparatus capable of performing a cooling operation (cooling operation) or a heating operation (heating operation) using a vapor compression heat pump cycle.

  The heat pump system 101 mainly includes a heat source unit 102, a plurality of (two in FIG. 5) use units 105a and 105b, a discharge refrigerant communication pipe 12, a liquid refrigerant communication pipe 13, and an intake refrigerant communication pipe 14. It has aqueous medium air conditioning units 75a and 75b (aqueous medium utilization equipment) and aqueous medium communication pipes 15a, 16a, 15b and 16b. The heat source unit 102 and the utilization units 105a and 105b are connected via the refrigerant communication tubes 12, 13, and 14 to constitute the heat source side refrigerant circuit 120. The usage units 105a and 105b constitute usage-side refrigerant circuits 50a and 50b. The utilization units 105a and 105b and the aqueous medium cooling / heating units 75a and 75b are connected via aqueous medium communication pipes 15a, 16a, 15b, and 16b to constitute aqueous medium circuits 170a and 170b. In the heat source side refrigerant circuit 120, HFC-410A, which is a kind of HFC refrigerant, is enclosed as a heat source side refrigerant. Further, HFC-134a, which is a kind of HFC refrigerant, is sealed in the use side refrigerant circuits 50a and 50b as the use side refrigerant. In addition, as a use side refrigerant | coolant, from a viewpoint that the refrigerant | coolant advantageous to a high temperature refrigerating cycle is used, the pressure corresponding to the saturation gas temperature of 65 degreeC is 2.8 MPa or less at a gauge pressure at most, Preferably, it is 2.0 MPa. The following refrigerants are preferably used. HFC-134a is a kind of refrigerant having such saturation pressure characteristics. In addition, water as an aqueous medium circulates in the aqueous medium circuits 170a and 170b.

-Heat source unit-
The heat source unit 102 is installed outdoors (for example, an apartment house or a rooftop of a building). The heat source unit 102 is connected to the utilization units 105 a and 105 b via the refrigerant communication tubes 12, 13, and 14 and constitutes a part of the heat source side refrigerant circuit 120.
The heat source unit 102 mainly includes a heat source side compressor 21, an oil separation mechanism 22, a first heat source side switching mechanism 23a, a second heat source side switching mechanism 23b, a first heat source side heat exchanger 26a, A heat source side heat exchanger 26b, a first heat source side expansion valve 28a, a second heat source side expansion valve 28b, a first suction return pipe 29a, a second suction return pipe 29b, a first subcooler 31a, The second subcooler 31b, the liquid side closing valve 33, the suction side closing valve 34, the discharge side closing valve 35, and the third heat source side switching mechanism 39 are provided.

The heat source side compressor 21 is a mechanism that compresses the heat source side refrigerant. Here, as the heat source side compressor 21, a rotary type or scroll type positive displacement compression element (not shown) accommodated in a casing (not shown) is also used. A hermetic compressor driven by a machine motor 21a is employed. The heat source side compressor motor 21a can change the rotation speed (that is, the operating frequency) by an inverter device (not shown), thereby enabling capacity control of the heat source side compressor 21.
The oil separation mechanism 22 is a mechanism for separating the refrigerating machine oil contained in the heat source side refrigerant discharged from the heat source side compressor 21 and returning it to the suction of the heat source side compressor 21. The oil separation mechanism 22 mainly includes an oil separator 22a provided in the heat source side discharge pipe 21b of the heat source side compressor 21, and an oil that connects the oil separator 22a and the heat source side suction pipe 21c of the heat source side compressor 21. And a return pipe 22b. The oil separator 22a is a device that separates refrigeration oil contained in the heat source side refrigerant discharged from the heat source side compressor 21. The oil return pipe 22 b has a capillary tube, and is a refrigerant pipe that returns the refrigeration oil separated from the heat source side refrigerant in the oil separator 22 a to the heat source side suction pipe 21 c of the heat source side compressor 21. A heat source side gas refrigerant tube 25 is connected to the heat source side suction tube 21c. The heat source side gas refrigerant tube 25 is a refrigerant tube for introducing the heat source side refrigerant into the suction of the heat source side compressor 21 from outside the heat source unit 102 (more specifically, the suction refrigerant communication tube 14).

  The first heat source side switching mechanism 23a is a first heat source side heat dissipation operation state in which the first heat source side heat exchanger 26a functions as a heat source side refrigerant radiator, and the first heat source side heat exchanger 26a is an evaporator of the heat source side refrigerant. It is a four-way switching valve that can switch between the first heat source side evaporation operation state to function as. The first heat source side switching mechanism 23a is connected to a heat source side discharge pipe 21b, a heat source side suction pipe 21c, and a first heat source side gas refrigerant pipe 24a connected to the gas side of the first heat source side heat exchanger 26a. ing. One of the four ports of the first heat source side switching mechanism 23a communicates with the heat source side suction pipe 21c through the capillary tube 48a, whereby the first heat source side switching mechanism 23a is connected to the three-way switching valve. It is supposed to function as. The first heat source side switching mechanism 23a switches the communication between the heat source side discharge pipe 21b and the first heat source side gas refrigerant pipe 24a (corresponding to the first heat source side heat radiation operation state, the first heat source side switching mechanism 23a of FIG. (See solid line). The first heat source side switching mechanism 23a switches the first heat source side gas refrigerant tube 24a and the heat source side suction tube 21c to communicate (corresponding to the first heat source side evaporation operation state, the first heat source side switching mechanism in FIG. 5). 23a) (see dashed line 23a). The first heat source side switching mechanism 23a is not limited to the four-way switching valve. For example, the first heat source side switching mechanism 23a switches the flow direction of the heat source side refrigerant similar to the above by using a plurality of solenoid valves in combination. It may be configured to have a function.

  The second heat source side switching mechanism 23b is a second heat source side heat dissipation operation state in which the second heat source side heat exchanger 26b functions as a heat source side refrigerant radiator, and the second heat source side heat exchanger 26b is an evaporator of the heat source side refrigerant. It is a four-way switching valve that can switch between the second heat source side evaporation operation state to function as. The second heat source side switching mechanism 23b includes a heat source side discharge pipe 21b, a heat source side suction pipe 21c (more specifically, a communication pipe 38 communicating with the heat source side gas refrigerant pipe 25 and the heat source side suction pipe 21c), The second heat source side heat exchanger 26b is connected to the second heat source side gas refrigerant tube 24b connected to the gas side. That is, the heat source side discharge pipe 21b is a branch pipe connected to both the first heat source side switching mechanism 23a and the second heat source side switching mechanism 23b. One of the four ports of the second heat source side switching mechanism 23b communicates with the communication pipe 38 through the capillary tube 48b, whereby the second heat source side switching mechanism 23b functions as a three-way switching valve. It is supposed to be. The second heat source side switching mechanism 23b switches the communication between the heat source side discharge pipe 21b and the second heat source side gas refrigerant pipe 24b (corresponding to the second heat source side heat radiation operation state, the second heat source side switching mechanism 23b of FIG. (See solid line). The second heat source side switching mechanism 23b switches the second heat source side gas refrigerant pipe 24b and the heat source side suction pipe 21c to communicate (corresponding to the second heat source side evaporation operation state, the second heat source side switching mechanism in FIG. 5). 23b). Note that the second heat source side switching mechanism 23b is not limited to the four-way switching valve, and switches the flow direction of the heat source side refrigerant similar to the above by, for example, using a plurality of electromagnetic valves in combination. It may be configured to have a function.

  The third heat source side switching mechanism 39 is a four-way switching valve provided in the heat source side discharge branch pipe 21d branched from the heat source side discharge pipe 21b. The third heat source side switching mechanism 39 is a cooling / heating simultaneous operation state for configuring a heat pump system capable of operating the heat source unit 102 simultaneously with cooling and heating, and a cooling / heating switching operation for configuring a heat pump system capable of performing the cooling / heating switching operation of the heat source unit 102. This is a four-way switching valve capable of switching between states. The third heat source side switching mechanism 39 includes a heat source side discharge branch pipe 21d and a heat source side suction pipe 21c (more specifically, a communication pipe 40 communicating with the heat source side gas refrigerant pipe 25 and the heat source side suction pipe 21c). It is connected. One of the four ports of the third heat source side switching mechanism 39 communicates with the communication pipe 40 through the capillary tube 39a, whereby the third heat source side switching mechanism 39 functions as a three-way switching valve. It is supposed to be. Regardless of the switching operation of the first and second heat source side switching mechanisms 23a, 23b, the third heat source side switching mechanism 39 passes the heat source side discharge branch pipe 21d from the discharge of the heat source side compressor 21 to the heat source side refrigerant to the heat source unit 102. Switching outside (more specifically, switching to function as a refrigerant pipe leading to the discharge refrigerant communication pipe 12 (corresponding to the simultaneous heating and cooling operation state, see the solid line of the third heat source side switching mechanism 39 in FIG. 5)) It is possible. Further, the third heat source side switching mechanism 39 changes the heat source side refrigerant from the discharge of the heat source side compressor 21 to the heat source side discharge branch pipe 21d in accordance with the switching operation of the first and second heat source side switching mechanisms 23a, 23b. Switching to function as a refrigerant pipe leading out of the unit 102 and as a refrigerant pipe for introducing the heat source side refrigerant into the suction of the heat source side compressor 21 from outside the heat source unit 102 (corresponding to the cooling / heating switching operation state, the third in FIG. 5) It is possible to perform (see the broken line of the heat source side switching mechanism 39). The third heat source side switching mechanism 39 is not limited to the four-way switching valve, and switches the direction of the heat source side refrigerant flow as described above, for example, by using a combination of a plurality of solenoid valves. It may be configured to have a function.

  The first heat source side heat exchanger 26a is a heat exchanger that functions as a heat radiator or evaporator of the heat source side refrigerant by exchanging heat between the heat source side refrigerant and outdoor air, and the first heat source side on the liquid side The liquid refrigerant pipe 27a is connected, and the first heat source side gas refrigerant pipe 24a is connected to the gas side thereof. The first heat source side liquid refrigerant tube 27a is a refrigerant tube for leading the heat source side refrigerant from the outlet of the first heat source side heat exchanger 26a that functions as a heat source side refrigerant radiator to the heat source side liquid refrigerant junction tube 27. . The first heat source side liquid refrigerant tube 27a is a refrigerant tube for introducing the heat source side refrigerant from the heat source side liquid refrigerant junction tube 27 to the inlet of the first heat source side heat exchanger 26a that functions as an evaporator of the heat source side refrigerant. But there is. The outdoor air that exchanges heat with the heat source side refrigerant in the first heat source side heat exchanger 26 is supplied by a first heat source side fan 36a driven by a first heat source side fan motor 37a. The first heat source side fan motor 37a can vary the rotation speed (that is, the operating frequency) by an inverter device (not shown), thereby enabling the air volume control of the first heat source side fan 36a.

The first heat source side expansion valve 28a is an electric expansion valve that depressurizes the heat source side refrigerant flowing through the first heat source side heat exchanger 26a, and is provided in the first heat source side liquid refrigerant pipe 27a.
The first suction return pipe 29a is a refrigerant pipe that branches a part of the heat source side refrigerant flowing through the first heat source side liquid refrigerant pipe 27a and returns it to the suction of the heat source side compressor 21, and one end thereof is a first pipe. The other end of the heat source side liquid refrigerant pipe 27a is connected to the heat source side suction pipe 21c. The first suction return pipe 29a is provided with a first suction return expansion valve 30a whose opening degree can be controlled. The first suction return expansion valve 30a is an electric expansion valve.
The first subcooler 31a includes a refrigerant flowing through the first heat source side liquid refrigerant pipe 27a and a heat source side refrigerant flowing through the first suction return pipe 29a (more specifically, after being decompressed by the first suction return expansion valve 30a). It is a heat exchanger which performs heat exchange with the heat source side refrigerant.

  The second heat source side heat exchanger 26b is a heat exchanger that functions as a heat radiator or evaporator of the heat source side refrigerant by exchanging heat between the heat source side refrigerant and outdoor air, and the second heat source side on the liquid side. The liquid refrigerant pipe 27b is connected, and the second heat source side gas refrigerant pipe 24b is connected to the gas side thereof. The second heat source side liquid refrigerant tube 27b is a refrigerant tube for leading to the heat source side liquid refrigerant junction tube 27 from the outlet of the second heat source side heat exchanger 26b which functions as a heat source side refrigerant radiator. The second heat source side liquid refrigerant tube 27b is a refrigerant tube for introducing the heat source side refrigerant from the heat source side liquid refrigerant junction tube 27 to the inlet of the second heat source side heat exchanger 26b that functions as an evaporator of the heat source side refrigerant. But there is. That is, the first heat source side liquid refrigerant pipe 27 a and the second heat source side liquid refrigerant pipe 27 b are refrigerant pipes branched from the heat source side liquid refrigerant junction pipe 27. The heat source side liquid refrigerant junction tube 27 removes the heat source side refrigerant from the junction of the first heat source side liquid refrigerant tube 27a and the second heat source side liquid refrigerant tube 27b outside the heat source unit 102 (more specifically, the liquid refrigerant communication tube 13). It is a refrigerant pipe for deriving to (1). The heat source side liquid refrigerant junction tube 27 is also a refrigerant tube for introducing the heat source side refrigerant from the outside of the heat source unit 102 to the junction of the first heat source side liquid refrigerant tube 27a and the second heat source side liquid refrigerant tube 27b. The outdoor air that exchanges heat with the heat source side refrigerant in the second heat source side heat exchanger 26b is supplied by the second heat source side fan 36b driven by the second heat source side fan motor 37b. The second heat source side fan motor 37b can vary the rotation speed (that is, the operating frequency) by an inverter device (not shown), thereby enabling the air volume control of the second heat source side fan 36b.

The second heat source side expansion valve 28b is an electric expansion valve that depressurizes the heat source side refrigerant flowing through the second heat source side heat exchanger 26b, and is provided in the second heat source side liquid refrigerant pipe 27b.
The second suction return pipe 29b is a refrigerant pipe that branches a part of the heat source side refrigerant flowing through the second heat source side liquid refrigerant pipe 27b and returns it to the suction of the heat source side compressor 21, where one end of the second suction return pipe 29b is a second one. The other end of the heat source side liquid refrigerant pipe 27b is connected to the heat source side suction pipe 21c. The second suction return pipe 29b is provided with a second suction return expansion valve 30b whose opening degree can be controlled. The second suction return expansion valve 30b is an electric expansion valve.
The second subcooler 31b includes a refrigerant flowing through the second heat source side liquid refrigerant pipe 27b and a heat source side refrigerant flowing through the second suction return pipe 29b (more specifically, after being decompressed by the second suction return expansion valve 30b). It is a heat exchanger which performs heat exchange with the heat source side refrigerant.

