JP6175165B1 - Combined system - Google Patents

Abstract

A combined system capable of operating with high efficiency is provided. A selection control unit (C1) is one of at least two operation modes in which electric energy and thermal energy supplied from a cogeneration system (CG) are used by a thermal heat transfer system (ACS) and an electric heat transfer system (EHP). One is automatically selected for optimal use of thermal and electrical energy. The operation control unit C2 executes an operation according to the operation mode automatically selected by the selection control unit C1. [Selection] Figure 1

Description

  The present invention relates to a combination system.

  2. Description of the Related Art Conventionally, there is known a first heat transfer system such as a compression heat pump system that is driven by energy consisting of electricity or power and transfers heat from a cold supply unit to a warm supply unit. In addition, a second heat transfer system that receives drive heat and transfers heat from the cold supply unit to the hot supply unit, such as an absorption refrigeration system, an absorption heat pump system, or an adsorption refrigeration system, is known. .

  In these heat transfer systems, individual heat transfer systems may be used independently. However, in order to improve energy use efficiency, a system using each heat transfer system in combination has been proposed.

  For example, Patent Documents 1 and 2 disclose an air conditioner including a compression heat pump system that is a first heat transfer system and an absorption refrigeration system that is a second heat transfer system.

  Further, in this air conditioner, power for driving the compressor of the compression heat pump system is obtained from the gas engine, and the exhaust heat of the gas engine is used in the absorber refrigeration system. Furthermore, in the air conditioner, the condensation heat generated in the refrigerant circuit of the compression heat pump system is recovered, and this recovered heat is used to heat the absorption liquid sent from the absorber to the regenerator in the absorption refrigeration system. Yes.

JP 2000-146355 A JP 2000-55505 A

  However, such systems are required to manage energy use and operate with high efficiency.

  The present invention has been made in view of such circumstances, and an object thereof is to provide a combined system that can be operated with high efficiency.

In order to solve such a problem, the present invention supplies a first energy composed of electricity or motive power, and also supplies a second energy that is thermal energy generated during driving, and a co-supply system. The first heat transfer system that is driven by receiving the first energy and transfers heat from the cold supply unit to the hot supply unit, the second energy supplied from the cogeneration system , and the heat of the hot supply unit of the first heat transfer system A second heat transfer system that receives one or both driving heats selected from the above and transfers heat from the cold heat supply unit to the hot heat supply unit, and the first heat and the second energy supplied from the co-supply system. One of the at least two operation modes used in the system and the second heat transfer system is automatically selected, and the first energy and the second heat mode are selected. A selection control unit for optimum utilization of the energy, to provide a combination system comprising a driving control unit for executing the operation corresponding to the auto-selected operating mode by the selection control section. In this case, there are at least two operation modes corresponding to the cooling operation mode related to the cooling operation and those corresponding to the heating operation mode related to the heating operation, respectively, and the cooling operation mode related to the cooling operation and the heating operation related to the heating operation. The modes each include a mode in which hot water flowing through the hot heat supply unit of the first heat transfer system is supplied as driving heat for the second heat transfer system.

  Here, in the present invention, the cogeneration system generates electrical energy, supplies the generated electrical energy as the first energy, and supplies the thermal energy generated along with the generation of the first energy as the second energy. A system is preferred. In this case, the operation mode is a cooling operation mode related to the cooling operation, the second energy supplied from the cogeneration system is used as driving heat to drive the second heat transfer system, and the cold water flowing through the cold heat supply unit of the second heat transfer system is supplied. While cooling operation mode used for cooling and driving the second heat transfer system using the second energy supplied from the cogeneration system as driving heat, the cooling water flowing through the cooling heat supply unit of the second heat transfer system is used for cooling, The first heat transfer system is driven by the first energy supplied from the combined supply system, and the cold water flowing through the cold heat supply unit of the first heat transfer system is used for cooling, and the hot water flowing through the hot heat supply unit of the first heat transfer system And a cooling operation mode for supplying the second heat transfer system as drive heat of the second heat transfer system, and the selection control unit is generated in the co-feed system. Electrical demand for electrical energy, and the cooling ability of the second heat transfer system can be output, based on the cooling demand, among the plurality of cooling operation mode, it is preferable to automatically select one.

  In the present invention, the co-feed system is preferably a system that generates and supplies electric energy as the first energy, and generates heat energy generated along with the generation of the first energy as the second energy. . In this case, the operation mode is a heating operation mode related to the heating operation, a heating operation mode in which the second energy supplied from the cogeneration system is directly used for heating, and a second energy supplied from the cogeneration system as the driving heat. While driving the heat transfer system and using the hot water flowing through the heat supply part of the second heat transfer system to which the heat collected from the atmosphere is transferred for heating, the first heat is supplied by the first energy supplied from the cogeneration system. A heating operation mode in which the transfer system is driven and hot water flowing through the heat supply unit of the first heat transfer system is supplied as drive heat for the second heat transfer system, and the second energy supplied from the combined supply system is directly used for heating. On the other hand, the first heat transfer system is driven by the first energy supplied from the co-feeding system, and the heat collected from the atmosphere is transferred. At least a heating operation mode in which hot water flowing through the hot-water supply unit of the system is used for heating, and the selection control unit is configured to supply the electric demand for the electric energy generated in the combined supply system and the second energy supplied from the combined supply system. It is preferable to automatically select any one of a plurality of heating operation modes based on the energy amount, the heating demand, and the outside air temperature.

  In the present invention, the operation mode is a heating operation mode related to the heating operation, and the second heat transfer system is driven using the second energy supplied from the cogeneration system as drive heat, and the heat collected from the atmosphere is transferred. It is preferable to further include a heating operation mode in which the hot water flowing through the heat supply unit of the second heat transfer system is used for heating.

  In the present invention, the combined supply system is preferably a system that generates and supplies electric energy as the first energy and supplies the thermal energy generated along with the generation of the first energy as the second energy. . In this case, the operation mode is a cooling operation mode related to the cooling operation, the second energy supplied from the cogeneration system is used as driving heat to drive the second heat transfer system, and the cold water flowing through the cold heat supply unit of the second heat transfer system is supplied. While being used for cooling, the first heat transfer system is driven by the first energy supplied from the cogeneration system, and the cold water flowing through the cold heat supply unit of the first heat transfer system is used for cooling, and the first heat transfer system A cooling operation mode in which hot water flowing through the hot heat supply unit is supplied as drive heat for the second heat transfer system, and the second heat transfer system is driven by using the second energy supplied from the co-supply system as drive heat. The cold water flowing through the cold heat supply section is used for cooling, while the first heat transfer system is driven by the first energy supplied from the cogeneration system, At least a cooling operation mode in which the cold water flowing through the cold heat supply unit of the heat transfer system is used for cooling and the hot water flowing through the hot heat supply unit of the first heat transfer system is radiated to the atmosphere. Based on the above, it is preferable to automatically select any one of a plurality of cooling operation modes.