The liquid side closing valve 33 is a valve provided at a connection portion between the heat source side liquid refrigerant merging pipe 27 and the liquid refrigerant communication pipe 13. The suction side closing valve 34 is a valve provided at a connection portion between the heat source side gas refrigerant pipe 25 and the suction refrigerant communication pipe 14. The discharge side closing valve 35 is a valve provided at a connection portion between the heat source side discharge branch pipe 21 d and the discharge refrigerant communication pipe 12.
The heat source unit 102 is provided with various sensors. Specifically, the heat source unit 102 includes a heat source side suction pressure sensor 41, a heat source side discharge pressure sensor 42, a heat source side suction temperature sensor 43, a heat source side discharge temperature sensor 44, and first and second heat source sides. Heat exchange gas side temperature sensors 45a and 45b, first and second heat source side heat exchange liquid side temperature sensors 46a and 46b, and an outside air temperature sensor 47 are provided. The heat source side suction pressure sensor 41 is a pressure sensor that detects the heat source side suction pressure Ps1 that is the pressure of the heat source side refrigerant in the suction of the heat source side compressor 21. The heat source side discharge pressure sensor 42 is a pressure sensor that detects the heat source side discharge pressure Pd <b> 1 that is the pressure of the heat source side refrigerant in the discharge of the heat source side compressor 21. The heat source side suction temperature sensor 43 is a temperature sensor that detects a heat source side suction temperature Ts1 that is the temperature of the heat source side refrigerant in the suction of the heat source side compressor 21. The heat source side discharge temperature sensor 44 is a temperature sensor that detects the heat source side discharge temperature Td <b> 1 that is the temperature of the heat source side refrigerant in the discharge of the heat source side compressor 21. The first and second heat source side heat exchange gas side temperature sensors 45a, 45b are heat source side heat exchange gas side temperatures Thg1, Thg2, which are the refrigerant temperatures on the gas side of the first and second heat source side heat exchangers 26a, 26b. It is a temperature sensor that detects The first and second heat source side heat exchange liquid side temperature sensors 46a and 46b are the heat source side heat exchange liquid side temperature Thl1 which is the temperature of the heat source side refrigerant on the liquid side of the first and second heat source side heat exchangers 26a and 26b. , Thl2. The outside air temperature sensor 47 is a temperature sensor that detects the outside air temperature To. Further, the heat source unit 102 includes a heat source side control unit 49 that controls the operation of each unit constituting the heat source unit 102. The heat source side control unit 49 includes a microcomputer and a memory for controlling the heat source unit 102. The heat source side control unit 49 can exchange control signals and the like with use side control units 69a and 69b of use units 105a and 105b described later.

−Discharge refrigerant communication tube−
The discharge refrigerant communication pipe 12 is connected to the heat source side discharge branch pipe 21d via the discharge side closing valve 35. When the third heat source side switching mechanism 39 is in the cooling and heating simultaneous operation state, the discharge refrigerant communication tube 12 is in either the heat source side heat radiation operation state or the heat source side evaporation operation state when the first and second heat source side switching mechanisms 23a and 23b are in the cooling and heating simultaneous operation state. The refrigerant pipe is capable of leading the heat source side refrigerant out of the heat source unit 102 from the discharge of the heat source side compressor 21.
−Liquid refrigerant connection tube−
The liquid refrigerant communication pipe 13 is connected to the heat source side liquid refrigerant junction pipe 27 via a liquid side closing valve 33. The liquid refrigerant communication tube 13 is an outlet of the first and second heat source side heat exchangers 26a and 26b in which the first and second heat source side switching mechanisms 23a and 23b function as a heat source side refrigerant radiator in the heat source side heat radiation operation state. It is a refrigerant pipe which can lead out the heat source side refrigerant from the heat source unit 102 to the outside. In addition, the liquid refrigerant communication tube 13 includes first and second heat source side heats that function as an evaporator of the heat source side refrigerant from outside the heat source unit 102 when the first and second heat source side switching mechanisms 23a and 23b are in the heat source side evaporation operation state. It is also a refrigerant pipe capable of introducing the heat source side refrigerant into the inlets of the exchangers 26a and 26b.

−Suction refrigerant communication tube−
The suction refrigerant communication pipe 14 is connected to the heat source side gas refrigerant pipe 25 via a suction side closing valve 34. The suction refrigerant communication pipe 14 is used for the suction of the heat source side compressor 21 from the outside of the heat source unit 102 regardless of whether the first and second heat source side switching mechanisms 23a and 23b are in the heat source side heat radiation operation state or the heat source side evaporation operation state. It is a refrigerant pipe into which a side refrigerant can be introduced.
-Usage unit-
The use units 105a and 105b are installed indoors (for example, each door of an apartment house, each section of a building, etc.). The utilization units 105 a and 105 b are connected to the heat source unit 102 via the refrigerant communication pipes 12, 13, and 14 and constitute a part of the heat source side refrigerant circuit 120. Further, the usage units 105a and 105b constitute usage-side refrigerant circuits 50a and 50b. Furthermore, the utilization units 105a and 105b are connected to the aqueous medium cooling / heating units 75a and 75b via the aqueous medium communication pipes 15a, 16a, 15b and 16b, and constitute a part of the aqueous medium circuits 170a and 170b. . The configuration of the usage unit 105b is the same as the configuration of the usage unit 105a. Therefore, here, only the configuration of the usage unit 105a will be described, and for the configuration of the usage unit 105b, the subscript “b” is attached instead of the subscript “a” indicating the respective portions of the usage unit 105a. The description of is omitted.

The usage unit 105a mainly includes a first usage side heat exchanger 51a, a first usage side expansion valve 52a, a second usage side heat exchanger 151a, a second usage side expansion valve 152a, and a usage side compressor 55a. A refrigerant-water heat exchanger 57a, a refrigerant-water heat exchange side expansion valve 58a, a use-side accumulator 59a, a first circulation pump 71a, a second circulation pump 171a, and a hot water storage tank 161a. Yes. In addition, the structure of the utilization side refrigerant circuit 50a is the same as that of the utilization side refrigerant circuit 50a of 1st Embodiment. For this reason, detailed description of the apparatus 55a, 58a, 59a which comprises only the utilization side refrigerant circuit 50a is abbreviate | omitted here.
The first usage-side heat exchanger 51a is a heat exchanger that functions as a heat-source-side refrigerant radiator by performing heat exchange between the heat-source-side refrigerant and the usage-side refrigerant. The use side heat exchange inlet / outlet pipe 53a is connected to the liquid side of the flow path through which the heat source side refrigerant of the first use side heat exchanger 51a flows, and the heat source side refrigerant of the first use side heat exchanger 51a flows. A first usage-side gas refrigerant tube 54a is connected to the gas side of the flow path. Further, a cascade side liquid refrigerant pipe 66a is connected to the liquid side of the flow path through which the usage side refrigerant flows of the first usage side heat exchanger 51a, and the usage side refrigerant of the first usage side heat exchanger 51a flows. A cascade side gas refrigerant pipe 67a is connected to the gas side of the flow path. The use side heat exchange inlet / outlet connection pipe 53a passes the heat source side refrigerant from the outlet of the first use side heat exchanger 51a functioning as a heat source side refrigerant radiator (more specifically, the liquid refrigerant communication pipe 13). It is a refrigerant pipe for deriving to (1). The first usage-side gas refrigerant pipe 54a is connected to the inlet of the first usage-side heat exchanger 51a that functions as a heat-source-side refrigerant radiator from the outside of the usage unit 105a (more specifically, the gas refrigerant communication pipe 14). It is a refrigerant pipe for introducing a refrigerant. A refrigerant-water heat exchanger 57a is connected to the cascade side liquid refrigerant pipe 66a, and a use side compressor 55a is connected to the cascade side gas refrigerant pipe 67a.

The first use side expansion valve 52a is an electric expansion valve capable of changing the flow rate of the heat source side refrigerant flowing through the first use side heat exchanger 51a by performing opening degree control. It is provided in the pipe 53a.
Thus, the use side compressor 55a, the refrigerant-water heat exchanger 57a, the refrigerant-water heat exchange side expansion valve 58a, the use side heat exchanger 51a, and the use side accumulator 59a are connected via the refrigerant pipes 60a, 66a. Thus, the use-side refrigerant circuit 50a is configured.
The first circulation pump 71a is a mechanism for boosting the aqueous medium. Here, a pump in which a centrifugal or positive displacement pump element (not shown) is driven by the first circulation pump motor 72a is employed. . The first circulation pump 71a is provided in the first usage-side water outlet pipe 73a. The first circulation pump motor 72a can change the rotation speed (that is, the operating frequency) by an inverter device (not shown), thereby enabling capacity control of the first circulation pump 71a.

  The second usage-side heat exchanger 151a is a heat exchanger that functions as an evaporator of the heat source side refrigerant by performing heat exchange between the heat source side refrigerant and the aqueous medium. The liquid side of the flow path through which the heat source side refrigerant of the second usage side heat exchanger 151a flows is connected to the usage side heat exchange inlet / outlet pipe 53a, and the heat source side refrigerant of the second usage side heat exchanger 151a flows. A second usage-side gas refrigerant tube 153a is connected to the gas side of the flow path. That is, the use side heat exchange inlet / outlet connection pipe 53a functions as a refrigerant pipe that connects the outlet of the heat source side refrigerant of the first use side heat exchanger 51a and the inlet of the heat source side refrigerant of the second use side heat exchanger 151a. ing. For this reason, the use side heat exchange inlet / outlet connection pipe 53a is connected to the heat source side from the outlet of the heat source side refrigerant outside the use unit 105a (more specifically, the liquid refrigerant communication pipe 13) and / or the first use side heat exchanger 51a. It is also a refrigerant pipe for introducing the heat source side refrigerant into the inlet of the second usage side heat exchanger 151a which functions as a refrigerant radiator. The second usage-side gas refrigerant pipe 153a is provided with a usage-side heat exchange outlet on-off valve 154a capable of opening / closing control. The use side heat exchange outlet on / off valve 154a is composed of an electromagnetic valve. In addition, the second usage-side water inlet pipe 173a is connected to the inlet side of the flow path through which the aqueous medium of the second usage-side heat exchanger 151a flows, and the aqueous medium of the second usage-side heat exchanger 151a flows. A second usage-side water outlet pipe 174a is connected to the outlet side of the flow path.

  The second circulation pump 171a is a mechanism for boosting the aqueous medium. Here, a pump in which a centrifugal or positive displacement pump element (not shown) is driven by the second circulation pump motor 172a is employed. . The second circulation pump 171a is provided in the second usage-side water outlet pipe 73a. The second circulation pump motor 172a can vary the rotation speed (that is, the operating frequency) by an inverter device (not shown), thereby enabling the capacity control of the second circulation pump 171a. The second usage-side water inlet pipe 173a is branched from a portion upstream of the first circulation pump 71a of the first usage-side water inlet pipe 73a via the cold / hot water switching mechanism 175a. The second usage-side water outlet pipe 174a merges with the first usage-side water outlet pipe 74a. The cold / hot water switching mechanism 175a is an aqueous medium heating / cooling unit provided outside the use unit 105a with the aqueous medium heated in the refrigerant-water heat exchanger 57a or the aqueous medium cooled in the second use side heat exchanger 151a. This is a mechanism for enabling selective exchange with 75a. The cold / hot water switching mechanism 175a is a three-way valve.

The second usage side expansion valve 152a is an electric expansion valve capable of changing the flow rate of the heat source side refrigerant flowing through the second usage side heat exchanger 151a by performing opening degree control, and is connected to the usage side heat exchange inlet / outlet connection. It is provided in the pipe 53a.
The hot water storage tank 161a is installed indoors (here, in the usage unit 105a). The hot water storage tank 161a is a container that stores water as an aqueous medium used for hot water supply. A hot water supply pipe 163a is connected to the upper part of the hot water storage tank 161a to send the hot water medium to a faucet or a shower. A water supply pipe 164a for replenishment is connected. A heat exchange coil 162a is provided in the hot water storage tank 161a.
The heat exchange coil 162a is provided in the hot water storage tank 161a. The heat exchange coil 162a is a heat exchanger that functions as a heater for the aqueous medium in the hot water storage tank 161a by exchanging heat between the aqueous medium circulating in the aqueous medium circuit 170a and the aqueous medium in the hot water storage tank 161a. A hot water storage tank side water inlet pipe 176a branched from the first usage side water outlet pipe 74a is connected to the inlet of the heat exchange coil 162a. In addition, a hot water storage tank side water outlet pipe 178a joined to the first usage side water inlet pipe 73a is connected to the outlet of the heat exchange coil 162a. The hot water storage tank side water inlet pipe 176a is branched from the first usage side water outlet pipe 74a via the heating / hot water switching mechanism 177a. The heating / hot water switching mechanism 177a switches whether the aqueous medium circulating in the aqueous medium circuit 170a is supplied to both the hot water storage tank 161a and the aqueous medium cooling / heating unit 75a or either the hot water storage tank 161a and the aqueous medium cooling / heating unit 75a. Can be done. The heating / hot water switching mechanism 177a is a three-way valve. The hot water storage tank side water outlet pipe 178a merges between the cold / hot water switching mechanism 175a of the first usage side water inlet pipe 73a and the first circulation pump 71a. Thereby, the hot water storage tank 161a can heat the aqueous medium in the hot water storage tank 161a by the aqueous medium circulating in the aqueous medium circuit 170a heated in the utilization unit 105a, and can store it as hot water. Here, as the hot water storage tank 161a, a hot water storage tank of a type that stores an aqueous medium heated by heat exchange with the aqueous medium heated in the usage unit 105a is used. You may employ | adopt the type of hot water storage tank which stores a medium.

  In addition, the utilization unit 105a is provided with various sensors. Specifically, the use unit 105a includes a first use side heat exchange liquid side temperature sensor 61a, a second use side heat exchange gas side temperature sensor 156a, a second use side heat exchange liquid side temperature sensor 155a, Aqueous medium inlet temperature sensor 63a, first aqueous medium outlet temperature sensor 64a, second aqueous medium outlet temperature sensor 159a, usage side suction pressure sensor 68a, usage side discharge pressure sensor 69a, and usage side discharge temperature sensor 157a. A refrigerant-water heat exchanger temperature sensor 158a, a cascade-side liquid refrigerant pipe temperature sensor 160a, and a hot water storage temperature sensor 165a. The first use side heat exchange liquid side temperature sensor 61a is a temperature sensor that detects a first use side heat exchange liquid side temperature Tul1a that is the temperature of the heat source side refrigerant on the liquid side of the first use side heat exchanger 51a. The second usage-side heat exchange gas side temperature sensor 156a is a temperature sensor that detects a second usage-side heat exchange gas side temperature Tug2a that is the temperature of the heat source side refrigerant on the gas side of the second usage-side heat exchanger 151a. The second use side heat exchange liquid side temperature sensor 155a is a temperature sensor that detects a second use side heat exchange liquid side temperature Tul2a that is the temperature of the heat source side refrigerant on the liquid side of the second use side heat exchanger 151a. The aqueous medium inlet temperature sensor 63a is a temperature sensor that detects an aqueous medium inlet temperature Twr that is the temperature of the aqueous medium at the inlet of the refrigerant-water heat exchanger 57a and the inlet of the second usage-side heat exchanger 151a. The first aqueous medium outlet temperature sensor 64a is a temperature sensor that detects an aqueous medium outlet temperature Twl1a that is the temperature of the aqueous medium at the outlet of the refrigerant-water heat exchanger 57a. The second aqueous medium outlet temperature sensor 159a is a temperature sensor that detects an aqueous medium outlet temperature Twl2a that is the temperature of the aqueous medium at the outlet of the second usage-side heat exchanger 151a. The use side suction pressure sensor 68a is a pressure sensor that detects the use side suction pressure Ps2a that is the pressure of the use side refrigerant in the suction of the use side compressor 55a. The use side discharge pressure sensor 69a is a pressure sensor that detects the use side discharge pressure Pd2a that is the pressure of the use side refrigerant in the discharge of the use side compressor 55a. The use side discharge temperature sensor 157a is a temperature sensor that detects a use side discharge temperature Td2a that is the temperature of the use side refrigerant in the discharge of the use side compressor 55a. The refrigerant-water heat exchanger temperature sensor 158a is a temperature sensor that detects the cascade-side refrigerant temperature Tpl1a that is the temperature of the use-side refrigerant on the liquid side of the refrigerant-water heat exchanger 57a. The cascade side liquid refrigerant pipe temperature sensor 160a is a temperature sensor that detects the temperature Tpl2a of the usage side refrigerant on the liquid side of the first usage side heat exchanger 51a. This temperature is a use side refrigerant evaporation temperature corresponding to the saturation temperature of the use side refrigerant in the first use side heat exchanger 51a. The hot water storage temperature sensor 165a is a temperature sensor that detects the hot water storage temperature Twha, which is the temperature of the aqueous medium stored in the hot water storage tank 161a. In addition, the usage unit 105a includes a usage-side control unit 69a that controls the operation of each unit constituting the usage unit 105a. The use side control unit 69a has a microcomputer, a memory, and the like for controlling the use unit 105a. The usage-side control unit 69a can exchange control signals and the like with a remote controller (not shown), and exchange control signals and the like with the heat source side control unit 49 of the heat source unit 102. It has become.