  In the present invention, the co-feed system is preferably a system that generates and supplies electric energy as the first energy, and generates heat energy generated along with the generation of the first energy as the second energy. . In this case, the operation mode is a heating operation mode related to the heating operation, the second heat transfer system is driven by using the second energy supplied from the cogeneration system as drive heat, and the heat collected from the atmosphere is transferred second. While the hot water flowing through the heat supply unit of the heat transfer system is used for heating, the first heat transfer system is driven by the first energy supplied from the cogeneration system, and the hot water flowing through the heat supply unit of the first heat transfer system is The heating operation mode supplied as driving heat of the two heat transfer system and the second energy supplied from the co-feed system are directly used for heating, while the first heat transfer system is driven by the first energy supplied from the co-feed system. And at least a heating operation mode in which hot water flowing through the heat supply section of the first heat transfer system to which heat collected from the atmosphere is transferred is used for heating. Wherein, the selection control unit, based on the outside air temperature, among a plurality of heating operation mode, it is preferable to automatically select one.

  In the present invention, the selection control unit uses the second energy supplied from the co-supply system for supplying cold / hot water, and the first energy generated in the co-supply system is used for supplying cold / hot water. It is preferable to automatically select the operation mode and automatically adjust the operation load so as to meet the power demand from the outside.

  Furthermore, in the present invention, it is preferable that the selection control unit automatically selects the operation mode and automatically adjusts the operation load so that the first energy supplied from the cogeneration system is consumed in the combined system.

  According to the present invention, the two energies can be optimally utilized with high efficiency.

Explanatory drawing which shows the structure of the combined use system which concerns on this embodiment typically Flow chart showing processing of automatic selection of operation mode in cooling operation Explanatory drawing which shows the path | route of the cold / hot water in 1st air_conditionaing | cooling operation mode Explanatory drawing which shows the path | route of the cold / hot water in 2nd air_conditionaing | cooling operation mode Explanatory drawing which shows the path | route of the cold / hot water in 3rd air_conditionaing | cooling operation mode Explanatory drawing which shows the path | route of the cold / hot water in 4th air_conditionaing | cooling operation mode Explanatory drawing which shows the temperature relationship of the cold / hot water corresponding to each cooling operation mode The flowchart which shows the process of the automatic selection of the operation mode in heating operation Explanatory drawing which shows the path | route of the cold / hot water in 1st heating operation mode Explanatory drawing which shows the path | route of the cold / hot water in 2nd heating operation mode Explanatory drawing which shows the path | route of the cold / hot water in 3rd heating operation mode Explanatory drawing which shows the path | route of the cold / hot water in 4th heating operation mode Explanatory drawing which shows the path | route of the cold / hot water in 5th heating operation mode Explanatory drawing which shows the path | route of the cold / hot water in 6th heating operation mode Explanatory drawing which shows the temperature relationship of the cold / hot water corresponding to each heating operation mode Flow chart showing processing of automatic selection of operation mode in cooling operation The flowchart which shows the process of the automatic selection of the operation mode in heating operation

  FIG. 1 is an explanatory diagram schematically showing the configuration of the combined system according to the present embodiment. The combined system according to the present embodiment performs air conditioning (cooling and heating) using electric energy and thermal energy in combination, and includes a cogeneration system CG, a thermal heat transfer system (second heat transfer system) ACS, It has an electric heat transfer system (first heat transfer system) EHP, an outdoor radiator OR, an indoor unit IC, and a control unit C.

  The cogeneration system CG includes a gas engine GE, a generator GN, and a water jacket WJ.

  The gas engine GE is driven using gas supplied from a gas supply source (not shown). The output shaft of the gas engine GE is connected to the generator GN.

  The generator GN generates power by being driven by the gas engine GE. The electric power generated by the generator GN is supplied to the switchboard SWBD via the power controller PC, and various loads used in the combined system from the switchboard SWBD and external loads scheduled to be used by the cogeneration system CG. To be supplied. A grid power supply (not shown) is connected to the switchboard SWBD, and power from the grid power supply can be supplied in addition to the power generated by the generator GN.

  The water jacket WJ is provided in the gas engine GE. The water jacket WJ cools the gas engine GE when cooling water (warm water) for cooling flows from the inlet side to the outlet side.

  On the outlet side of the water jacket WJ, a first pipe R1, a second pipe R2, a third pipe R3, and a fourth pipe R4 are connected in this order, and the fourth pipe R4 is connected to the thermal heat transfer system ACS. It is connected to the inlet side of the drive heat receiving part DHP. These pipes R1 to R4 form a flow path that guides the hot water flowing out from the water jacket WJ to the drive heat receiving part DHP of the thermal heat transfer system ACS.

  The first pipe R1 is provided with a first pump P1 serving as a power source for circulating hot water. The first pump P1 is operated so that the hot water reaches from the inlet side to the outlet side through the inside of the water jacket WJ. In addition, a first valve V1, a second valve V2, and a third valve V3 are respectively provided at connection portions of the first pipe R1, the second pipe R2, the third pipe R3, and the fourth pipe R4. Each of the first valve V1 to the third valve V3 is a three-way solenoid valve.

  On the other hand, a fifth pipe R5, a sixth pipe R6, a seventh pipe R7, and an eighth pipe R8 are connected in this order to the outlet side of the drive heat receiving unit DHP of the thermal heat transfer system ACS. The pipe R8 is connected to the inlet side of the water jacket WJ. These pipes R5 to R8 form a flow path for guiding the hot water flowing out from the drive heat receiving part DHP of the thermal heat transfer system ACS to the water jacket WJ.

  In addition, a fourth valve V4, a fifth valve V5, and a sixth valve V6 are provided at each connection portion of the fifth pipe R5, the sixth pipe R6, the seventh pipe R7, and the eighth pipe R8, respectively. Each of the fourth valve V4 to the sixth valve V6 is a three-way solenoid valve.

  The cogeneration system CG corresponds to a combined supply system that generates electric energy, supplies the generated electric energy, and supplies heat energy generated when the electric energy is generated.