-Aqueous medium heating / cooling unit-
The aqueous medium cooling / heating units 75a and 75b (aqueous medium utilization devices) are installed indoors (for example, each door of an apartment house, each section of a building, etc.). The aqueous medium cooling / heating units 75a and 75b are the same as the aqueous medium heating units 75a and 75b of the first embodiment except that they are used not only for indoor heating but also for indoor cooling. For this reason, detailed description of the aqueous medium air conditioning units 75a and 75b is omitted here.
-Aqueous medium connection pipe-
The aqueous medium communication tubes 15a and 16a have the same configuration as the aqueous medium communication tubes 15a and 16a of the first embodiment. For this reason, detailed description of the aqueous medium communication pipes 15a and 16a is omitted here.
The use side control units 69a and 69b and the heat source side control unit 49 constitute a control unit 101a that controls the operation of the heat pump system 101, and performs the following operations and various controls.

<Operation>
Next, the operation of the heat pump system 101 will be described.
The operation of the heat pump system 101 includes a heating only operation mode, a cooling / heating simultaneous operation mode, and a cooling only operation mode. The all-heating operation mode is an operation mode in which only the heating operation (and / or the hot water supply operation) is performed in a state where only the use units set to the heating operation and the hot water supply operation (heating operation) exist. In the cooling / heating simultaneous operation mode, one of the use units 105a and 105b is set to a cooling operation (cooling operation), and the other of the use units 105a and 105b is set to a heating operation (heating operation) or a hot water supply operation (heating operation). Or a mixed operation of cooling operation and heating operation (and / or hot water supply operation) in a state where at least one of the use units 105a and 105b is set to a cooling hot water supply operation in which the cooling operation and the hot water supply operation are performed simultaneously. This is an operation mode in which The all-cooling operation mode is an operation mode in which only the cooling operation is performed in a state where only the use units set to the cooling operation (cooling operation) exist. The cooling / heating simultaneous operation mode is divided into a cooling / heating simultaneous operation mode (evaporation main) and a cooling / heating simultaneous operation mode (heat dissipation main) according to the heat load of the entire usage units 105a and 105b (the total of the cooling load and the heating load). Can be divided. In the cooling / heating simultaneous operation mode (evaporation main body), the cooling operation and the heating operation (and / or hot water supply operation) of the use units 105a and 105b are mixed, and the heat source is supplied from the use units 105a and 105b to the liquid refrigerant communication tube 13. This is an operation mode in which the heat source side refrigerant is sent to the unit 102. In the cooling / heating simultaneous operation mode (heat radiation main body), the cooling operation and the heating operation (and / or hot water supply operation) of the use units 105 a and 105 b are mixed, and the use unit 105 a is supplied from the heat source unit 102 through the liquid refrigerant communication tube 13. , 105b, an operation mode in which the heat source side refrigerant is sent.

-Heating operation mode-
When only the heating operation (and / or hot water supply operation) of the use units 105a and 105b is performed, in the heat source side refrigerant circuit 120, the first and second heat source side switching mechanisms 23a and 23b are in the heat source side evaporation operation state (FIG. 5). Of the first and second heat source side switching mechanisms 23a, 23b). The third heat source side switching mechanism 39 is switched to the cooling / heating simultaneous operation state (the state indicated by the solid line of the third heat source side switching mechanism 39 in FIG. 5). Further, the suction return expansion valves 30a and 30b are closed. Further, the second use side expansion valves 152a and 152b and the use side heat exchange outlet on / off valves 154a and 154b are closed. Further, the cold / hot water switching mechanisms 175a, 175b and the heating / hot water switching mechanisms 177a, 177b convert the aqueous medium heated in the refrigerant-water heat exchangers 57a, 57b into the aqueous medium cooling / heating units 75a, 75b and / or hot water storage tanks 161a, 161b. It is switched to the state to supply to. Here, description will be given assuming that all of the usage units 105a and 105b are set to the heating operation.

In the heat source side refrigerant circuit 120 in such a state, the low pressure heat source side refrigerant in the refrigeration cycle is sucked into the heat source side compressor 21 through the heat source side suction pipe 21c and compressed to a high pressure in the refrigeration cycle, and then the heat source side refrigerant circuit 120 is heated. It is discharged to the discharge pipe 21b. The high pressure heat source side refrigerant discharged to the heat source side discharge pipe 21b is separated from the refrigerating machine oil in the oil separator 22a. The refrigerating machine oil separated from the heat source side refrigerant in the oil separator 22a is returned to the heat source side suction pipe 21c through the oil return pipe 22b. The high-pressure heat source side refrigerant from which the refrigeration oil is separated is sent from the heat source unit 102 to the discharge refrigerant communication tube 12 through the heat source side discharge branch pipe 21d, the third heat source side switching mechanism 39, and the discharge side shut-off valve 35.
The high-pressure heat source side refrigerant sent to the discharge refrigerant communication tube 12 is branched into two and sent to the use units 105a and 105b.

The high-pressure heat-source-side refrigerant sent to the usage units 105a and 105b is sent to the first usage-side heat exchangers 51a and 51b through the first usage-side gas refrigerant tubes 54a and 54b. The high-pressure heat-source-side refrigerant sent to the first usage-side heat exchangers 51a, 51b is the low-pressure usage-side in the refrigeration cycle circulating in the usage-side refrigerant circuits 50a, 50b in the first usage-side heat exchangers 51a, 51b. Heat is exchanged with the refrigerant to dissipate heat. The high-pressure heat-source-side refrigerant radiated in the first usage-side heat exchangers 51a and 51b is transferred from the usage units 105a and 105b through the first usage-side expansion valves 52a and 52b and the usage-side heat exchange inlet / outlet connection pipes 53a and 53b. It is sent to the connecting pipe 13 and merges.
The heat source side refrigerant sent to the liquid refrigerant communication tube 13 is sent to the heat source unit 102. The heat source side refrigerant sent to the heat source unit 102 is sent to the subcoolers 31a and 31b through the liquid side shut-off valve 33 and the heat source side liquid refrigerant merging pipe 27. The heat source side refrigerant sent to the subcoolers 31a and 31b is sent to the heat source side expansion valves 28a and 28b without performing heat exchange because the heat source side refrigerant does not flow through the suction return pipes 29a and 29b. The heat source side refrigerant sent to the heat source side expansion valves 28a, 28b is depressurized in the heat source side expansion valves 28a, 28b to become a low-pressure gas-liquid two-phase state, and passes through the heat source side liquid refrigerant tubes 27a, 27b. It is sent to the heat exchangers 26a and 26b. The low-pressure heat source side refrigerant sent to the heat source side heat exchangers 26a and 26b evaporates by exchanging heat with outdoor air supplied by the heat source side fans 36a and 36b in the heat source side heat exchangers 26a and 26b. The low-pressure heat-source-side refrigerant evaporated in the heat-source-side heat exchangers 26a and 26b is returned again to the heat-source-side compressor 21 through the heat-source-side gas refrigerant tubes 24a and 24b, the heat-source-side switching mechanisms 23a and 23b, and the heat-source-side suction tube 21c. Inhaled.

  On the other hand, in the usage-side refrigerant circuits 50a and 50b, the low-pressure usage-side refrigerant in the refrigeration cycle circulating through the usage-side refrigerant circuits 50a and 50b is heated by the heat radiation of the heat source-side refrigerant in the first usage-side heat exchangers 51a and 51b. Evaporate. The low-pressure use-side refrigerant evaporated in the first use-side heat exchangers 51a and 51b is sent to the use-side accumulators 59a and 59b through the cascade-side gas refrigerant tubes 67a and 67b. The low-pressure use-side refrigerant sent to the use-side accumulators 59a and 59b is sucked into the use-side compressors 55a and 55b, compressed to a high pressure in the refrigeration cycle, and then discharged to the cascade-side discharge pipes 60a and 60b. The high-pressure use-side refrigerant discharged to the cascade-side discharge pipes 60a and 60b is sent to the refrigerant-water heat exchangers 57a and 57b. The high-pressure use-side refrigerant sent to the refrigerant-water heat exchangers 57a, 57b is an aqueous medium that circulates in the aqueous medium circuits 170a, 170b by the first circulation pumps 71a, 71b in the refrigerant-water heat exchangers 57a, 57b. Heat exchange with the heat. The high-pressure use-side refrigerant radiated in the refrigerant-water heat exchangers 57a, 57b is decompressed in the refrigerant-water heat exchange side expansion valves 58a, 58b to be in a low-pressure gas-liquid two-phase state, and the cascade-side liquid refrigerant pipe It is again sent to the 1st utilization side heat exchanger 51a, 51b through 66a, 66b.

In the aqueous medium circuits 170a and 170b, the aqueous medium circulating through the aqueous medium circuits 170a and 170b is heated by the heat radiation of the heat source side refrigerant in the refrigerant-water heat exchangers 57a and 57b. The aqueous medium heated in the refrigerant-water heat exchangers 57a and 57b is transferred from the usage units 105a and 105b to the aqueous medium communication pipe 16a by the first circulation pumps 71a and 71b through the first usage-side water outlet pipes 74a and 74b. 16b. The aqueous medium sent to the aqueous medium communication pipes 16a and 16b is sent to the aqueous medium cooling / heating units 75a and 75b. The aqueous medium sent to the aqueous medium cooling / heating units 75a and 75b dissipates heat in the heat exchange panels 76a and 76b, thereby heating the indoor walls and the like, and heating the indoor floor.
When the hot water supply operation of the use units 105a and 105b is performed, a heating hot water supply switching mechanism is provided so that the aqueous medium heated in the refrigerant-water heat exchanger is supplied to the hot water storage tank in the use unit performing the hot water supply operation. May be switched. Thereby, the aqueous medium heated in the refrigerant-water heat exchangers 57a and 57b is passed through the first usage-side water outlet pipes 74a and 74b and the hot water tank-side water inlet pipes 176a and 176b by the first circulation pumps 71a and 71b. The hot water storage tanks 161a and 161b are supplied. The heat exchange coils 162a and 162b exchange heat with the aqueous medium in the hot water storage tanks 161a and 161b to dissipate heat to heat the aqueous medium in the hot water storage tanks 161a and 161b.

Further, when the heating operation and the hot water supply operation of the use units 105a and 105b are performed at the same time, in the use unit performing the heating operation and the hot water supply operation, the aqueous medium heated in the refrigerant-water heat exchanger is What is necessary is just to switch a heating hot-water supply switching mechanism so that it may be supplied to a hot water storage tank.
Thus, the operation | movement in the heating only operation mode which performs only the heating operation (and / or hot water supply operation) of utilization unit 105a, 105b is performed.
-Simultaneous cooling / heating operation mode (evaporation mainly)-
When the cooling operation and the heating operation (and / or hot water supply operation) of the use units 105a and 105b are mixed, in the heat source side refrigerant circuit 120, one of the heat source side switching mechanisms 23a and 23b is in the heat source side heat radiation operation state. (The state indicated by the solid lines of the heat source side switching mechanisms 23a and 23b in FIG. 5), and the other of the heat source side switching mechanisms 23a and 23b is in the heat source side evaporation operation state (of the heat source side switching mechanisms 23a and 23b in FIG. 5). (The state indicated by the broken line). The third heat source side switching mechanism 39 is switched to the cooling / heating simultaneous operation state (the state indicated by the solid line of the third heat source side switching mechanism 39 in FIG. 5). Of the suction return expansion valves 30a and 30b, the suction return expansion valve corresponding to the heat source side switching mechanism that is switched to the heat source side evaporation operation state is closed. And about the utilization unit set to air_conditionaing | cooling operation among utilization unit 105a, 105b, a 1st utilization side expansion valve is closed, a utilization side heat exchange outlet on-off valve is opened, and a cold / hot water switching mechanism is 2nd utilization side. The state is switched to a state in which the aqueous medium cooled in the heat exchanger is supplied to the aqueous medium cooling / heating unit. On the other hand, among the usage units 105a and 105b, for the usage unit set to the heating operation (and / or hot water supply operation), the second usage side expansion valve and the usage side heat exchange outlet on / off valve are closed, and the cold / hot water switching mechanism is The state is switched to a state in which the aqueous medium heated in the refrigerant-water heat exchanger is supplied to the aqueous medium cooling / heating unit. Here, it is assumed that the first heat source side switching mechanism 23a is switched to the heat source side heat radiation operation state, the second heat source side switching mechanism 23b is switched to the heat source side evaporation operation state, and the suction return expansion valve 30b is closed. explain. Further, description will be made assuming that the usage unit 105a is set to the cooling operation and the usage unit 105b is set to the heating operation.

  In the heat source side refrigerant circuit 120 in such a state, the low pressure heat source side refrigerant in the refrigeration cycle is sucked into the heat source side compressor 21 through the heat source side suction pipe 21c and compressed to a high pressure in the refrigeration cycle, and then the heat source side refrigerant circuit 120 is heated. It is discharged to the discharge pipe 21b. The high pressure heat source side refrigerant discharged to the heat source side discharge pipe 21b is separated from the refrigerating machine oil in the oil separator 22a. The refrigerating machine oil separated from the heat source side refrigerant in the oil separator 22a is returned to the heat source side suction pipe 21c through the oil return pipe 22b. A part of the high-pressure heat source side refrigerant from which the refrigeration oil is separated is sent to the first heat source side heat exchanger 26a through the first heat source side switching mechanism 23a and the first heat source side gas refrigerant tube 24a, and the rest is the heat source. The refrigerant is sent from the heat source unit 102 to the discharge refrigerant communication pipe 12 through the side discharge branch pipe 21d and the discharge side closing valve 35. The high-pressure heat-source-side refrigerant sent to the first heat-source-side heat exchanger 26a radiates heat by exchanging heat with outdoor air supplied by the first heat-source-side fan 36a in the first heat-source-side heat exchanger 26a. The high-pressure heat-source-side refrigerant that has radiated heat in the first heat-source-side heat exchanger 26a is sent to the first subcooler 31a through the first heat-source-side expansion valve 28a. The heat-source-side refrigerant sent to the first subcooler 31a exchanges heat with the heat-source-side refrigerant branched from the first heat-source-side liquid refrigerant tube 27a to the first suction return tube 29a so as to be in a supercooled state. To be cooled. The heat source side refrigerant flowing through the first suction return pipe 29a is returned to the heat source side suction pipe 21c. The heat-source-side refrigerant cooled in the first subcooler 31a is sent to the heat-source-side liquid refrigerant merging pipe 27 through the heat-source-side liquid refrigerant pipe 27a.

The high-pressure heat source side refrigerant sent to the discharge refrigerant communication tube 12 is sent to the use unit 105b.
The high-pressure heat-source-side refrigerant sent to the usage unit 105b is sent to the first usage-side heat exchanger 51b through the first usage-side gas refrigerant tube 54b. The high-pressure heat-source-side refrigerant sent to the first usage-side heat exchanger 51b exchanges heat with the low-pressure usage-side refrigerant in the refrigeration cycle circulating in the usage-side refrigerant circuit 50b in the first usage-side heat exchanger 51b. To dissipate heat. The high-pressure heat-source-side refrigerant radiated in the first usage-side heat exchanger 51b is sent from the usage unit 105b to the liquid refrigerant communication tube 13 through the first usage-side expansion valve 52b and the usage-side heat exchange inlet / outlet connection tube 53b.
A part of the heat source side refrigerant sent from the use unit 105 b to the liquid refrigerant communication tube 13 is sent to the use unit 105 a and the rest is sent to the heat source unit 102.

The heat-source-side refrigerant sent from the liquid refrigerant communication tube 13 to the usage unit 105a is sent to the second usage-side expansion valve 152a. The heat-source-side refrigerant sent to the second usage-side expansion valve 152a is depressurized by the second usage-side expansion valve 152a to be in a low-pressure gas-liquid two-phase state, through the usage-side heat exchange inlet / outlet connection pipe 53a. It is sent to the use side heat exchanger 151a. The low-pressure heat source side refrigerant sent to the second usage side heat exchanger 151a exchanges heat with the aqueous medium circulating in the aqueous medium circuit 170a by the second circulation pump 171a in the second usage side heat exchanger 151a. Evaporate. The low-pressure heat source side refrigerant evaporated in the second usage side heat exchanger 151a is sent from the usage unit 105a to the suction refrigerant communication tube 14 through the usage side heat exchange outlet on-off valve 154a and the second usage side gas refrigerant tube 153a.
The low-pressure heat source side refrigerant sent to the suction refrigerant communication tube 14 is sent to the heat source unit 102. The low-pressure heat source side refrigerant sent to the heat source unit 102 is sent to the suction side closing valve 34 and the heat source side gas refrigerant pipe 25. Further, the heat source side refrigerant sent from the liquid refrigerant communication tube 13 to the heat source unit 102 is sent to the heat source side liquid refrigerant merging tube 27 through the liquid side shut-off valve 33, and the heat source from the first heat source side liquid refrigerant tube 27a. Merge with side refrigerant. The liquid refrigerant merged in the heat source side liquid refrigerant merging pipe 27 is sent to the second subcooler 31b through the second heat source side liquid refrigerant pipe 27b. The heat source side refrigerant sent to the second subcooler 31b is sent to the second heat source side expansion valve 28b without performing heat exchange because the heat source side refrigerant does not flow through the second suction return pipe 29b. The heat source side refrigerant sent to the second heat source side expansion valve 28b is depressurized by the second heat source side expansion valve 28b to be in a low-pressure gas-liquid two-phase state, and is passed through the second heat source side liquid refrigerant tube 27b to the second. It is sent to the heat source side heat exchanger 26b. The low-pressure heat source side refrigerant sent to the second heat source side heat exchanger 26b evaporates by exchanging heat with the outdoor air supplied by the second heat source side fan 36b in the second heat source side heat exchanger 26b. The low-pressure heat source side refrigerant evaporated in the second heat source side heat exchanger 26b is sent to the heat source side gas refrigerant tube 25 through the second heat source side gas refrigerant tube 24b, the second heat source side switching mechanism 23b, and the communication tube 38. The heat source side refrigerant sent from the suction refrigerant communication tube 14 to the heat source unit 102 is merged. The low-pressure heat source side refrigerant joined in the heat source side gas refrigerant pipe 25 is again sucked into the heat source side compressor 21 through the heat source side suction pipe 21c.

On the other hand, in the aqueous medium circuit 170a, the aqueous medium circulating in the aqueous medium circuit 170a is cooled by evaporation of the heat source side refrigerant in the second usage-side heat exchanger 151a. The aqueous medium cooled in the second usage-side heat exchanger 151a is transferred from the usage unit 105a to the aqueous medium communication pipe by the second circulation pump 171a through the second usage-side water outlet pipe 174a and the first usage-side water outlet pipe 74a. 16a. The aqueous medium sent to the aqueous medium communication pipe 16a is sent to the aqueous medium cooling / heating unit 75a. The aqueous medium sent to the aqueous medium cooling / heating unit 75a is heated in the heat exchange panel 76a, thereby cooling the indoor wall or the like, or the indoor floor.
In the aqueous medium circuit 170b, the aqueous medium circulating in the aqueous medium circuit 170b is heated by the heat radiation of the heat source side refrigerant in the refrigerant-water heat exchanger 57b. The aqueous medium heated in the refrigerant-water heat exchanger 57b is sent from the usage unit 105b to the aqueous medium communication pipe 16b through the first usage-side water outlet pipe 74b by the first circulation pump 71b. The aqueous medium sent to the aqueous medium communication pipe 16b is sent to the aqueous medium cooling / heating unit 75b. The aqueous medium sent to the aqueous medium cooling / heating unit 75b dissipates heat in the heat exchange panel 76b, thereby heating the indoor wall or the like, or heating the indoor floor.

When the hot water supply operation of the use units 105a and 105b is performed, a heating hot water supply switching mechanism is provided so that the aqueous medium heated in the refrigerant-water heat exchanger is supplied to the hot water storage tank in the use unit performing the hot water supply operation. May be switched. Thus, the aqueous medium heated in the refrigerant-water heat exchanger is supplied to the hot water storage tank by the first circulation pump through the first usage side water outlet pipe and the hot water tank side water inlet pipe. In the heat exchange coil, heat exchange is performed with the aqueous medium in the hot water storage tank to dissipate heat, and the aqueous medium in the hot water storage tank is heated.
Further, when the heating operation and the hot water supply operation of the use units 105a and 105b are performed at the same time, in the use unit performing the heating operation and the hot water supply operation, the aqueous medium heated in the refrigerant-water heat exchanger is What is necessary is just to switch a heating hot-water supply switching mechanism so that it may be supplied to a hot water storage tank.

In this manner, with one of the usage units 105a and 105b set to the cooling operation and the other of the usage units 105a and 105b set to the heating operation, the cooling operation and the heating operation (and / or the hot water supply operation) are performed. The operation in the cooling and heating simultaneous operation mode (evaporation main body) in which the operation is mixed is performed.
Further, at least one of the usage units 105a and 105b can be set to a cooling hot water supply operation in which a cooling operation and a hot water supply operation are performed simultaneously. In this case, in the heat source side refrigerant circuit 120, as described above, one of the heat source side switching mechanisms 23a and 23b is in a heat source side heat radiation operation state (indicated by the solid line of the heat source side switching mechanisms 23a and 23b in FIG. 5). State), and the other of the heat source side switching mechanisms 23a, 23b is switched to the heat source side evaporation operation state (the state indicated by the broken lines of the heat source side switching mechanisms 23a, 23b in FIG. 5). The third heat source side switching mechanism 39 is switched to the cooling / heating simultaneous operation state (the state indicated by the solid line of the third heat source side switching mechanism 39 in FIG. 5). Of the suction return expansion valves 30a and 30b, the suction return expansion valve corresponding to the heat source side switching mechanism that is switched to the heat source side evaporation operation state is closed. And about the utilization unit set to cooling water supply operation among utilization unit 105a, 105b, a 1st and 2nd utilization side expansion valve is opened, a utilization side heat exchange outlet on-off valve is opened, and a cold / hot water switching mechanism is provided. A state in which the aqueous medium cooled in the second usage-side heat exchanger is switched to a state in which the aqueous medium is supplied to the aqueous medium cooling / heating unit, and the heating / hot water switching mechanism supplies the aqueous medium heated in the refrigerant-water heat exchanger to the hot water storage tank Can be switched to. Here, description will be made on the assumption that all of the use units 105a and 105b are set to the cooling hot water supply operation.

  In the heat source side refrigerant circuit 120 in such a state, the low pressure heat source side refrigerant in the refrigeration cycle is sucked into the heat source side compressor 21 through the heat source side suction pipe 21c and compressed to a high pressure in the refrigeration cycle, and then the heat source side refrigerant circuit 120 is heated. It is discharged to the discharge pipe 21b. The high pressure heat source side refrigerant discharged to the heat source side discharge pipe 21b is separated from the refrigerating machine oil in the oil separator 22a. The refrigerating machine oil separated from the heat source side refrigerant in the oil separator 22a is returned to the heat source side suction pipe 21c through the oil return pipe 22b. A part of the high-pressure heat source side refrigerant from which the refrigeration oil is separated is sent to the first heat source side heat exchanger 26a through the first heat source side switching mechanism 23a and the first heat source side gas refrigerant tube 24a, and the rest is the heat source. The refrigerant is sent from the heat source unit 102 to the discharge refrigerant communication pipe 12 through the side discharge branch pipe 21d and the discharge side closing valve 35. The high-pressure heat-source-side refrigerant sent to the first heat-source-side heat exchanger 26a radiates heat by exchanging heat with outdoor air supplied by the first heat-source-side fan 36a in the first heat-source-side heat exchanger 26a. The high-pressure heat-source-side refrigerant that has radiated heat in the first heat-source-side heat exchanger 26a is sent to the first subcooler 31a through the first heat-source-side expansion valve 28a. The heat-source-side refrigerant sent to the first subcooler 31a exchanges heat with the heat-source-side refrigerant branched from the first heat-source-side liquid refrigerant tube 27a to the first suction return tube 29a so as to be in a supercooled state. To be cooled. The heat source side refrigerant flowing through the first suction return pipe 29a is returned to the heat source side suction pipe 21c. The heat-source-side refrigerant cooled in the first subcooler 31a is sent to the heat-source-side liquid refrigerant merging pipe 27 through the heat-source-side liquid refrigerant pipe 27a.

The high-pressure heat source side refrigerant sent to the discharge refrigerant communication tube 12 is branched into two and sent to the use units 105a and 105b.
The high-pressure heat-source-side refrigerant sent to the usage units 105a and 105b is sent to the first usage-side heat exchangers 51a and 51b through the first usage-side gas refrigerant tubes 54a and 54b. The high-pressure heat-source-side refrigerant sent to the first usage-side heat exchangers 51a, 51b is the low-pressure usage-side in the refrigeration cycle circulating in the usage-side refrigerant circuits 50a, 50b in the first usage-side heat exchangers 51a, 51b. Heat is exchanged with the refrigerant to dissipate heat. The high-pressure heat-source-side refrigerant radiated in the first usage-side heat exchangers 51a and 51b is sent to the usage-side heat exchange inlet / outlet connection pipes 53a and 53b through the first usage-side expansion valves 52a and 52b. A part of the heat source side refrigerant sent to the use side heat exchange inlet / outlet connection pipes 53a and 53b is sent to the liquid refrigerant communication pipe 13 and merged, and the rest is sent to the second use side expansion valves 152a and 152b.

The heat-source-side refrigerant sent to the liquid refrigerant communication tube 13 and merged is sent to the heat source unit 102.
The heat-source-side refrigerant sent to the second usage-side expansion valves 152a and 152b is depressurized by the second usage-side expansion valves 152a and 152b to be in a low-pressure gas-liquid two-phase state, and the usage-side heat exchange inlet / outlet connection pipe 53a. , 53b to the second usage side heat exchangers 151a, 151b. The low-pressure heat-source-side refrigerant sent to the second usage-side heat exchangers 151a and 151b circulates in the aqueous medium circuits 170a and 170b by the second circulation pumps 171a and 171b in the second usage-side heat exchangers 151a and 151b. Evaporates by exchanging heat with the aqueous medium. The low-pressure heat-source-side refrigerant evaporated in the second usage-side heat exchangers 151a and 151b is sucked from the usage units 105a and 105b through the usage-side heat exchange outlet on / off valves 154a and 154b and the second usage-side gas refrigerant tubes 153a and 153b. It is sent to the refrigerant communication pipe 14 and merges.

  The low-pressure heat source side refrigerant sent to the suction refrigerant communication tube 14 is sent to the heat source unit 102. The low-pressure heat source side refrigerant sent to the heat source unit 102 is sent to the suction side closing valve 34 and the heat source side gas refrigerant pipe 25. Further, the heat source side refrigerant sent from the liquid refrigerant communication tube 13 to the heat source unit 102 is sent to the heat source side liquid refrigerant merging tube 27 through the liquid side shut-off valve 33, and the heat source from the first heat source side liquid refrigerant tube 27a. Merge with side refrigerant. The liquid refrigerant merged in the heat source side liquid refrigerant merging pipe 27 is sent to the second subcooler 31b through the second heat source side liquid refrigerant pipe 27b. The heat source side refrigerant sent to the second subcooler 31b is sent to the second heat source side expansion valve 28b without performing heat exchange because the heat source side refrigerant does not flow through the second suction return pipe 29b. The heat source side refrigerant sent to the second heat source side expansion valve 28b is depressurized by the second heat source side expansion valve 28b to be in a low-pressure gas-liquid two-phase state, and is passed through the second heat source side liquid refrigerant tube 27b to the second. It is sent to the heat source side heat exchanger 26b. The low-pressure heat source side refrigerant sent to the second heat source side heat exchanger 26b evaporates by exchanging heat with the outdoor air supplied by the second heat source side fan 36b in the second heat source side heat exchanger 26b. The low-pressure heat source side refrigerant evaporated in the second heat source side heat exchanger 26b is sent to the heat source side gas refrigerant tube 25 through the second heat source side gas refrigerant tube 24b, the second heat source side switching mechanism 23b, and the communication tube 38. The heat source side refrigerant sent from the suction refrigerant communication tube 14 to the heat source unit 102 is merged. The low-pressure heat source side refrigerant joined in the heat source side gas refrigerant pipe 25 is again sucked into the heat source side compressor 21 through the heat source side suction pipe 21c.

On the other hand, in the aqueous medium circuits 170a and 170b, the aqueous medium circulating through the aqueous medium circuits 170a and 170b is cooled by evaporation of the heat source side refrigerant in the second usage-side heat exchangers 151a and 151b. The aqueous medium cooled in the second usage-side heat exchangers 151a and 151b is passed through the second usage-side water outlet pipes 174a and 174b and the first usage-side water outlet pipes 74a and 74b by the second circulation pumps 171a and 171b. It is sent from the use units 105a and 105b to the aqueous medium communication pipes 16a and 16b. The aqueous medium sent to the aqueous medium communication pipes 16a and 16b is sent to the aqueous medium cooling / heating units 75a and 75b. The aqueous medium sent to the aqueous medium cooling / heating units 75a and 75b is heated in the heat exchange panels 76a and 76b, thereby cooling the indoor walls and the like and cooling the indoor floor.
In the aqueous medium circuits 170a and 170b, the aqueous medium circulating through the aqueous medium circuits 170a and 170b is heated by the heat radiation of the heat source side refrigerant in the refrigerant-water heat exchangers 57a and 57b. The aqueous medium heated in the refrigerant-water heat exchangers 57a and 57b is stored in the hot water storage tank by the first circulation pumps 71a and 71b through the first usage side water outlet pipes 74a and 74b and the hot water storage tank side water inlet pipes 176a and 176b. 161a and 161b. The heat exchange coils 162a and 162b exchange heat with the aqueous medium in the hot water storage tanks 161a and 161b to dissipate heat to heat the aqueous medium in the hot water storage tanks 161a and 161b.
In this way, an operation in which the cooling operation and the heating operation (and / or the hot water supply operation) are mixed in a state where at least one of the use units 105a and 105b is set to the cooling hot water supply operation in which the cooling operation and the hot water supply operation are performed simultaneously. The operation in the simultaneous cooling and heating operation mode (evaporation main body) is performed.

-Cooling and heating simultaneous operation mode (mainly heat dissipation)-
When the cooling operation and the heating operation (and / or hot water supply operation) of the use units 105a and 105b are mixed, in the heat source side refrigerant circuit 120, one of the heat source side switching mechanisms 23a and 23b is in the heat source side heat radiation operation state. (The state indicated by the solid lines of the heat source side switching mechanisms 23a and 23b in FIG. 5), and the other of the heat source side switching mechanisms 23a and 23b is in the heat source side evaporation operation state (of the heat source side switching mechanisms 23a and 23b in FIG. 5). (The state indicated by the broken line). The third heat source side switching mechanism 39 is switched to the cooling / heating simultaneous operation state (the state indicated by the solid line of the third heat source side switching mechanism 39 in FIG. 5). Of the suction return expansion valves 30a and 30b, the suction return expansion valve corresponding to the heat source side switching mechanism that is switched to the heat source side evaporation operation state is closed. And about the utilization unit set to air_conditionaing | cooling operation among utilization unit 105a, 105b, a 1st utilization side expansion valve is closed, a utilization side heat exchange outlet on-off valve is opened, and a cold / hot water switching mechanism is 2nd utilization side. The state is switched to a state in which the aqueous medium cooled in the heat exchanger is supplied to the aqueous medium cooling / heating unit. On the other hand, among the usage units 105a and 105b, for the usage unit set to the heating operation (and / or hot water supply operation), the second usage side expansion valve and the usage side heat exchange outlet on / off valve are closed, and the cold / hot water switching mechanism is The state is switched to a state in which the aqueous medium heated in the refrigerant-water heat exchanger is supplied to the aqueous medium cooling / heating unit. Here, it is assumed that the first heat source side switching mechanism 23a is switched to the heat source side heat radiation operation state, the second heat source side switching mechanism 23b is switched to the heat source side evaporation operation state, and the suction return expansion valve 30b is closed. explain. Further, description will be made assuming that the usage unit 105a is set to the cooling operation and the usage unit 105b is set to the heating operation.