  The thermal heat transfer system ACS introduces an evaporator that evaporates the refrigerant, an absorber that absorbs the refrigerant vapor introduced from the evaporator into the absorption liquid, and an absorption liquid after the refrigerant is absorbed by the absorber. A regenerator that discharges the refrigerant from the absorption liquid and a condenser that condenses the refrigerant vapor sent out from the regenerator are included. This thermal heat transfer system ACS takes out cold heat with an evaporator when used as a refrigerator, and takes out heat with a condenser when used as a heat pump device.

  When this is viewed functionally, the thermal heat transfer system ACS is constituted by a cold heat supply unit CSA, a heat supply unit HSA, and a drive heat receiving unit DHP.

  The cold heat supply unit CSA is provided in the evaporator and lowers the temperature of the cold water flowing from the inlet side to the outlet side. A ninth pipe R9 is connected to the inlet side of the cold heat supply unit CSA, and a tenth pipe R10 is connected to the outlet side of the cold heat supply part CSA. The ninth pipe R9 is provided with a second pump P2 serving as a power source for circulating cold water. The second pump P2 is operated so that the cold water reaches from the inlet side to the outlet side via the cold heat supply unit CSA.

  The hot heat supply unit HSA is provided in the condenser and raises the temperature of hot water flowing from the inlet side to the outlet side. The eighteenth pipe R18 is connected to the inlet side of the heat supply unit HSA, and the thirteenth pipe R13 is connected to the outlet side of the heat supply unit HSA. The eighteenth pipe R18 is provided with a third pump P3 serving as a power source for circulating hot water. The third pump P3 is operated so that the hot water reaches the outlet side from the inlet side via the hot heat supply unit HSA.

  The driving heat receiving unit DHP is provided in the regenerator and receives driving heat from the hot water flowing from the inlet side to the outlet side.

  The thermal heat transfer system ACS corresponds to a second heat transfer system that receives drive heat and transfers heat from the cold heat supply unit CSA to the hot heat supply unit HSA.

  The electric heat transfer system EHP circulates the refrigerant discharged from the compressor driven by the electric motor so as to return to the compressor through the condenser, the expansion valve, and the evaporator, and absorbs heat in the evaporator and heat radiation in the condenser. It is used for air conditioning.

  The electric heat transfer system EHP includes a cold heat supply unit CSE and a hot heat supply unit HSE.

  The cold heat supply unit CSE is provided in the evaporator and lowers the temperature of the cold water flowing from the inlet side to the outlet side. A thirty-second pipe R32 is connected to the inlet side of the cold heat supply unit CSE, and a thirty-third pipe R33 is connected to the outlet side of the cold heat supply part CSE. The 32nd piping R32 is provided with the 4th pump P4 used as the power source which circulates cold water. The fourth pump P4 is normally operated so that the cold water reaches the outlet side from the inlet side via the cold heat supply unit CSE, but can be operated with the direction reversed if necessary. is there.

  The hot heat supply unit HSE is provided in the condenser and raises the temperature of hot water flowing from the inlet side to the outlet side. The eleventh pipe R11 is connected to the inlet side of the heat supply unit HSA, and the twelfth pipe R12 is connected to the outlet side of the heat supply unit HSE. The eleventh pipe R11 is provided with a fifth pump P5 serving as a power source for circulating hot water. The fifth pump P5 is operated so that the hot water reaches the outlet side from the inlet side via the hot heat supply unit HSE.

  This electric heat transfer system EHP is driven by receiving electric energy supplied from the cogeneration system CG, and corresponds to a first heat transfer system that transfers heat from the cold heat supply unit CSE to the hot heat supply unit HSE.

  The outdoor radiator OR is a heat exchanger that exchanges heat with the atmosphere by flowing cold / hot water supplied from the inlet side to the outlet side, and moves the cold / hot water up and down. When an indoor unit IC, which will be described later, is used for cooling, hot water is supplied to the outdoor radiator OR. In this case, the outdoor radiator OR lowers the temperature of the hot water by exchanging heat with the atmosphere. On the other hand, when the indoor unit IC is used for heating, cold water is supplied to the outdoor radiator OR. In this case, the outdoor radiator OR raises the temperature of the cold water by exchanging heat with the atmosphere.

  A thirty-first pipe R31 is connected to the inlet side of the outdoor radiator OR, and a thirty-fourth pipe R34 is connected to the outlet side of the outdoor radiator OR.

  The indoor unit IC is provided in a room that is used for air conditioning, and the supplied cold / hot water flows from the inlet side to the outlet side to exchange heat with the indoor air, and to heat the indoor air up and down. It is. When the indoor unit IC is used for cooling, cold water is supplied to the indoor unit IC. In this case, the indoor unit IC cools (cools) the indoor air by exchanging heat with the indoor air. On the other hand, when the indoor unit IC is used for heating, hot water is supplied to the indoor unit IC. In this case, the indoor unit IC heats up (heats) the indoor air by exchanging heat with the indoor air.

  The fifteenth pipe R15 is connected to the inlet side of the indoor unit IC, and the sixteenth pipe R16 is connected to the outlet side of the indoor unit IC.

  In the combined supply system according to the present embodiment, the pipes are connected to each other so that heat energy can be exchanged among the cogeneration system CG, the thermal heat transfer system ACS, and the electric heat transfer system EHP.

  First, the twelfth pipe R12 on the outlet side of the heat supply unit HSE of the electric heat transfer system EHP and the ninth pipe R9 on the inlet side of the cold heat supply part CSA of the thermal heat transfer system ACS are connected via the seventh valve V7. Connected. The eleventh pipe R11 on the inlet side of the hot heat supply unit HSE of the electric heat transfer system EHP and the tenth pipe R10 on the outlet side of the cold heat supply part CSA of the thermal heat transfer system ACS are connected via an eighth valve V8. Connected. The seventh valve V7 and the eighth valve V8 are each a four-way solenoid valve.

  The thirty-first pipe R31 on the inlet side of the outdoor radiator OR and the thirty-second pipe R32 on the inlet side of the cold heat supply unit CSE of the electric heat transfer system EHP are connected via a thirteenth valve V13. In addition, the 34th pipe R34 on the outlet side of the outdoor radiator OR and the 33rd pipe R33 on the outlet side of the cold heat supply unit CSE of the electric heat transfer system EHP are connected via a 14th valve V14. Each of the thirteenth valve V13 and the fourteenth valve V14 is a three-way solenoid valve.

  The thirteenth pipe R13 on the outlet side of the heat supply section HSA of the thermal heat transfer system ACS and the fifteenth pipe R15 on the inlet side of the indoor unit IC are connected via a fourteenth pipe R14. A ninth valve V9 is provided at the connection between the thirteenth pipe R13 and the fourteenth pipe R14, and a tenth valve V10 is provided at the connection between the fourteenth pipe R14 and the fifteenth pipe R15. Yes. Each of the ninth valve V9 and the tenth valve V10 is a three-way solenoid valve.