  In the heat source side refrigerant circuit 120 in such a state, the low pressure heat source side refrigerant in the refrigeration cycle is sucked into the heat source side compressor 21 through the heat source side suction pipe 21c and compressed to a high pressure in the refrigeration cycle, and then the heat source side refrigerant circuit 120 is heated. It is discharged to the discharge pipe 21b. The high pressure heat source side refrigerant discharged to the heat source side discharge pipe 21b is separated from the refrigerating machine oil in the oil separator 22a. The refrigerating machine oil separated from the heat source side refrigerant in the oil separator 22a is returned to the heat source side suction pipe 21c through the oil return pipe 22b. A part of the high-pressure heat source side refrigerant from which the refrigeration oil is separated is sent to the first heat source side heat exchanger 26a through the first heat source side switching mechanism 23a and the first heat source side gas refrigerant tube 24a, and the rest is the heat source. The refrigerant is sent from the heat source unit 102 to the discharge refrigerant communication pipe 12 through the side discharge branch pipe 21d and the discharge side closing valve 35. The high-pressure heat-source-side refrigerant sent to the first heat-source-side heat exchanger 26a radiates heat by exchanging heat with outdoor air supplied by the first heat-source-side fan 36a in the first heat-source-side heat exchanger 26a. The high-pressure heat-source-side refrigerant that has radiated heat in the first heat-source-side heat exchanger 26a is sent to the first subcooler 31a through the first heat-source-side expansion valve 28a. The heat-source-side refrigerant sent to the first subcooler 31a exchanges heat with the heat-source-side refrigerant branched from the first heat-source-side liquid refrigerant tube 27a to the first suction return tube 29a so as to be in a supercooled state. To be cooled. The heat source side refrigerant flowing through the first suction return pipe 29a is returned to the heat source side suction pipe 21c. The heat-source-side refrigerant cooled in the first subcooler 31a is sent to the heat-source-side liquid refrigerant merging pipe 27 through the heat-source-side liquid refrigerant pipe 27a. A part of the high-pressure heat source side refrigerant sent to the heat source side liquid refrigerant junction tube 27 is sent to the liquid refrigerant communication tube 13 through the liquid side shut-off valve 33, and the rest is sent to the second heat source side liquid refrigerant tube 27b. .

The high-pressure heat source side refrigerant sent to the discharge refrigerant communication tube 12 is sent to the use unit 105b.
The high-pressure heat-source-side refrigerant sent to the usage unit 105b is sent to the first usage-side heat exchanger 51b through the first usage-side gas refrigerant tube 54b. The high-pressure heat-source-side refrigerant sent to the first usage-side heat exchanger 51b exchanges heat with the low-pressure usage-side refrigerant in the refrigeration cycle circulating in the usage-side refrigerant circuit 50b in the first usage-side heat exchanger 51b. To dissipate heat. The high-pressure heat-source-side refrigerant radiated in the first usage-side heat exchanger 51b is sent from the usage units 105a and 105b to the liquid refrigerant communication tube 13 through the first usage-side expansion valve 52b and the usage-side heat exchange inlet / outlet connection tube 53b. Thus, the heat source side refrigerant sent from the heat source unit 102 to the liquid refrigerant communication tube 13 merges.

The heat-source-side refrigerant that merges in the liquid refrigerant communication tube 13 is sent to the use unit 105a.
The heat-source-side refrigerant sent to the usage unit 105a is sent to the second usage-side expansion valve 152a. The heat-source-side refrigerant sent to the second usage-side expansion valve 152a is depressurized by the second usage-side expansion valve 152a to be in a low-pressure gas-liquid two-phase state, through the usage-side heat exchange inlet / outlet connection pipe 53a. It is sent to the use side heat exchanger 151a. The low-pressure heat-source-side refrigerant sent to the second usage-side heat exchanger 151a evaporates in the second usage-side heat exchanger 151a by exchanging heat with the aqueous medium circulating in the aqueous medium circuit 170a by the circulation pump 71a. . The low-pressure heat source side refrigerant evaporated in the second usage side heat exchanger 151a is sent from the usage unit 105a to the suction refrigerant communication tube 14 through the usage side heat exchange outlet on-off valve 154a and the second usage side gas refrigerant tube 153a.
The low-pressure heat source side refrigerant sent to the suction refrigerant communication tube 14 is sent to the heat source unit 102. The low-pressure heat source side refrigerant sent to the heat source unit 102 is sent to the suction side closing valve 34 and the heat source side gas refrigerant pipe 25. The heat source side refrigerant sent from the heat source side liquid refrigerant merging pipe 27 to the second heat source side liquid refrigerant pipe 27b is sent to the second subcooler 31b. The heat source side refrigerant sent to the second subcooler 31b is sent to the second heat source side expansion valve 28b without performing heat exchange because the heat source side refrigerant does not flow through the second suction return pipe 29b. The heat source side refrigerant sent to the second heat source side expansion valve 28b is depressurized by the second heat source side expansion valve 28b to be in a low-pressure gas-liquid two-phase state, and is passed through the second heat source side liquid refrigerant tube 27b to the second. It is sent to the heat source side heat exchanger 26b. The low-pressure heat source side refrigerant sent to the second heat source side heat exchanger 26b evaporates by exchanging heat with the outdoor air supplied by the second heat source side fan 36b in the second heat source side heat exchanger 26b. The low-pressure heat source side refrigerant evaporated in the second heat source side heat exchanger 26b is sent to the heat source side gas refrigerant tube 25 through the second heat source side gas refrigerant tube 24b, the second heat source side switching mechanism 23b, and the communication tube 38. The heat source side refrigerant sent from the suction refrigerant communication tube 14 to the heat source unit 102 is merged. The low-pressure heat source side refrigerant joined in the heat source side gas refrigerant pipe 25 is again sucked into the heat source side compressor 21 through the heat source side suction pipe 21c.

On the other hand, in the aqueous medium circuit 170a, the aqueous medium circulating in the aqueous medium circuit 170a is cooled by evaporation of the heat source side refrigerant in the second usage-side heat exchanger 151a. The aqueous medium cooled in the second usage-side heat exchanger 151a is supplied to the second usage-side water outlet pipe 174a and the first usage-side water outlet pipe 74a through the second usage-side water outlet pipe 174a by the second circulation pump 171a. And sent from the use unit 105a to the aqueous medium communication pipe 16a. The aqueous medium sent to the aqueous medium communication pipe 16a is sent to the aqueous medium cooling / heating unit 75a. The aqueous medium sent to the aqueous medium cooling / heating unit 75a is heated in the heat exchange panel 76a, thereby cooling the indoor wall or the like, or the indoor floor.
In the aqueous medium circuit 170b, the aqueous medium circulating in the aqueous medium circuit 170b is heated by the heat radiation of the heat source side refrigerant in the refrigerant-water heat exchanger 57b. The aqueous medium heated in the refrigerant-water heat exchanger 57b is sent from the usage unit 105b to the aqueous medium communication pipe 16b through the first usage-side water outlet pipe 74b by the first circulation pump 71b. The aqueous medium sent to the aqueous medium communication pipe 16b is sent to the aqueous medium cooling / heating unit 75b. The aqueous medium sent to the aqueous medium cooling / heating unit 75b dissipates heat in the heat exchange panel 76b, thereby heating the indoor wall or the like, or heating the indoor floor.

When the hot water supply operation of the use units 105a and 105b is performed, a heating hot water supply switching mechanism is provided so that the aqueous medium heated in the refrigerant-water heat exchanger is supplied to the hot water storage tank in the use unit performing the hot water supply operation. May be switched. Thus, the aqueous medium heated in the refrigerant-water heat exchanger is supplied to the hot water storage tank by the first circulation pump through the first usage side water outlet pipe and the hot water tank side water inlet pipe. In the heat exchange coil, heat exchange is performed with the aqueous medium in the hot water storage tank to dissipate heat, and the aqueous medium in the hot water storage tank is heated.
Further, when the heating operation and the hot water supply operation of the use units 105a and 105b are performed at the same time, in the use unit performing the heating operation and the hot water supply operation, the aqueous medium heated in the refrigerant-water heat exchanger is What is necessary is just to switch a heating hot-water supply switching mechanism so that it may be supplied to a hot water storage tank.

In this way, in the state where one of the use units 105a and 105b is set to the cooling operation and the other of the use units 105a and 105b is set to the heating operation, the cooling operation and the heating operation (and / or the hot water supply operation) are performed. The operation is performed in the cooling and heating simultaneous operation mode (mainly heat dissipation) in which the operation is mixed.
Further, at least one of the usage units 105a and 105b can be set to a cooling hot water supply operation in which a cooling operation and a hot water supply operation are performed simultaneously. In this case, in the heat source side refrigerant circuit 120, as described above, one of the heat source side switching mechanisms 23a and 23b is in a heat source side heat radiation operation state (indicated by the solid line of the heat source side switching mechanisms 23a and 23b in FIG. 5). State), and the other of the heat source side switching mechanisms 23a, 23b is switched to the heat source side evaporation operation state (the state indicated by the broken lines of the heat source side switching mechanisms 23a, 23b in FIG. 5). The third heat source side switching mechanism 39 is switched to the cooling / heating simultaneous operation state (the state indicated by the solid line of the third heat source side switching mechanism 39 in FIG. 5). Of the suction return expansion valves 30a and 30b, the suction return expansion valve corresponding to the heat source side switching mechanism that is switched to the heat source side evaporation operation state is closed. And about the utilization unit set to cooling water supply operation among utilization unit 105a, 105b, a 1st and 2nd utilization side expansion valve is opened, a utilization side heat exchange outlet on-off valve is opened, and a cold / hot water switching mechanism is provided. A state in which the aqueous medium cooled in the second usage-side heat exchanger is switched to a state in which the aqueous medium is supplied to the aqueous medium cooling / heating unit, and the heating / hot water switching mechanism supplies the aqueous medium heated in the refrigerant-water heat exchanger to the hot water storage tank Can be switched to. Here, description will be made on the assumption that all of the use units 105a and 105b are set to the cooling hot water supply operation.

  In the heat source side refrigerant circuit 120 in such a state, the low pressure heat source side refrigerant in the refrigeration cycle is sucked into the heat source side compressor 21 through the heat source side suction pipe 21c and compressed to a high pressure in the refrigeration cycle, and then the heat source side refrigerant circuit 120 is heated. It is discharged to the discharge pipe 21b. The high pressure heat source side refrigerant discharged to the heat source side discharge pipe 21b is separated from the refrigerating machine oil in the oil separator 22a. The refrigerating machine oil separated from the heat source side refrigerant in the oil separator 22a is returned to the heat source side suction pipe 21c through the oil return pipe 22b. A part of the high-pressure heat source side refrigerant from which the refrigeration oil is separated is sent to the first heat source side heat exchanger 26a through the first heat source side switching mechanism 23a and the first heat source side gas refrigerant tube 24a, and the rest is the heat source. The refrigerant is sent from the heat source unit 102 to the discharge refrigerant communication pipe 12 through the side discharge branch pipe 21d and the discharge side closing valve 35. The high-pressure heat-source-side refrigerant sent to the first heat-source-side heat exchanger 26a radiates heat by exchanging heat with outdoor air supplied by the first heat-source-side fan 36a in the first heat-source-side heat exchanger 26a. The high-pressure heat-source-side refrigerant that has radiated heat in the first heat-source-side heat exchanger 26a is sent to the first subcooler 31a through the first heat-source-side expansion valve 28a. The heat-source-side refrigerant sent to the first subcooler 31a exchanges heat with the heat-source-side refrigerant branched from the first heat-source-side liquid refrigerant tube 27a to the first suction return tube 29a so as to be in a supercooled state. To be cooled. The heat source side refrigerant flowing through the first suction return pipe 29a is returned to the heat source side suction pipe 21c. The heat-source-side refrigerant cooled in the first subcooler 31a is sent to the heat-source-side liquid refrigerant merging pipe 27 through the heat-source-side liquid refrigerant pipe 27a. A part of the high-pressure heat source side refrigerant sent to the heat source side liquid refrigerant junction tube 27 is sent to the liquid refrigerant communication tube 13 through the liquid side shut-off valve 33, and the rest is sent to the second heat source side liquid refrigerant tube 27b. .

The high-pressure heat source side refrigerant sent to the discharge refrigerant communication tube 12 is branched into two and sent to the use units 105a and 105b.
The high-pressure heat-source-side refrigerant sent from the discharge refrigerant communication tube 12 to the usage units 105a and 105b is sent to the first usage-side heat exchangers 51a and 51b through the first usage-side gas refrigerant tubes 54a and 54b. The high-pressure heat-source-side refrigerant sent to the first usage-side heat exchangers 51a, 51b is the low-pressure usage-side in the refrigeration cycle circulating in the usage-side refrigerant circuits 50a, 50b in the first usage-side heat exchangers 51a, 51b. Heat is exchanged with the refrigerant to dissipate heat. The high-pressure heat-source-side refrigerant radiated in the first usage-side heat exchangers 51a and 51b is sent to the usage-side heat exchange inlet / outlet connection pipes 53a and 53b through the first usage-side expansion valves 52a and 52b.
The heat-source-side refrigerant sent to the liquid refrigerant communication tube 13 is branched into two and sent to the usage units 105a and 105b.

  The high-pressure heat-source-side refrigerant sent from the liquid refrigerant communication tube 13 to the utilization units 105a and 105b is heat-source-side refrigerant that has radiated heat in the first utilization-side heat exchangers 51a and 51b in the utilization-side heat exchange inlet / outlet connection tubes 53a and 53b. To join. The heat-source-side refrigerant merged in the use-side heat exchange inlet / outlet connection pipes 53a and 53b is sent to the second use-side expansion valves 152a and 152b. The heat-source-side refrigerant sent to the second usage-side expansion valves 152a and 152b is depressurized by the second usage-side expansion valves 152a and 152b to be in a low-pressure gas-liquid two-phase state, and the usage-side heat exchange inlet / outlet connection pipe 53a. , 53b to the second usage side heat exchangers 151a, 151b. The low-pressure heat-source-side refrigerant sent to the second usage-side heat exchangers 151a and 151b circulates in the aqueous medium circuits 170a and 170b by the second circulation pumps 171a and 171b in the second usage-side heat exchangers 151a and 151b. Evaporates by exchanging heat with the aqueous medium. The low-pressure heat source side refrigerant evaporated in the second usage side heat exchangers 151a and 151b is sucked from the usage units 105a and 105b through the usage side heat exchange outlet on / off valves 154a and 154b and the second usage side gas refrigerant pipes 153a and 153b. It is sent to the refrigerant communication pipe 14 and merges.

  The low-pressure heat source side refrigerant sent to the suction refrigerant communication tube 14 is sent to the heat source unit 102. The low-pressure heat source side refrigerant sent to the heat source unit 102 is sent to the suction side closing valve 34 and the heat source side gas refrigerant pipe 25. The heat source side refrigerant sent from the heat source side liquid refrigerant merging pipe 27 to the second heat source side liquid refrigerant pipe 27b is sent to the second subcooler 31b. The heat source side refrigerant sent to the second subcooler 31b is sent to the second heat source side expansion valve 28b without performing heat exchange because the heat source side refrigerant does not flow through the second suction return pipe 29b. The heat source side refrigerant sent to the second heat source side expansion valve 28b is depressurized by the second heat source side expansion valve 28b to be in a low-pressure gas-liquid two-phase state, and is passed through the second heat source side liquid refrigerant tube 27b to the second. It is sent to the heat source side heat exchanger 26b. The low-pressure heat source side refrigerant sent to the second heat source side heat exchanger 26b evaporates by exchanging heat with the outdoor air supplied by the second heat source side fan 36b in the second heat source side heat exchanger 26b. The low-pressure heat source side refrigerant evaporated in the second heat source side heat exchanger 26b is sent to the heat source side gas refrigerant tube 25 through the second heat source side gas refrigerant tube 24b, the second heat source side switching mechanism 23b, and the communication tube 38. The heat source side refrigerant sent from the suction refrigerant communication tube 14 to the heat source unit 102 is merged. The low-pressure heat source side refrigerant joined in the heat source side gas refrigerant pipe 25 is again sucked into the heat source side compressor 21 through the heat source side suction pipe 21c.

On the other hand, in the aqueous medium circuits 170a and 170b, the aqueous medium circulating through the aqueous medium circuits 170a and 170b is cooled by evaporation of the heat source side refrigerant in the second usage-side heat exchangers 151a and 151b. The aqueous medium cooled in the second usage-side heat exchangers 151a and 151b is passed through the second usage-side water outlet pipes 174a and 174b and the first usage-side water outlet pipes 74a and 74b by the second circulation pumps 171a and 171b. It is sent from the use units 105a and 105b to the aqueous medium communication pipes 16a and 16b. The aqueous medium sent to the aqueous medium communication pipes 16a and 16b is sent to the aqueous medium cooling / heating units 75a and 75b. The aqueous medium sent to the aqueous medium cooling / heating units 75a and 75b is heated in the heat exchange panels 76a and 76b, thereby cooling the indoor walls and the like and cooling the indoor floor.
In the aqueous medium circuits 170a and 170b, the aqueous medium circulating through the aqueous medium circuits 170a and 170b is heated by the heat radiation of the heat source side refrigerant in the refrigerant-water heat exchangers 57a and 57b. The aqueous medium heated in the refrigerant-water heat exchangers 57a and 57b is stored in the hot water storage tank by the first circulation pumps 71a and 71b through the first usage side water outlet pipes 74a and 74b and the hot water storage tank side water inlet pipes 176a and 176b. 161a and 161b. The heat exchange coils 162a and 162b exchange heat with the aqueous medium in the hot water storage tanks 161a and 161b to dissipate heat to heat the aqueous medium in the hot water storage tanks 161a and 161b.
In this way, an operation in which the cooling operation and the heating operation (and / or the hot water supply operation) are mixed in a state where at least one of the use units 105a and 105b is set to the cooling hot water supply operation in which the cooling operation and the hot water supply operation are performed simultaneously. The operation in the simultaneous cooling and heating operation mode (mainly heat dissipation) is performed.

-Cooling operation mode-
In the case where only the cooling operation of the use units 105a and 105b is performed, in the heat source side refrigerant circuit 120, the first and second heat source side switching mechanisms 23a and 23b are in the heat source side heat radiation operation state (the first and second heat sources in FIG. 5). The state is switched to the state shown by the solid lines of the side switching mechanisms 23a and 23b. The third heat source side switching mechanism 39 is switched to the cooling / heating simultaneous operation state (the state indicated by the solid line of the third heat source side switching mechanism 39 in FIG. 5). Further, the first use side expansion valves 52a and 52b are closed, and the use side heat exchange outlet on / off valves 154a and 154b are opened. Furthermore, the cold / hot water switching mechanisms 175a, 175b are switched to a state in which the aqueous medium cooled in the second usage-side heat exchangers 151a, 151b is supplied to the aqueous medium cooling / heating units 75a, 75b. Here, description will be made assuming that all of the usage units 105a and 105b are set in the cooling operation.

  In the heat source side refrigerant circuit 120 in such a state, the low pressure heat source side refrigerant in the refrigeration cycle is sucked into the heat source side compressor 21 through the heat source side suction pipe 21c and compressed to a high pressure in the refrigeration cycle, and then the heat source side refrigerant circuit 120 is heated. It is discharged to the discharge pipe 21b. The high pressure heat source side refrigerant discharged to the heat source side discharge pipe 21b is separated from the refrigerating machine oil in the oil separator 22a. The refrigerating machine oil separated from the heat source side refrigerant in the oil separator 22a is returned to the heat source side suction pipe 21c through the oil return pipe 22b. The high-pressure heat-source-side refrigerant from which the refrigeration oil is separated is sent to the heat-source-side heat exchangers 26a and 26b through the heat-source-side switching mechanisms 23a and 23b and the heat-source-side gas refrigerant tubes 24a and 24b. The high-pressure heat-source-side refrigerant sent to the heat-source-side heat exchangers 26a and 26b radiates heat by exchanging heat with outdoor air supplied by the heat-source-side fans 36a and 36b in the heat source-side heat exchangers 26a and 26b. The high-pressure heat-source-side refrigerant radiated in the heat-source-side heat exchangers 26a and 26b is sent to the subcoolers 31a and 31b through the heat-source-side expansion valves 28a and 28b. The heat-source-side refrigerant sent to the subcoolers 31a and 31b exchanges heat with the heat-source-side refrigerant branched from the heat-source-side liquid refrigerant tubes 27a and 27b to the suction return tubes 29a and 29b so as to be in a supercooled state. To be cooled. The heat source side refrigerant flowing through the suction return pipes 29a and 29b is returned to the heat source side suction pipe 21c. The heat source side refrigerant cooled in the subcoolers 31a and 31b is sent from the heat source unit 102 to the liquid refrigerant communication tube 13 through the heat source side liquid refrigerant tubes 27a and 27b, the heat source side liquid refrigerant junction tube 27 and the liquid side shut-off valve 33. It is done.

The high-pressure heat source side refrigerant sent to the liquid refrigerant communication tube 13 is branched into two and sent to the use units 105a and 105b.
The high-pressure heat-source-side refrigerant sent to the usage units 105a and 105b is sent to the second usage-side expansion valves 152a and 152b. The high-pressure heat-source-side refrigerant sent to the second usage-side expansion valves 152a and 152b is depressurized by the second usage-side expansion valves 152a and 152b to be in a low-pressure gas-liquid two-phase state, and the usage-side heat exchange inlet / outlet connection It sends to the 2nd utilization side heat exchanger 151a, 151b through the pipe | tube 53a, 53b. The low-pressure heat-source-side refrigerant sent to the second usage-side heat exchangers 151a and 151b circulates in the aqueous medium circuits 170a and 170b by the second circulation pumps 171a and 171b in the second usage-side heat exchangers 151a and 151b. Evaporates by exchanging heat with the aqueous medium. The low-pressure heat-source-side refrigerant evaporated in the second usage-side heat exchangers 151a and 151b is sucked from the usage units 105a and 105b through the usage-side heat exchange outlet on / off valves 154a and 154b and the second usage-side gas refrigerant tubes 153a and 153b. It is sent to the refrigerant communication pipe 14 and merges.

The low-pressure heat source side refrigerant sent to the suction refrigerant communication tube 14 is sent to the heat source unit 102. The low-pressure heat source side refrigerant sent to the heat source unit 102 is again sucked into the heat source side compressor 21 through the suction side closing valve 34, the heat source side gas refrigerant tube 25, and the heat source side suction tube 21c.
On the other hand, in the aqueous medium circuits 170a and 170b, the aqueous medium circulating through the aqueous medium circuits 170a and 170b is cooled by evaporation of the heat source side refrigerant in the second usage-side heat exchangers 151a and 151b. The aqueous medium cooled in the second usage-side heat exchangers 151a and 151b is passed through the second usage-side water outlet pipes 174a and 174b and the first usage-side water outlet pipes 74a and 74b by the second circulation pumps 171a and 171b. It is sent from the use units 105a and 105b to the aqueous medium communication pipes 16a and 16b. The aqueous medium sent to the aqueous medium communication pipes 16a and 16b is sent to the aqueous medium cooling / heating units 75a and 75b. The aqueous medium sent to the aqueous medium cooling / heating units 75a and 75b is heated in the heat exchange panels 76a and 76b, thereby cooling the indoor walls and the like and cooling the indoor floor.

In this manner, the operation in the cooling only operation mode in which only the cooling operation of the use units 105a and 105b is performed is performed.
-Condensation temperature control of each refrigerant circuit-
As described above, in the heat pump system 101, similarly to the heat pump system 1 of the first embodiment, the control unit 101a has the heat source side condensation temperature Tc1 corresponding to the saturation temperature of the heat source side refrigerant in the discharge of the heat source side compressor 21. The operating capacity of the heat source side compressor 21 is controlled so as to reach a predetermined target heat source side condensation temperature Tc1s. Moreover, the control unit 101a controls the operation capacity of the heat source side compressor 21 and uses the use side condensation temperature Tc2 corresponding to the saturation temperature of the use side refrigerant in the discharge of the use side compressors 50a and 50b. The operation capacities of the use side compressors 55a and 55b are controlled so as to be the side condensation temperature Tc2s. Thereby, in the heat pump system 101, both the refrigeration cycle in the heat source side refrigerant circuit 120 and the refrigeration cycle in the use side refrigerant circuits 50a and 50b are stabilized.

<Heat source unit power consumption apportioning system>
Since the heat pump system 101 is installed in an apartment house, a building, or the like, the users who use the usage units 510a and 105b may not be the same. In this case, it is necessary to share the power consumption Wr of the heat source unit 102 provided in common with the use units 105a and 105b among the users. However, since the capacity, usage frequency, or set temperature of the utilization units 105a and 105b differs depending on the user, a dedicated heat source unit power consumption apportioning system is necessary for each user to share the power consumption of the heat source unit 102 fairly. It becomes.
Therefore, here, the following heat source unit power consumption apportioning system 110 is applied to the heat pump system 101.

-Overall-
FIG. 6 is a system configuration diagram of the heat source unit power consumption apportioning system 110. The heat source unit power consumption apportioning system 110 mainly includes a heat source unit wattmeter 17, first heat quantity water medium sensors 80 a and 80 b, second heat quantity water medium sensors 90 a and 90 b, a controller 101 a, and an interface device 18. And an arithmetic unit 119.
The heat source unit wattmeter 17 is a device that detects the power consumption Wr of the heat source unit 102, and can transmit the detected power consumption Wr to the arithmetic device 119.
The first heat quantity measurement aqueous medium sensors 80a and 80b use the usage units 105a and 105b and the aqueous medium cooling and heating unit 75a, in order to calculate the usage-side usage heat quantity in the cooling operation (cooling operation) or the heating operation (heating operation) described later. This is a sensor unit that detects the flow rate and temperature of the aqueous medium exchanged with 75b. The configuration of the first heat quantity measurement aqueous medium sensor 80b is the same as the structure of the first heat quantity measurement aqueous medium sensor 80a. Therefore, here, only the configuration of the first heat quantity measurement aqueous medium sensor 80a will be described, and the structure of the first heat quantity measurement aqueous medium sensor 80b will be denoted by the suffix “ Subscript “b” is attached instead of “a”, and description of each part is omitted. As shown in FIG. 3, the first heat quantity measurement aqueous medium sensor 80a mainly includes a first heat quantity measurement inlet temperature sensor 81a, a first heat quantity measurement outlet temperature sensor 82a, and a first heat quantity measurement flow rate sensor 83a. have. The first heat quantity measuring inlet temperature sensor 81a is a temperature sensor that detects the first heat quantity measuring inlet temperature Twi1a that is the temperature of the aqueous medium flowing through the aqueous medium connecting pipe 16a. The first heat quantity measurement outlet temperature sensor 82a is a temperature sensor that detects the first heat quantity measurement outlet temperature Two1a that is the temperature of the aqueous medium flowing through the aqueous medium communication pipe 15a. The first heat quantity measurement flow rate sensor 83a is a flow rate sensor that detects a first heat quantity measurement flow rate Gw1a that is a flow rate of the aqueous medium flowing through the aqueous medium communication pipe 15a. Further, the first heat quantity measurement aqueous medium sensor 80a can transmit the detected flow rate Gw1a of the aqueous medium and the temperatures Twi1a and Two1a to the arithmetic device 119.

  The second heat quantity measurement aqueous medium sensors 90a and 90b are used between the refrigerant-water heat exchangers 57a and 57b and the hot water storage tanks 161a and 161b in order to calculate the use side heat consumption in the hot water supply operation (heating operation) described later. It is a sensor unit that detects the flow rate and temperature of the aqueous medium to be exchanged. The configuration of the second heat quantity measurement aqueous medium sensor 80b is the same as the structure of the second heat quantity measurement aqueous medium sensor 90a. Therefore, here, only the configuration of the second heat quantity measurement aqueous medium sensor 90a will be described, and the structure of the second heat quantity measurement aqueous medium sensor 90b will be described with reference numerals indicating the respective parts of the second heat quantity measurement aqueous medium sensor 90a. Subscript “b” is attached instead of “a”, and description of each part is omitted. As shown in FIG. 3, the second heat quantity measurement aqueous medium sensor 90a mainly includes a second heat quantity measurement inlet temperature sensor 91a, a second heat quantity measurement outlet temperature sensor 92a, and a second heat quantity measurement flow rate sensor 93a. have. The second heat quantity measurement inlet temperature sensor 91a is a temperature sensor that detects a heat quantity measurement inlet temperature Twi2a that is the temperature of the aqueous medium flowing through the hot water storage tank side water inlet pipe 176a. The second heat quantity measurement outlet temperature sensor 92a is a temperature sensor that detects a second heat quantity measurement outlet temperature Two2a that is the temperature of the aqueous medium flowing through the hot water storage tank side water outlet pipe 178a. The second heat quantity measurement flow rate sensor 93a is a flow rate sensor that detects a second heat quantity measurement flow rate Gw2a that is a flow rate of the aqueous medium flowing through the hot water storage tank side water outlet pipe 178a. Further, the second heat quantity measurement aqueous medium sensor 90a can transmit the detected flow rate Gw2a of the aqueous medium and the temperatures Twi2a and Two2a to the computing device 119.

As described above, the control unit 101a includes the heat source side control unit 49 and the use side control units 69a and 69b, and the operation data and equipment of the heat pump system 101 (here, the heat source unit 102 and the use units 105a and 105b). Information or the like can be transmitted to the arithmetic device 119.
The interface device 18 transmits operation data, device information, and the like from the heat source unit wattmeter 17, the first heat quantity measurement aqueous medium sensors 80a and 80b, the second heat quantity measurement aqueous medium sensors 90a and 90b, and the control unit 1a to the arithmetic unit 19. Therefore, the heat source unit wattmeter 17, the first heat quantity measurement aqueous medium sensors 80 a and 80 b, the second heat quantity measurement aqueous medium sensors 90 a and 90 b, and the control unit 101 a are interposed between the arithmetic device 119.
The arithmetic unit 119 receives operation data, device information, and the like from the heat source unit wattmeter 17, the first calorific measurement aqueous medium sensors 80a and 80b, the second calorific measurement aqueous medium sensors 90a and 90b, and the control unit 101a, and consumes them. It is a computer which performs the process which apportions electric power Wr to each user. The computing device 119 includes a use heat amount calculation unit 119a, a correction heat amount calculation unit 119b, and a power apportioning unit 119c.