  A connection portion between the eighteenth pipe R18 on the inlet side of the heat supply unit HSA of the thermal heat transfer system ACS and the sixteenth pipe R16 on the outlet side of the indoor unit IC is connected via a seventeenth pipe R17. A twelfth valve V12 is provided at the connection between the eighteenth pipe R18 and the seventeenth pipe R17, and an eleventh valve V11 is provided at the connection between the sixteenth pipe R16 and the seventeenth pipe R17. Yes. Each of the eleventh valve V11 and the twelfth valve V12 is a three-way solenoid valve.

  The 27th pipe R27 and the 25th pipe R25 are connected in this order from the remaining port of the 13th valve V13 to the remaining port of the 9th valve V9. A twentieth valve V20, which is a three-way solenoid valve, is provided at a connection portion between the 27th pipe R27 and the 25th pipe R25.

  The 28th pipe R28 and the 26th pipe R26 are connected in this order from the remaining port of the 14th valve V14 to the remaining port of the 12th valve V12. A connecting portion between the 28th pipe R28 and the 26th pipe R26 is provided with a 19th valve V19 which is a three-way solenoid valve.

  The remaining port of the eleventh valve V11 is connected to the nineteenth pipe R19, the twenty-first pipe R21, and the twenty-ninth pipe R29 in this order, and the end of the twenty-ninth pipe R29 is an intermediate portion of the twenty-eighth pipe R28. It is connected to the. An eighteenth valve V18 and a sixteenth valve V16 are provided at each connection portion of the nineteenth pipe R19, the twenty-first pipe R21, and the twenty-ninth pipe R29, respectively.

  The remaining port of the tenth valve V10 is connected to the 20th pipe R20, the 22nd pipe R22, and the 30th pipe R30 in this order, and the end of the 30th pipe R30 is the middle part of the 27th pipe R27. It is connected to the. In addition, a 17th valve V17 and a 15th valve V15 are provided at each connection portion of the 20th pipe R20, the 22nd pipe R22, and the 30th pipe R30, respectively.

  The remaining port of the first valve V1 and the remaining port of the sixteenth valve V16 are connected via a twenty-third pipe R23. Further, the remaining port of the second valve V2 and the remaining port of the 18th valve V18 are connected via a 35th pipe R35.

  The remaining port of the third valve V3 is connected to the 36th pipe R36, and the end of the 36th pipe R36 is connected to the 37th pipe R37 via the seventh valve V7. The end of the 37th pipe R37 is connected to the remaining port of the 20th valve V20.

  The remaining port of the fourth valve V4 is connected to the 38th pipe R38, and the end of the 38th pipe R38 is connected to the 39th pipe R39 via the eighth valve V8. The end of the 39th pipe R39 is connected to the remaining port of the 19th valve V19.

  The remaining port of the fifth valve V5 and the remaining port of the 17th valve V17 are connected via a 40th pipe R40. Further, the remaining port of the sixth valve V6 and the remaining port of the 15th valve V15 are connected via a 24th pipe R24.

  The control unit C controls the combined system. The control unit C includes a selection control unit C1 and an operation control unit C2. The selection control unit C1 automatically uses any one of at least two operation modes in which the electric energy and thermal energy supplied from the cogeneration system CG are used by the thermal heat transfer system ACS and the electric heat transfer system EHP. Select to make optimal use of thermal and electrical energy. The operation control unit C2 executes an operation according to the operation mode automatically selected by the selection control unit C1.

  In order to perform such control, information detected by various sensors (not shown) is input to the control unit C. Specifically, the room temperature sensor T1 detects the temperature of the air in the room where the indoor unit IC is provided. The energy temperature sensor T2 is a sensor that detects the temperature of hot water near the outlet of the water jacket WJ. The outside air temperature sensor T3 detects the outdoor temperature (outside air temperature) where the outdoor radiator OR is provided.

  Further, an operation panel (not shown) is connected to the control unit C, and the air conditioning temperature set by the air conditioning user operating the operation panel can be acquired.

  Hereinafter, the air conditioning operation of the co-feed system according to the present embodiment will be described. In this combined supply system, air-conditioning operation is performed while electric power generated by the cogeneration system CG is supplied to various loads used in the combined system and external loads scheduled to be used by the combined system.

  First, the cooling operation will be described. In the present embodiment, the selection control unit C1 has a first cooling operation mode, a second cooling operation mode, and a third cooling operation mode as operation modes, specifically, cooling operation modes related to cooling operation. The selection control unit C1 automatically selects any one of the three cooling operation modes based on the cooling capacity that can be output by the thermal heat transfer system ACS and the cooling demand. Here, FIG. 2 is a flowchart showing processing for automatically selecting an operation mode in the cooling operation.

  First, in step 1 (S1), the operation control unit C2 operates the load of the cogeneration system CG according to the electric demand. Here, the electric demand is determined in consideration of the current electric energy consumed in the external load, the electric energy consumed in the load of the combined system when operating in the cooling operation mode described later, and the like. That is, the operation control unit C2 adjusts the operation load of the cogeneration system CG according to the electric demand.

  In step 2 (S2), the selection control unit C1 determines whether or not the thermal performance is equal to or higher than the cooling demand. Here, the cooling demand is obtained based on the indoor temperature obtained from the room temperature sensor T1 and the air conditioning temperature set by the user. On the other hand, the thermal capacity is the maximum cooling capacity that the thermal heat transfer system ACS can output in the amount of heat of hot water obtained from the cogeneration system CG with the load at that time, but the maximum value is the thermal heat transfer This is a specified value determined from the performance of the system ACS.

  If the thermal capacity is equal to or greater than the cooling demand, an affirmative determination is made in step 2 and the process proceeds to step 3 (S3). On the other hand, if the thermal capacity is lower than the cooling demand, a negative determination is made in step 2, and the process proceeds to step 4 (S4).

  In step 3, the selection control unit C1 selects the first cooling operation mode. Here, FIG. 3 is an explanatory diagram showing a path of cold / hot water in the first cooling operation mode.

  In the first cooling operation mode, hot water is circulated between the cogeneration system CG and the drive heat receiving part DHP of the thermal heat transfer system ACS, and the hot water heated in the cogeneration system CG is Received as drive heat in the heat transfer system ACS.

  Cold water is circulated between the cold heat supply unit CSA of the thermal heat transfer system ACS and the indoor unit IC, and the cold water cooled in the cold heat supply unit CSA of the thermal heat transfer system ACS is used for cooling in the indoor unit IC. The

  Hot water is circulated between the heat supply unit HSA of the thermal heat transfer system ACS and the outdoor radiator OR, and the hot water heated in the heat supply unit HSA of the heat dynamic heat transfer system ACS is radiated in the outdoor radiator OR. The

  And the operation control part C2 performs the operation | movement according to the 1st cooling operation mode automatically selected by the selection control part C1. In this mode, the power consumption is very small, so that the power supplied from the cogeneration system CG can be used for other power demands as much as possible.

  In step 4, the selection control unit C1 determines whether or not the outside air temperature detected by the outside air temperature sensor T3 is 25 ° C. or higher. If the outside air temperature is 25 ° C. or higher, an affirmative determination is made in step 4 and the process proceeds to step 5 (S5). On the other hand, if the outside air temperature is lower than 25 ° C., a negative determination is made in step 4, and the process proceeds to step 6 (S 6).

  In step 5, the selection control unit C1 selects the second cooling operation mode. Here, FIG. 4 is an explanatory diagram showing a path of cold / warm water in the second cooling operation mode.

  In the second cooling operation mode, hot water is circulated between the cogeneration system CG and the drive heat receiving part DHP of the thermal heat transfer system ACS, and the hot water heated in the cogeneration system CG is Received as drive heat in the heat transfer system ACS.

  Hot water is circulated between the heat supply unit HSE of the electric heat transfer system EHP and the drive heat receiving unit DHP of the thermal heat transfer system ACS, and the hot water heated in the heat supply unit HSE of the electric heat transfer system EHP is And received as drive heat in the thermal heat transfer system ACS.

  Cold water is circulated between the cold heat supply unit CSA of the thermal heat transfer system ACS and the cold heat supply unit CSE of the electric heat transfer system EHP, and the indoor unit IC, and the cold water cooled in each of the cold heat supply units CSA and CSE Is used for cooling in the indoor unit IC.

  Hot water is circulated between the heat supply unit HSA of the thermal heat transfer system ACS and the outdoor radiator OR, and the hot water heated in the heat supply unit HSA of the heat dynamic heat transfer system ACS is radiated in the outdoor radiator OR. The

  In addition, the operation control unit C2 adjusts the operation load of the cogeneration system so as to correspond to the selection of the second cooling operation mode. And the operation control part C2 performs the operation | movement according to the 2nd cooling operation mode automatically selected by the selection control part C1.

  In the second cooling operation mode, the electric heat transfer system EHP is cooled, and both hot water generated by the cooling operation and gas hot water are used for driving heat of the thermal heat transfer system ACS. In this mode, surplus heat is difficult to circulate, but surplus power is easy to divert and circulate. Therefore, the thermal heat transfer system ACS is operated at full load as much as possible, and when the air conditioning demand cannot be satisfied, the electric heat transfer system EHP is limitedly operated as much as necessary, so that the cooling operation with surplus power can be performed. It can be carried out.

  In step 6, the selection control unit C1 selects the third cooling operation mode. Here, FIG. 5 is an explanatory diagram showing a path of cold / hot water in the third cooling operation mode.

  In the third cooling operation mode, hot water is circulated between the cogeneration system CG and the drive heat receiving unit DHP of the thermal heat transfer system ACS, and the hot water heated in the cogeneration system CG is Received as drive heat in the heat transfer system ACS.

  Cold water is circulated between the cold heat supply unit CSA of the thermal heat transfer system ACS and the cold heat supply unit CSE of the electric heat transfer system EHP, and the indoor unit IC, and the cold water cooled in each of the cold heat supply units CSA and CSE Is used for cooling in the indoor unit IC.

  Hot water is circulated between the heat supply unit HSA of the thermal heat transfer system ACS and the heat supply unit HSE of the electric heat transfer system EHP and the outdoor radiator OR, and the hot water heated in each heat supply unit HSA, HSE is Heat is dissipated in the outdoor radiator OR.

  In addition, the operation control unit C2 adjusts the operation load of the cogeneration system so as to correspond to the selection of the third cooling operation mode. The operation control unit C2 executes an operation according to the third cooling operation mode automatically selected by the selection control unit C1.

  In the third cooling operation mode, the electric heat transfer system EHP is cooled, the heat of the hot water generated by the cooling operation is discarded to the atmosphere, and the thermal heat transfer system ACS is obtained from the cogeneration system CG. Cooling operation is performed using only hot water as driving heat. When the outside air temperature is not high, power consumption can be suppressed more than the second cooling operation by suppressing the temperature of the hot water generated by the electric heat transfer system EHP to about 10 ° C. above the outside air temperature. .

  In such a cooling operation mode, the following fourth cooling operation mode can be used. Here, FIG. 6 is an explanatory diagram showing a path of cold / hot water in the fourth cooling operation mode. In the fourth cooling operation mode, the twenty-first valve V21 is provided in the twenty-fifth pipe R25, and the twenty-first valve V21 is connected to the twenty-first pipe R21. The twenty-sixth pipe R26 is provided with a twenty-second valve V22, and the twenty-second valve V22 is connected to the twenty-second pipe R22.

  In the fourth cooling operation mode, the thermal heat transfer system ACS is heated only by driving heat of hot water obtained from the cogeneration system CG, and the hot water generated at that time is supplied to the cold heat supply unit CSE of the electric heat transfer system EHP. This heat is transferred to the warm heat supply unit HSE, and is radiated to the atmosphere via warm water from the warm heat supply unit HSE.

  According to the fourth cooling operation mode, even when the hot water temperature of the heat and heat transfer system ACS is not sufficiently higher than the outside air temperature and it is difficult to release heat to the atmosphere as it is, the cooling operation using the gas hot water as driving heat is performed. It can be carried out. This fourth cooling operation mode is particularly effective in areas with high temperatures, and can be used as an alternative to the first cooling operation mode.

  Here, the temperature relationship of the cold / hot water corresponding to each cooling operation mode is as shown in FIG. 7, for example.

  Next, the heating operation will be described. In the present embodiment, the selection control unit C1 has a first heating operation mode, a second heating operation mode, and a third heating operation mode as operation modes, specifically, heating operation modes related to the heating operation. The selection control unit C1 automatically selects one of the three heating operation modes based on the amount of heat (heat energy) of the hot water output from the cogeneration system CG, the heating demand, and the outside air temperature. . Here, FIG. 8 is a flowchart showing a process of automatically selecting the operation mode in the heating operation.

  First, in step 10 (S10), the operation control unit C2 operates the load of the cogeneration system CG according to the electric demand. Here, the electricity demand is determined in consideration of the current amount of power consumed in the external load, the amount of power consumed in the load of the combined system when the heating operation mode described later is used, and the like.