-Use calorific value calculation unit, correction calorific value calculation unit-
The used heat amount calculation unit 119a performs cooling operation (cooling operation) or cooling operation (cooling operation) in each usage unit 5a, 5b from the flow rate Gw1a, Gw1b, Gw2a, Gw2b of the aqueous medium and the temperature Twi1a, Two1a, Twi1b, Two1b, Two2a, Two2a, Two2b, Two2b. The usage-side use heat amount, which is the use heat amount in the heating operation and / or hot water supply operation (heating operation), is calculated. The corrected calorific value calculation unit 119b is based on the refrigeration cycle characteristics of the respective use-side refrigerant circuits 50a and 50b that are assumed from the heat-source-side condensation temperature Tc1 or the use-side evaporation temperatures Tpl2a and Tpl2b and the aqueous medium outlet temperatures Twl1a and Twl1b. The usage-side usage heat quantity qh of the heating operation and / or the hot water supply operation in each usage unit 5a, 5b is corrected. Further, the corrected calorific value calculation unit 119b sets the expected performance value when it is assumed that each usage unit 105a, 105b performs only the cooling operation or the heating operation (and / or the hot water supply operation) with respect to the usage-side usage heat amount. Based on the correction. In addition, when the use unit 105a, 105b is performing the cooling hot water supply operation, the corrected heat amount calculation unit 119b performs the correction based on the expected performance value, and then uses the use side heat amount and the hot water supply operation of the cooling operation. Compared with the side use heat amount, the larger one is used as the use side use heat amount of the use unit.

Such use heat amount calculation unit 119a and correction heat amount calculation unit 119b calculate use side use heat amount and correct it as follows.
First, the used heat amount calculation unit 119a receives the heat pump system 101 operation data and device information transmitted from the heat amount measurement aqueous medium sensors 80a, 80b, 90a, 90b and the control unit 101a to the calculation device 119 via the interface device 18. obtain.
Next, the used heat amount calculation unit 119a includes the heat medium measuring water medium sensors 80a, 80b, 90a, and 90b. Using the data of Two2b, the use side usage heat quantity qc of the use unit performing the cooling operation or the cooling hot water supply operation and the use side use heat quantity qh of the use unit performing the heating operation (and / or the hot water supply operation) are calculated. Calculate. Note that whether each use unit is performing a cooling operation, a heating operation (and / or a hot water supply operation), or a cooling hot water supply operation is, for example, the first use side expansion valves 52a and 52b, the second use side expansion valve 152a, 152b, heating / hot water switching mechanism 177a, heating / hot water switching mechanism 177a, such as the open / closed state of the heating / hot water switching mechanism 177a.

The usage-side usage heat quantity qc of the usage unit performing the cooling operation or the cooling hot water supply operation is the flow rate Gw1a, Gw1b (heat amount measurement flow rate) and temperature Twi1a of the aqueous medium detected by the first heat quantity measurement aqueous medium sensors 80a, 80b. , Two1a, Two1b, Two1b. That is, the usage-side usage heat quantity qc can be calculated according to the following equation.
qc = Gw1 × (Two1-Twi1)
Here, Gw1 is the flow rate of the aqueous medium (heat quantity measurement flow rate) that passes through the aqueous medium heating units 75a and 75b during the cooling operation or the cooling hot water supply operation. Twi1 is the temperature of the aqueous medium (heat medium measuring aqueous medium inlet temperature) supplied to the aqueous medium heating units 75a and 75b during the cooling operation or the cooling hot water supply operation. Two1 is the temperature of the aqueous medium returned to the use units 5a and 5b from the aqueous medium heating units 75a and 75b during the cooling operation or cooling hot water supply operation (heat medium measurement aqueous medium outlet temperature).

Next, the usage side usage heat quantity qh of the usage unit performing the heating operation (and / or the hot water supply operation) is the flow rate Gw1a, Gw1b of the aqueous medium detected by the aqueous medium sensors 80a, 80b, 90a, 90b for heat quantity measurement. It is calculated based on Gw2a, Gw2b (flow rate for calorimetric measurement) and temperatures Twi1a, Two1a, Twi1b, Two1b, Twi2a, Two2a, Twi2b, Two2b. That is, the use side use heat quantity qh can be calculated according to the following equation.
qh = Gw1 * (Twi1-Two1) + Gw2 * (Twi2-Two2)
Here, Gw1 is a flow rate of the aqueous medium that passes through the aqueous medium heating units 75a and 75b during the heating operation (flow rate for calorific value measurement). Twi1 is the temperature of the aqueous medium supplied to the aqueous medium heating units 75a and 75b during the heating operation (the aqueous medium inlet temperature for calorimetric measurement). Two1 is the temperature of the aqueous medium (heat medium measurement aqueous medium outlet temperature) returned from the aqueous medium heating units 75a and 75b to the utilization units 5a and 5b during the heating operation. Gw2 is the flow rate of the aqueous medium that passes through the hot water storage tanks 161a and 161b during the hot water supply operation (the amount of heat measurement flow rate). Twi2 is the temperature of the aqueous medium supplied to the hot water storage tanks 161a and 161b during the hot water supply operation (heat medium measuring aqueous medium inlet temperature). Two2 is the temperature of the aqueous medium returned to the refrigerant-water heat exchangers 57a and 57b from the hot water storage tanks 161a and 161b during the hot water supply operation (heat medium measurement aqueous medium outlet temperature).

Next, the corrected heat amount calculation unit 119b multiplies the calculated use side use heat amount qh by the correction coefficients kpl and kwl to obtain the corrected use side use heat amount qh ''.
That is, for the use side usage heat quantity qh in the heating operation (and / or hot water supply operation), the corrected use side use heat quantity qh '' is calculated by the following equation. The use side use heat quantity qh '' obtained by this correction corresponds to the exchange heat quantity between the heat source side refrigerant and the use side refrigerant in the first use side heat exchangers 51a and 51b.
qh ″ = qh × kpl × kwl
The correction coefficients kpl and kwl are values obtained based on the refrigeration cycle characteristics of the respective use-side refrigerant circuits 50a and 50b that are assumed from the heat-source-side condensation temperature Tc1 or the use-side evaporation temperature Tpl2 and the aqueous medium outlet temperature Twl.

  Here, considering the refrigeration cycle characteristics of the usage-side refrigerant circuits 50a and 50b, first, as shown in FIG. 4, the aqueous medium outlet temperature Twl remains constant while the low pressure in the refrigeration cycle of the usage-side refrigerant circuits 50a and 50b remains constant. When it becomes higher, the high pressure in the refrigeration cycle of the use-side refrigerant circuits 50a and 50b tends to increase. When the high pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b increases, the amount of heat exchanged between the heat source side refrigerant and the use side refrigerant in the first use side heat exchangers 51a and 51b decreases, and the use side compressor 55a, The power consumption of 55b tends to increase. In contrast, when the high pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b remains constant and the heat source side condensation temperature Tc1 or the use side evaporation temperature Tpl2 decreases, the low pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b decreases. It tends to be lower. When the low pressure in the refrigeration cycle of the use side refrigerant circuits 50a, 50b is reduced, the amount of heat exchanged between the heat source side refrigerant and the use side refrigerant in the first use side heat exchangers 51a, 51b is reduced, and the use side compressor 55a, The power consumption of 55b tends to increase. As described above, the use side refrigerant circuits 50a and 50b have the first use side heat exchanger 51a as the aqueous medium outlet temperature Twl, which is a state quantity corresponding to the high pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b, increases. , 51b has a refrigeration cycle characteristic in which the amount of exchange heat between the heat source side refrigerant and the use side refrigerant is small. Further, the use side refrigerant circuits 50a and 50b are configured so that the heat source side condensation temperature Tc1 or the use side evaporation temperature Tpl2, which is a state quantity corresponding to the low pressure in the refrigeration cycle of the use side refrigerant circuits 50a and 50b, decreases as the first use side. The heat exchangers 51a and 51b have refrigeration cycle characteristics in which the amount of heat exchanged between the heat source side refrigerant and the use side refrigerant is reduced.

  Therefore, here, a characteristic is used in which the amount of heat exchanged between the heat source side refrigerant and the use side refrigerant in the first use side heat exchangers 51a and 51b decreases as the heat source side condensation temperature Tc1 or the use side evaporation temperature Tpl2 decreases. Thus, the first correction coefficient kpl is prepared as a function that decreases as the heat source side condensation temperature Tc1 or the use side evaporation temperature Tpl2 decreases. Further, the aqueous medium outlet temperature Twl is increased by using the characteristic that the amount of heat exchanged between the heat source side refrigerant and the utilization side refrigerant in the first usage-side heat exchangers 51a and 51b decreases as the aqueous medium outlet temperature Twl increases. The second correction coefficient kwl is prepared as a function that decreases as the time increases. The correction coefficients are not limited to the two correction coefficients kpl and kwl described above, but are assumed from the heat source side condensation temperature Tc1 or the use side evaporation temperatures Tpl2a and Tpl2b and the aqueous medium outlet temperatures Twla and Twlb. Any correction coefficient may be used as long as it is obtained based on the refrigeration cycle characteristics of the use-side refrigerant circuits 50a and 50b.

Next, the corrected calorific value calculation unit 119b multiplies the calculated usage side usage calorie qc, qh ″ by the correction coefficients kc, kh to obtain the corrected usage side usage calorie qc ′, qh ′. obtain.
That is, for the usage side usage heat quantity qc of the cooling operation or the cooling hot water supply operation, the corrected usage side usage heat quantity qc ′ is calculated by the following equation.
qc ′ = qc × kc
Further, for the use side use heat quantity qh in the heating operation (and / or hot water supply operation) or the cooling hot water supply operation, the corrected use side use heat quantity qh ′ is calculated by the following equation.
qh ′ = qh ″ × kh
Here, the correction coefficients kc and kh are values obtained based on expected performance values when it is assumed that each of the usage units 5a and 5b has performed only the cooling operation or the heating operation (and / or the hot water supply operation). . Here, the expected value of the coefficient of performance (COP) of the heat pump system 101 is used as the expected performance value (see FIG. 7). The term “expected value” is used in consideration of a coefficient of performance that cannot be obtained in an operating state in which the cooling operation and the heating operation are performed simultaneously. Moreover, since the expected value of the coefficient of performance is influenced by the outside air temperature Ta, it is prepared as a function or map as a value that changes according to the outside air temperature Ta.

The cooling correction coefficient kc is expressed as the reciprocal (1 / COPc) of the coefficient of performance COPc when it is assumed that only the cooling operation is performed. The heating correction coefficient kh is expressed as an inverse number (1 / COPh) of the coefficient of performance COPh when it is assumed that only the heating operation is performed.
Then, the corrected usage-side usage heat amounts qc ′ and qh ′ obtained by the above correction are used as the usage-side usage heat amounts Qa and Qb of the usage units 105a and 105b.
However, when the cooling hot water supply operation is performed in each of the usage units 105a and 105b, an effect of exhaust heat recovery occurs in each of the usage units 105a and 105b. For this reason, if the usage side usage heat quantity qc ′ of the cooling operation in the same usage unit and the usage side usage heat quantity qh ′ of the hot water supply operation are simply added, the effect of exhaust heat recovery in the same usage unit is considered. Will not be.

Therefore, here, for the use unit performing the cooling hot water supply operation, the use side use heat amount qc ′ of the cooling operation and the use side use heat amount qh ′ of the hot water operation are compared, and the larger one is used on the use side. The amount of heat is set to Qa and Qb.
-Power apportioning section-
The power apportioning unit 119c sets the power consumption Wr of the heat source unit 102 to each user according to the corrected usage-side usage heat amounts Qa and Qb (here, the users of the usage units 105a and 105b are users A and B). Apportion.
The process of apportioning the power consumption Wr of the heat source unit 102 in the electric power apportioning unit 119c is performed as follows.
First, the power apportioning unit 119c obtains the data of the power consumption Wr of the heat source unit 102 transmitted from the heat source unit wattmeter 17 to the arithmetic device 119 via the interface device 18.

Next, the power apportioning unit 119c uses the usage-side usage heat amounts Qa and Qb after the correction of the usage units 105a and 105b obtained by the usage heat amount calculation unit 119a and the correction heat amount calculation unit 119b. , 105b, the power consumption Wr of the heat source unit 102 is apportioned to the users A and B. For example, the apportioned power Wra of the power consumption Wr of the heat source unit 102 for the user A is expressed by the following equation.
Wra = Wr × Qa / Σ (Qa, Qb)
Here, Σ (Qa, Qb) means an integrated value of the use side usage heat amounts Qa, Qb after correction (that is, here, Qa + Qb is meant). Further, the apportioned power Wrb of the power consumption Wr of the heat source unit 102 for the user B can be calculated in the same manner as the apportioned power Wra.

-Specific example-
A specific example in which the above-described heat source unit power consumption apportioning system 110 is used to apportion the power consumption Wr of the heat source unit 102 to the users A and B who use the utilization units 105a and 105b will be described. In addition, since the correction | amendment by the correction coefficients klp and kwl of the utilization side use calorie | heat amount qh of the utilization unit which is performing heating operation and / or hot-water supply operation (heating operation) is the same as that of 1st Embodiment, it demonstrates. Omitted. And about the use side use heat amount of heating operation (and / or hot water supply operation), the use side use heat amount qh '' after correction by the correction coefficients klp and kwl shall be given, and the correction coefficients kc and kh The explanation will be focused on the correction by.
First, the case where all the use units 105a and 105b are performing the cooling operation (cooling operation) will be described. Here, it is assumed that the user A has performed the cooling operation with the use side use heat quantity qca = 3.0, and the user B has performed the cooling operation with the use side use heat quantity qcb = 3.0, and at the outside air temperature Ta during this operation. It is assumed that the expected value of the performance coefficient COPc is 3.75 (that is, the cooling correction coefficient kc = 1 / 3.75). Here, for convenience of explanation, the usage-side used heat quantities qca and qcb are represented by dimensionless numbers. In this case, the user-side use heat amount Qa (qca ′) after correction of the user A becomes 0.8, and the user-side use heat amount Qb (qcb ′) after the correction of the user B becomes 0.8. Therefore, the apportioned power Wra and Wrb of the power consumption Wr of the heat source unit 102 for the users A and B are 0.5 Wr and 0.5 Wr, respectively. In this case, even if the power consumption Wr of the heat source unit 102 is apportioned without correcting the usage-side usage heat quantities qca and qcb, the apportioned power of the power consumption Wr of the heat source unit 102 for each user A and B is apportioned. Wra and Wrb are 0.5 Wr and 0.5 Wr, respectively.

  Next, the case where all the usage units 105a and 105b are performing the heating operation (and / or the hot water supply operation) will be described. Here, the user A is in the heating operation (and / or hot water supply operation) with the use side use heat quantity qha ″ = 3.0, and the user B is in the heating operation (and / or with the use side use heat quantity qhb ″ = 3.0). (Or hot water supply operation), and the expected value of the coefficient of performance COPh at the outside air temperature Ta during this operation is 5.0 (that is, the heating correction coefficient kh = 1 / 5.0). Here, for convenience of explanation, the usage-side used heat quantities qha ″ and qhb ″ are represented by dimensionless numbers. In this case, the usage-side usage heat amount Qa (qha ′) after correction by the user A is 0.6, and the usage-side usage heat amount Qb (qcb ′) after correction by the user B is 0.6. Therefore, the apportioned power Wra and Wrb of the power consumption Wr of the heat source unit 102 for the users A and B are 0.5 Wr and 0.5 Wr, respectively. In this case, even if the power consumption Wr of the heat source unit 102 is apportioned without correcting the usage-side usage heat quantities qha and qhb, the apportioned electric power of the power consumption Wr of the heat source unit 102 for each user A and B is allocated. Wra and Wrb are 0.5 Wr and 0.5 Wr, respectively.