  In step 11 (S11), the selection control unit C1 determines whether or not the supply heat amount is equal to or greater than the heating demand. Here, the heating demand is obtained based on the indoor temperature obtained from the room temperature sensor T1 in the co-supply system and the air conditioning temperature set by the user. On the other hand, the amount of heat supplied is the amount of heat of hot water output from the cogeneration system CG, and varies depending on the operation load of the cogeneration system CG. Usually, however, to maintain the operating state of the gas engine GE, etc. In addition, the flow rate of the first pump P1 is controlled based on the temperature of the hot water obtained from the energy temperature sensor T2 so that the temperature falls within a certain range. Therefore, although the heat supplied from the gas engine GE has a substantially constant temperature, the amount of supplied heat varies with the output of the first pump P1.

  If the supplied heat quantity is equal to or greater than the heating demand, an affirmative determination is made in step 11 and the process proceeds to step 12 (S12). On the other hand, when the supply heat quantity is lower than the heating demand, a negative determination is made in step 11 and the process proceeds to step 13 (S13).

  In step 12, the selection control unit C1 selects the first heating operation mode. Here, FIG. 9 is an explanatory diagram showing a path of cold / hot water in the first heating operation mode.

  In the first heating operation mode, hot water is circulated between the cogeneration system CG and the indoor unit IC, and the hot water heated in the cogeneration system CG is heated and used in the indoor unit IC.

  Operation control part C2 performs operation according to the 1st heating operation mode automatically selected by selection control part C1. Since this first heating operation mode consumes very little power, the power supplied from the cogeneration system CG can be used for other power demands as much as possible.

  In step 13, the selection control unit C1 determines whether or not the outside air temperature detected by the outside air temperature sensor T3 is 15 ° C. or higher. If the outside air temperature is 15 ° C. or higher, an affirmative determination is made in step 13 and the process proceeds to step 14 (S14). On the other hand, if the outside air temperature is lower than 15 ° C., a negative determination is made in step 13, and the process proceeds to step 15 (S15).

  In step 14, the selection control unit C1 selects the second heating operation mode. Here, FIG. 10 is an explanatory diagram showing a path of cold / hot water in the second heating operation mode.

  In the second cooling operation mode, hot water is circulated between the cogeneration system CG and the drive heat receiving part DHP of the thermal heat transfer system ACS, and the hot water heated in the cogeneration system CG is Received as drive heat in the heat transfer system ACS.

  Hot water is circulated between the heat supply unit HSE of the electric heat transfer system EHP and the drive heat receiving unit DHP of the thermal heat transfer system ACS, and the hot water heated in the heat supply unit HSE of the electric heat transfer system EHP is And received as drive heat in the thermal heat transfer system ACS.

  Cold water is circulated between the cold heat supply unit CSA of the thermal heat transfer system ACS and the cold heat supply unit CSE of the electric heat transfer system EHP, and the outdoor radiator OR, and the cold water cooled in each of the cold heat supply units CSA and CSE Is heated in the outdoor radiator OR.

  Warm water is circulated between the heat supply unit HSA of the thermal heat transfer system ACS and the indoor unit IC, and the hot water heated in the heat supply unit HSA of the heat dynamic heat transfer system ACS is heated in the indoor unit IC. Is done.

  Moreover, the operation control unit C2 adjusts the operation load of the cogeneration system so as to correspond to the selection of the second heating operation mode. And the operation control part C2 performs the operation | movement according to the 2nd heating operation mode automatically selected by the selection control part C1.

  In the second heating operation mode, the heat and heat transfer system ACS is driven by gas hot water, and at the same time, the heat and heat transfer system ACS is driven by hot water collected from the atmosphere in the electric heat transfer system EHP. Thereby, large capacity heating operation can be performed.

  In step 15, the selection control unit C1 selects the third heating operation mode. Here, FIG. 11 is an explanatory diagram showing a path of cold / hot water in the third heating operation mode.

  In the third cooling operation mode, hot water is circulated between the cogeneration system CG and the indoor unit IC, and the hot water heated in the cogeneration system CG is heated and used in the indoor unit IC.

  Further, hot water is circulated between the hot heat supply unit HSE of the electric heat transfer system EHP and the indoor unit IC, and the hot water heated in the hot heat supply unit HSE of the electric heat transfer system EHP is heated in the indoor unit IC. Is done.

  Cold water is circulated between the cold heat supply unit CSE of the electric heat transfer system EHP and the outdoor radiator OR, and the cold water cooled in the cold heat supply unit CSE of the electric heat transfer system EHP is heated in the outdoor radiator OR.

  Moreover, the operation control unit C2 adjusts the operation load of the cogeneration system so as to correspond to the selection of the third heating operation mode. Operation control part C2 performs operation according to the 3rd heating operation mode automatically selected by selection control part C1.

  In this third heating operation mode, hot gas water is directly used for heating, and at the same time, hot water for heating is generated while collecting air in the electric heat transfer system EHP. Even when the outside air temperature is low and the thermal heat transfer system ACS cannot collect air, heating operation with a relatively large capacity can be performed.

  In addition, in such a heating operation mode, the 6th heating operation mode can be utilized from the 4th heating operation mode shown below.

  FIG. 12 is an explanatory diagram showing a path of cold / hot water in the fourth heating operation mode. In the fourth heating operation mode, the heating operation is performed by driving the thermal heat transfer system ACS using gas hot water as driving heat. This fourth cooling operation mode also consumes very little power. Therefore, when the outside air temperature is high to some extent and the atmospheric heat collection by the thermal heat transfer system ACS is possible, the heating operation can be performed with as much power as possible while supplying a large amount of heating hot water.

  FIG. 13 is an explanatory diagram showing a path of cold / hot water in the fifth heating operation mode. In the fifth heating operation mode, the thermal heat transfer system ACS is driven by using only gas hot water as driving heat to perform heating operation by atmospheric heat collection, and the electric heat transfer system EHP also performs heating operation by atmospheric heat collection. Yes. When the outside air temperature is high to some extent and the heat collection by the thermal heat transfer system ACS is possible, the maximum amount of hot water for heating can be supplied. In the fifth heating mode, the discharge direction of the fourth pump P4 is operated in the reverse direction.

  FIG. 14 is an explanatory diagram showing a path of cold / hot water in the sixth heating operation mode. In the sixth heating operation mode, a heating operation by atmospheric heat collection is performed by the electric heat transfer system EHP. The thermal heat transfer system ACS is an operation in which the heating operation for collecting heat from the hot water generated in the electric heat transfer system EHP (cold water at the input of the thermal heat transfer system ACS) is driven using the gas hot water as drive heat. Mode. Even when the outside air temperature is low and atmospheric heat collection by the thermal heat transfer system ACS is not directly possible, the necessary amount of heat is supplied to the hot water for heating without applying a load to the electric heat transfer system EHP. be able to.

  Here, the temperature relationship of the cold / hot water corresponding to each heating operation mode is as shown in FIG. 15, for example.

Specific examples will be described below. The target building of the combined supply system is a typical office building with a high heat insulation specification having a floor area of about 3600 m ² and the air conditioning scale is about 65 refrigeration tons.

  In the gas engine GE, the energy efficiency of power generation is about 40%, and the energy efficiency of heat recovery is about 50%. The gas engine GE consumes 100 kW of fuel when rated to generate 40 kW of power and 50 kW of hot water. The electric heat transfer system EHP takes in 40 kW at the maximum load and produces 96 kW cold water and 136 kW hot water. The thermal heat transfer system ACS obtains hot water of 50 kW from the gas engine and 136 kW of hot water from the electric heat transfer system at the maximum load, and produces 130 kW of cold water. Combined with that from the electric heat transfer system EHP, 226 kW of cold water is obtained and has a cooling capacity of about 65 refrigeration tons.

  In practice, such peak demand does not occur easily, and it is usually operated at a low load. Suppose that there is a cooling demand of 20 tons of refrigeration. In such a case, in order to minimize the fuel cost of this cogeneration system CG, 29 kW of cold water from the electric heat transfer system EHP and 12 kW of electric power generated with the gas engine GE loaded at 30% load and the gas engine A total of 68 kW of cold water, which is 15 kW from the GE and 41 kW to 39 kW of cold water from the electric heat transfer system EHP, may be obtained to meet the cooling demand of 20 refrigeration tons.

  For example, when the power demand of 20 kW is in an application (external load) other than air conditioning, the gas engine GE may be operated with a 73% load. In this case, 29 kW of electric power is obtained, 20 kW is used for other electric power demand, and 9 kW is used for the electric heat transfer system to obtain 22 kW of cold water and 31 kW of hot water. In addition, since the cold water of 48 kW is generated from the hot water of 68 kW together with the hot water of 37 kW from the gas engine GE, a total of 70 kW of cold water can be obtained to meet the cooling demand of 20 refrigeration tons.

  In this case, compared with the case where the combined system is used only for refrigeration demand, the fuel of the gas engine GE can be obtained with a fuel consumption increase of 43 kW in a simple proportional calculation to supply 20 kW of surplus power. Surplus power will be obtained with an energy efficiency of 46.5%. In general, since the gas engine GE has a low fuel consumption rate at a low load, in practice, it is more advantageous to operate at an operation close to the rating and to send surplus power to other demands.

In the above example, when power (kW) and cooling demand (kW) to be supplied to an external load other than the load of the combined supply system are given, the engine load (kW) to be set is calculated by the following formula 1. it can.
Engine load (kW) = {cooling demand (kW) + 4.8 × electric power supplied to external load (kW)} / 2.26 (Expression 1)

  In this way, the supply from the co-supply system can be operated for both the air conditioning demand and the power demand. In addition, comparing the fuel consumption of the gas engine GE and the cost of grid power that fluctuates depending on the time zone, whether to purchase power from the grid power supply or raise the output of the cogeneration system CG and increase the private power generation ratio automatically Judgment can also be made on optimum driving.

  As described above, according to the present embodiment, any one of at least two operation modes in which the electric energy and the thermal energy supplied from the cogeneration system CG are used by the electric heat transfer system EHP and the thermal heat transfer system ACS. One is automatically selected for optimal use of electrical energy and thermal energy. In this case, the selection control unit C1 uses the heat supplied from the cogeneration system CG for the supply of cold / hot water, and the electricity generated in the cogeneration system CG is used for the supply of the cold / hot water to the outside. The operation mode is automatically selected and the operation load is automatically adjusted to meet the power demand from the factory.

  According to this structure, two energy of heat and electricity can be utilized with high efficiency.

  According to this combination, supply from the cogeneration system CG can be adjusted simultaneously with electric power and heat according to the air conditioning demand, and the fuel used by the cogeneration system CG can be used without waste. And since the air-conditioning demand and the supply from the cogeneration system CG can be matched, the heat can always be used without any excess.

  In this combined supply system, the situation where the electricity generated by the cogeneration system CG is supplied to an external load has been described. However, if the combined system does not supply electricity to the external load, the selection control unit C1 automatically selects the operation mode so that the electricity supplied from the cogeneration system CG is consumed in the combined system and reduces the operation load. It is preferable to adjust automatically. Specifically, as shown in FIGS. 16 and 17, during the cooling operation, the second cooling operation mode and the third cooling operation mode are automatically selected according to the outside air temperature, and during the heating operation, the second cooling operation mode is selected according to the outside air temperature. The 2 heating operation mode and the 3rd heating operation mode are automatically selected.

  Of course, the control method shown in FIGS. 16 and 17 may be applied to a combined system that supplies electricity to an external load, or the control method shown in FIGS. 2 and 8 may be applied to a combined system that does not supply electricity to an external load. It is also possible to apply to.

  As mentioned above, although this invention was demonstrated based on embodiment, this invention is not limited to the said embodiment, You may add a change in the range which does not deviate from the meaning of this invention, and combines each embodiment. Also good.

  A cogeneration system is an internal combustion engine that uses fossil energy to generate power by turning a generator, and at the same time, supplies hot water from the cooling water of the internal combustion engine. Various types such as those that supply electric power and hot water from a fuel cell that uses gas as a fuel, and those that supply gas and fuel are used.

  In the present embodiment, the cogeneration system is configured by a cogeneration system, and generates and supplies electric energy and heat energy, respectively. However, the cogeneration system supplies power from a grid power source, and from a gas engine. Only the thermal energy generated during driving may be supplied.

  Moreover, the hot water and the cold water used in the present embodiment refer to a fluid (water) having a relative temperature relationship as a heat transfer target in each heat transfer system. Thus, the absolute temperature meaning may be different and the absolute temperature relationship for cold and hot water may be reversed in comparison with different heat transfer systems.