  Next, the case where the cooling operation and the heating operation are performed at the same time (the case where the cooling operation and the heating operation and / or the hot water supply operation are performed in a mixed manner between the use units) will be described. Here, first, the user A performs the heating operation (and / or hot water supply operation) with the use side use heat amount qha ″ = 6.0, and the user B performs the cooling operation with the use side use heat amount qcb = 3.0. Shall. Here, for convenience of explanation, the usage-side used heat quantities qha ″ and qcb are represented by dimensionless numbers. In this case, it is assumed that the user A (that is, the utilization unit 5a) has performed only the heating operation (and / or the hot water supply operation) alone, and the expected value of the coefficient of performance COPh at the outside air temperature Ta during this operation is If it is 5.0 (that is, the heating correction coefficient kh = 1 / 5.0), the use side use heat amount Qa (qha ′) after the correction of the user A becomes 1.2. Further, assuming that the user B (that is, the use unit 5b) has performed only the cooling operation alone, the expected value of the coefficient of performance COPc at the outside air temperature Ta during this operation is 3.75 (that is, the cooling correction coefficient kc). = 1 / 3.75), the use side use heat amount Qb (qcb ′) after correction of the user B becomes 0.8. For this reason, the apportioned power Wra and Wrb of the power consumption Wr of the heat source unit 102 for the users A and B are 0.6 Wr and 0.4 Wr, respectively. In this case, if the power consumption Wr of the heat source unit 102 is apportioned without correcting the usage-side usage heat quantities qha and qcb, the apportionment of the power consumption Wr of the heat source unit 102 to the users A and B is apportioned. The electric power Wra and Wrb are 0.67 Wr and 0.33, respectively.

  Next, the case where the cooling operation and the heating operation are performed at the same time (when the cooling operation and the hot water supply operation are performed together in the same use unit) will be described. It is assumed that the user A has performed the cooling hot water supply operation with the use side use heat quantity qha ″ = 6.0 and the use side use heat quantity qca = 3.0, and the user B has performed the cooling operation with the use side use heat quantity qcb = 3.0. (See FIG. 8). Here, for convenience of explanation, the usage-side used heat quantities qha ″, qca, and qcb are represented by dimensionless numbers. In this case, as shown in FIG. 9, it is assumed that the user A (that is, the utilization unit 5a) has performed only the hot water supply operation, and the expected value of the coefficient of performance COPh at the outside air temperature Ta during this operation is If it is 5.0 (that is, the heating correction coefficient kh = 1 / 5.0), the use side use heat quantity qha ′ of the hot water supply operation after correction by the user A becomes 1.2. Further, as shown in FIG. 10, it is assumed that each user A, B (that is, the use units 5a, 5b) has performed only the cooling operation, and the expectation of the coefficient of performance COPc at the outside air temperature Ta during this operation is expected. Assuming that the value is 3.75 (that is, the cooling correction coefficient ka = 1 / 3.75), the use side use heat quantity qca ′ after correction of the cooling operation of the user A becomes 0.8, and the user B's The use side use heat quantity Qb (qcb ′) after correction of the cooling operation becomes 0.8. Then, the use side use heat quantity qca ′ (= 0.8) of the cooling operation of the user A and the use side use heat quantity qha ′ (= 1.2) of the hot water supply operation are compared, and the larger use side use heat quantity qha. Let 'be the usage-side heat consumption Qa of user A. For this reason, the apportioned power Wra and Wrb of the power consumption Wr of the heat source unit 102 for the users A and B are 0.6 Wr and 0.4 Wr, respectively. In this case, if the power consumption Wr of the heat source unit 102 is apportioned without correcting the usage-side usage heat quantities qha ″, qca, and qcb, the consumption of the heat source unit 102 for each user A and B is assumed. The apportioned powers Wra and Wrb of the power Wr are 0.71 Wr and 0.29 Wr, respectively.

Thus, when all the usage units 105a and 105b are performing the cooling operation, or when all the usage units 105a and 105b are performing the heating operation (and / or the hot water supply operation), Regardless of the presence or absence of correction, the apportioned power for the users A and B is the same. On the other hand, when the cooling operation and the heating operation (and / or the hot water supply operation) are performed at the same time, depending on whether or not the use side use heat amount is corrected and whether or not the exhaust heat recovery in the same use unit is considered, The apportioned power for users A and B is different.
This is because the operation performance of the heat pump system 101 under the condition where the cooling operation and the heating operation (and / or hot water supply operation) are performed simultaneously, the condition where only the cooling operation is performed, and the heating operation (and / or hot water supply). This means that the operation performance of the heat pump system 101 may be different under the condition where only (operation) is performed. It also shows the need to consider exhaust heat recovery.

In the above case, when the user A (that is, the use unit 105a) performing the heating operation (and / or the hot water supply operation) performs the cooling operation simultaneously, only the user A alone performs the heating operation (and (/ Or hot water supply operation) means that the operation is performed under conditions with poor operation performance. That is, the user A receives a disadvantage because the cooling operation and the heating operation (and / or the hot water supply operation) are performed at the same time, and the user B receives the cooling operation and the heating operation (and / or the hot water supply operation). And benefit from being done at the same time. In addition, user A is disadvantaged by not considering exhaust heat recovery in the same use unit, and user B is benefited by not considering exhaust heat recovery in the same use unit. Become.
For this reason, unless correction of the usage-side usage heat amount or exhaust heat recovery in the same usage unit is taken into account, the user A distributes the electric power without correction (0.67 Wr in the former case, the latter case) Is 0.71 Wr) and the power difference (0.6 Wr in the former case is 0.07 Wr in the former case and 0.11 Wr in the latter case) when the correction is performed, the driving performance is poor. There is a disadvantage that the operation is performed under conditions and the exhaust heat recovery in the same use unit is not considered. On the other hand, the user B has an apportioned power (0.33 Wr for the former and 0.29 Wr for the latter) without correction and an apportioned power (0.4 Wr) with correction. The profit based on the disadvantage of the user A is received by the difference (0.07 Wr in the former case and 0.11 Wr in the latter case).
On the other hand, this disadvantage is prevented from being added to the user A by correcting the usage-side heat consumption and the exhaust heat recovery in the same usage unit, and the user B is not improperly benefited. I am doing so.

<Features>
The heat source unit power consumption apportioning system 110 has the following characteristics.
-A-
The heat source unit power consumption apportioning system 110 can obtain the same effects as the heat source unit power apportioning system 10 of the first embodiment (see <Features> of the heat source unit power apportioning system 10 of the first embodiment). .
-B-
Like the heat pump system 101, the use units 105a and 105b having the second usage-side heat exchangers 151a and 151b are capable of simultaneously operating the cooling operation (cooling operation), the heating operation and / or the hot water supply operation (heating operation). When employed, it is necessary to consider the usage-side usage heat amount in the cooling operation of the usage units 105a and 105b and the usage-side usage heat amount in the heating operation (and / or hot water supply operation).

However, when the use units 105a and 105b are in an operation state in which the cooling operation and the heating operation (and / or hot water supply operation) are performed simultaneously, the use unit performing the cooling operation and the heating operation (and / or hot water supply operation) are performed. The effect of exhaust heat recovery occurs between the used units. For this reason, it is necessary for the heat source unit power consumption apportioning system 110 to consider the influence of such exhaust heat recovery. Otherwise, it is difficult to appropriately apportion the power consumption Wr of the heat source unit 102. It is.
Therefore, in the heat source unit power consumption apportioning system 110 according to the present modification, the heat source side condensation temperature or the use side evaporation temperature is used for the use side use heat amount in the heating operation (and / or hot water supply operation) calculated from the flow rate and temperature of the aqueous medium. Based on the refrigeration cycle characteristics of the respective use-side refrigerant circuits 50a and 50b that are assumed from the temperature of the water medium and the outlet of the aqueous medium, the use-side usage heat amount in the heating operation (and / or hot water supply operation) is corrected. Thereby, the influence of the calorie | heat amount which bears in use side refrigerant circuit 50a, 50b can be considered. Then, based on the expected performance value (here, coefficient of performance) when it is assumed that only the cooling operation or the heating operation (and / or the hot water supply operation) is performed, the usage-side heat consumption is corrected. Thereby, about the use side use heat amount of heating operation (and / or hot water supply operation), the influence at the time of cooling operation can be considered, and about the use side use heat amount of cooling operation, The influence when the heating operation (and / or the hot water supply operation) is performed simultaneously can be considered. Then, the use side use heat amount in the cooling operation and the use side use heat amount in the heating operation (and / or hot water supply operation) are compared, and the larger one is set as the use side use heat amount. For this reason, the utilization side use heat amount in utilization unit 105a, 105b can be obtained as a value which considered the effect of exhaust heat recovery.

As a result, in the heat source unit power consumption apportioning system 110 according to the present modified example, the use unit 105a capable of simultaneously operating the cooling operation and the heating operation (and / or the hot water supply operation) by including the second use side heat exchangers 151a and 151b. , 105b, the power consumption Wr of the heat source unit 102 can be apportioned in consideration of the effect of exhaust heat recovery in the use units 105a, 105b.
<Modification>
In the heat pump system 101 described above, the correction heat amount calculation unit 119b corrects the correction coefficient kc for the use side use heat amount qc '' for the cooling operation (cooling operation) and the use side use heat amount qh '' for the heating operation (heating operation), respectively. , Kh are used to obtain corrected usage-side usage heat quantities qc ′ and qh ′.

However, since the correction of the usage-side usage heat amount is intended to apportion the power consumption Wr of the heat source unit, both the usage-side usage heat amount qc and the usage-side usage heat amount qh ″ are necessarily corrected. do not have to.
For example, a value obtained by dividing the heating correction coefficient kh by the cooling correction coefficient kc may be multiplied by the use side use heat quantity qh ″ as the cooling / heating correction coefficient khc. Further, a value obtained by dividing the cooling correction coefficient kc by the heating correction coefficient kh may be multiplied by the use side use heat quantity qc as the cooling / heating correction coefficient kch. Even in this case, it is possible to obtain an apportioned result of the power consumption Wr of the heat source unit similar to the case where both the use side use heat amount qc and the use side use heat amount qh ″ are corrected.

(3) Other Embodiments The embodiments of the present invention and the modifications thereof have been described above with reference to the drawings. However, the specific configuration is not limited to these embodiments and the modifications thereof. Changes can be made without departing from the scope of the invention.
-A-
In the heat source unit power consumption apportioning systems 10 and 110 described above, standby power Ws of the heat source units 2 and 102 (power consumption when all the utilization units are not operating) is not considered. However, when the standby power Ws of the heat source units 2 and 102 is considered in detail, the standby power Ws detected by the heat source unit wattmeter 17 is calculated when the power consumption Wr of the heat source units 2 and 102 is apportioned. The value subtracted from the power consumption Wr (= Wr−Ws) may be apportioned according to the usage-side heat consumption, and the allocation of the standby power Ws of each usage unit may be added to the apportioned power (for example, for the standby power Ws) Can be apportioned by the capacity of the unit used).
-B-
The heat pump system in which the heat source unit power consumption apportioning system can be adopted is not limited to the heat pump systems 1 and 101 described above. For example, in the heat pump system 101 having the utilization units 105a and 105b of the second embodiment, the utilization units 5a and 5b of the first embodiment are connected to the heat source unit 102 via the refrigerant communication tubes 12 and 14. May be.

  The present invention can be widely applied to a heat pump system configured by connecting a plurality of utilization units that perform an aqueous medium heating operation using a dual refrigeration cycle to a heat source unit.

DESCRIPTION OF SYMBOLS 1,101 Heat pump system 1a, 101a Control part 2,102 Heat source unit 5a, 5b, 105a, 105b Utilization unit 10,110 Heat source unit power consumption apportioning system 19a, 119a Use heat amount calculation part 19b, 119b Correction heat amount calculation part 19c, 119c Power apportioning part 21 Heat source side compressors 26a, 26b Heat source side heat exchangers 50a, 50b Use side refrigerant circuit 51a, 51b First use side heat exchangers 55a, 55b Use side compressors 57a, 57b Refrigerant-water heat exchanger 20 , 120 Heat source side refrigerant circuit 151a, 151b Second usage side heat exchanger

JP 2003-314838 A

Claims (4)

A heat source unit (2, 102) having a heat source side compressor for compressing the heat source side refrigerant and a heat source side heat exchanger, and a plurality of utilization units (5a, 5b) having first utilization side heat exchangers (51a, 51b). , 105a, 105b), and a heat source side refrigerant circuit (20, 120) configured by connecting the
Provided in each of the utilization units, a utilization side compressor (55a, 55b) that compresses a utilization side refrigerant different from the heat source side refrigerant, and heating that functions as a radiator of the utilization side refrigerant and heats the aqueous medium Refrigerant-water heat exchanger (57a, 57b) capable of operation, and the first utilization side heat exchanger capable of functioning as a utilization side refrigerant evaporator by heat radiation of the heat source side refrigerant. A use side refrigerant circuit (50a, 50b);
In the heat pump system (1, 101) having a heat source unit power consumption apportioning system that apportions the power consumption of the heat source unit,
Use heat amount calculation unit (19a, 119a) for calculating the use side use heat amount in each use unit from the flow rate and temperature of the aqueous medium,
Heat source side condensation temperature corresponding to the saturation temperature of the heat source side refrigerant in the first usage side heat exchanger functioning as a heat source side refrigerant radiator and a usage side refrigerant evaporator, or the first usage side heat exchanger Refrigeration cycle of each use side refrigerant circuit assumed from the use side evaporating temperature corresponding to the saturation temperature of the use side refrigerant and the aqueous medium outlet temperature which is the temperature of the aqueous medium at the outlet of the refrigerant-water heat exchanger Based on the characteristics, a correction calorific value calculation unit (19b, 119b) for correcting the usage-side usage calorie in each usage unit;
A power apportioning unit (19c, 119c) that apportions the power consumption of the heat source unit in accordance with the corrected usage-side use heat amount,
Heat source unit power consumption apportioning system (10, 110).   The correction calorific value calculation unit (19b, 119b) calculates a first correction coefficient obtained based on the heat source side condensation temperature or the use side evaporation temperature, and a second correction coefficient obtained based on the aqueous medium outlet temperature. The heat source unit power apportioning system (10, 110) according to claim 1, wherein the correction is performed by multiplying the usage-side heat consumption. The heat pump system (1, 101) has a control unit (1a, 101a) for performing operation control,
The control unit controls the operating capacity of the heat source side compressor (21) so that the heat source side condensation temperature becomes a predetermined target heat source side condensation temperature.
The heat source unit power consumption apportioning system (10, 110) according to claim 1 or 2. At least one of the plurality of usage units (105a, 105b) further includes a second usage side heat exchanger (151a, 151b) capable of performing a cooling operation for cooling the aqueous medium by evaporation of the heat source side refrigerant. And
When the cooling operation and the heating operation are performed at the same time in the utilization unit having the second utilization side heat exchanger, the use heat amount calculation unit (119a) determines the cooling operation from the flow rate and temperature of the aqueous medium. Calculate the usage-side heat consumption and the usage-side heat usage of the heating operation,
The correction heat amount calculation unit (119b) is a heat source that is a saturation temperature of the heat source side refrigerant in the first use side heat exchanger (51a, 51b) that functions as a heat source side refrigerant radiator and a use side refrigerant evaporator. A side condensation temperature, or a use side evaporation temperature which is a saturation temperature of a use side refrigerant in the first use side heat exchanger, and a temperature of an aqueous medium at an outlet of the refrigerant-water heat exchanger (57a, 57b). Based on the refrigeration cycle characteristics of each use-side refrigerant circuit (50a, 50b) assumed from the aqueous medium outlet temperature, the use-side use heat amount of the heating operation is corrected, and only the cooling operation or the heating operation is performed. Based on the expected performance value of the heat source side refrigerant circuit (120) when assumed to have been performed, further correcting the usage side usage heat amount, and after correcting the usage side usage heat amount based on the expected performance value, The use side heat consumption of the cooling operation and the use side use heat amount of the heating operation are compared, and either the use side use heat amount of the cooling operation or the use side use heat amount of the heating operation obtained by the comparison is larger. Is used side use heat amount in the use unit having the second use side heat exchanger,
The heat source unit power consumption apportioning system (110) according to any one of claims 1 to 3.

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