CG Cogeneration System GE Gas Engine GN Generator WJ Water Jacket ACS Thermal Heat Transfer System CSA Cold Heat Supply Unit HSA Thermal Supply Unit DHP Drive Heat Receiving Unit EHP Electric Heat Transfer System CSE Cold Heat Supply Unit HSE Thermal Supply Unit OR Outdoor Radiator IC Indoor Unit C control unit C1 selection control unit C2 operation control unit

Claims (8)

A combined supply system that supplies first energy consisting of electricity or power and supplies second energy that is thermal energy generated during driving;
A first heat transfer system that receives and drives the first energy supplied from the co-supply system, and transfers heat from the cold heat supply unit to the heat supply unit;
One or both driving heats selected from the second energy supplied from the co-supply system and the heat of the heat supply unit of the first heat transfer system are received and transferred from the cold supply unit to the heat supply unit A second heat transfer system,
Automatically selects one of at least two operation modes in which the first energy and the second energy supplied from the co-feed system are used in the first heat transfer system and the second heat transfer system. A selection control unit for optimal use of the first energy and the second energy;
An operation control unit that executes an operation according to the operation mode automatically selected by the selection control unit ,
The at least two operation modes include those corresponding to the cooling operation mode related to the cooling operation and those corresponding to the heating operation mode related to the heating operation, respectively.
Each of the cooling operation mode related to the cooling operation and the heating operation mode related to the heating operation includes a mode in which hot water flowing through the heat supply unit of the first heat transfer system is supplied as drive heat of the second heat transfer system. Feature combination system. The co-supply system is a system that generates electrical energy, supplies the generated electrical energy as the first energy, and supplies thermal energy generated along with the generation of the first energy as the second energy. ,
The operation mode is:
As a cooling operation mode related to cooling operation,
A cooling operation mode that drives the second heat transfer system using the second energy supplied from the co-feed system as drive heat, and uses cold water flowing in the cold heat supply unit of the second heat transfer system for cooling; and
The second energy supplied from the co-supply system is used as driving heat to drive the second heat transfer system, and the cold water flowing through the cold heat supply unit of the second heat transfer system is used for cooling, while being supplied from the co-feed system. The first heat transfer system is driven by the first energy, and the cold water flowing through the cold heat supply unit of the first heat transfer system is used for cooling, and the hot water flowing through the hot heat supply unit of the first heat transfer system At least a cooling operation mode for supplying the second heat transfer system as drive heat,
The selection control unit may be any one of a plurality of cooling operation modes based on an electric demand for electric energy generated in the co-supply system, a cooling capacity that can be output by the second heat transfer system, and a cooling demand. The combination system according to claim 1, wherein one is automatically selected. The co-supply system is a system that generates and supplies electric energy as the first energy, and generates thermal energy generated along with the generation of the first energy as the second energy,
The operation mode is:
As a heating operation mode related to heating operation,
A heating operation mode in which the second energy supplied from the combined supply system is directly used for heating;
The second energy supplied from the co-supply system is used as driving heat to drive the second heat transfer system, and the hot water flowing through the heat supply unit of the second heat transfer system to which the heat collected from the atmosphere is transferred The first heat transfer system is driven by the first energy supplied from the combined supply system while being used for heating, and the hot water flowing through the heat supply unit of the first heat transfer system is driven by the second heat transfer system. Heating operation mode to supply as heat,
The second energy supplied from the co-supply system is directly used for heating, while the first heat transfer system is driven by the first energy supplied from the co-supply system, and the heat collected from the atmosphere is transferred. A heating operation mode in which hot water flowing through the heat supply section of the first heat transfer system is used for heating,
The selection control unit includes a plurality of heating units based on an electrical demand for electrical energy generated in the combined supply system, an energy amount of the second energy supplied from the combined supply system, a heating demand, and an outside air temperature. The combined system according to claim 1 or 2, wherein any one of the operation modes is automatically selected. The operation mode is:
As a heating operation mode related to heating operation,
The second energy supplied from the co-supply system is used as driving heat to drive the second heat transfer system, and the hot water flowing through the heat supply unit of the second heat transfer system to which the heat collected from the atmosphere is transferred The combined system according to claim 3, further comprising a heating operation mode used for heating. The co-supply system is a system that generates and supplies electrical energy as the first energy and supplies thermal energy generated along with the generation of the first energy as the second energy,
The operation mode is:
As a cooling operation mode related to cooling operation,
The second energy supplied from the co-supply system is used as driving heat to drive the second heat transfer system, and the cold water flowing through the cold heat supply unit of the second heat transfer system is used for cooling, while being supplied from the co-feed system. The first heat transfer system is driven by the first energy, and the cold water flowing through the cold heat supply unit of the first heat transfer system is used for cooling, and the hot water flowing through the hot heat supply unit of the first heat transfer system Cooling operation mode for supplying the heat as driving heat of the second heat transfer system;
The second energy supplied from the co-supply system is used as driving heat to drive the second heat transfer system, and the cold water flowing through the cold heat supply unit of the second heat transfer system is used for cooling, while being supplied from the co-feed system. The first heat transfer system is driven by the first energy, and the cold water flowing through the cold heat supply unit of the first heat transfer system is used for cooling, and the hot water flowing through the hot heat supply unit of the first heat transfer system A cooling operation mode for radiating heat to the atmosphere,
The combined system according to claim 1, wherein the selection control unit automatically selects any one of a plurality of cooling operation modes based on an outside air temperature. The co-supply system is a system that generates and supplies electric energy as the first energy, and generates thermal energy generated along with the generation of the first energy as the second energy,
The operation mode is:
As a heating operation mode related to heating operation,
The second energy supplied from the co-supply system is used as driving heat to drive the second heat transfer system, and the hot water flowing through the heat supply unit of the second heat transfer system to which the heat collected from the atmosphere is transferred The first heat transfer system is driven by the first energy supplied from the combined supply system while being used for heating, and the hot water flowing through the heat supply unit of the first heat transfer system is driven by the second heat transfer system. Heating operation mode to supply as heat,
The second energy supplied from the co-supply system is directly used for heating, while the first heat transfer system is driven by the first energy supplied from the co-supply system, and the heat collected from the atmosphere is transferred. A heating operation mode in which hot water flowing through the heat supply section of the first heat transfer system is used for heating,
The combined system according to claim 1 or 5, wherein the selection control unit automatically selects any one of a plurality of heating operation modes based on an outside air temperature.   The selection control unit uses the second energy supplied from the combined supply system for supplying cold / hot water, and the first energy generated in the combined supply system is used for the supply of cold / hot water to the outside. The combined system according to any one of claims 1 to 6, wherein the operation mode is automatically selected and the operation load is automatically adjusted so as to meet the electric power demand.   The selection control unit automatically selects the operation mode and automatically adjusts the operation load so that the first energy supplied from the combined supply system is consumed in the combined system. To the combination system described in any one of 6.

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