JP2014228238A - Heat source system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat source system capable of stably operating an underground heat pump chiller and reducing energy consumption.SOLUTION: A heat source system 10 comprises: an underground heat exchanger 1 configured to implement heat exchange between soil and cooling water Wc underground 2; an underground-heat heat pump chiller 3 implementing heat exchange between the cooling water Wc and cold and hot water Wa; a first cold and hot water pump 11 feeding the cold and hot water Wa to the underground-heat heat pump chiller 3; a first inverter 11a frequency-controlling the first cold and hot water pump 11; a cooling water pump 12 circulating the cold water Wc between the underground heat exchanger 1 and the underground-heat heat pump chiller 3; a temperature sensor 41 measuring a water temperature of the cooling water Wc subjecting to the heat exchange with the cold and hot water Wa in the underground-heat heat pump chiller 3 and flowing into the underground heat exchanger 1; and a controller 100 determining a frequency of the first inverter 11a based on the water temperature of the cooling water Wc measured by the temperature sensor 41 during a heat storage operation of storing cold in the cold and hot water Wa.

Description

  The present invention relates to a heat source system.

  As background art of this technical field, for example, Patent Document 1 discloses that “the air conditioning system 10 includes a heat exchanger that uses geothermal heat, a cold / hot water pump 50 that circulates cold / hot water in the heat exchanger, and cold / hot water. An inverter 52 that changes the number of revolutions of the pump 50, an air conditioner 20 that cools or heats through cold / hot water circulated through the heat exchanger, a first detection means for calculating the indoor load of the air conditioner 20, The system COP is calculated by calculating the second detection means for calculating the cold / hot water load, the indoor load, the cold / hot water load, the first power consumption of the cold / hot water pump 50, and the second power consumption of the air conditioner 20. A control 62 that controls the chilled / hot water pump 50 with the frequency setting value of the simulator 62 that calculates and selects the chilled / hot water flow rate that maximizes the system COP and the chilled / hot water flow rate inverter 52 that maximizes the system COP. Includes a color 64. "Is described as (see Abstract).

JP 2011-247564 A

The air conditioning system (heat source system) using geothermal heat described in Patent Document 1 includes a heat pump type air conditioner (heat pump chiller), sends cooling water to the ground, and the cooling water and the ground in the ground. (Soil) is configured to exchange heat. Because the underground temperature is almost constant throughout the year, the heat pump system that uses geothermal heat (geothermal heat pump system) is more efficient than the heat pump system (air-cooled heat pump system) that exchanges heat with the outside air in summer and winter. It can be energy saving.
However, in the geothermal heat pump system, if the amount of heat exchange with the ground is too large, the temperature of the cooling water that exchanges heat with the ground rises, and there is a problem that the energy consumption is higher than that of the air-cooled heat pump system.

  Then, this invention makes it a subject to provide the heat-source system which can drive | operate stably the 1st heat pump chiller which heat-exchanges with the thermal refrigerant | coolant and working fluid which exchange heat with soil, and can reduce energy consumption.

  In order to solve the above-mentioned problems, the present invention is a heat source system comprising a ground heat exchanger that exchanges heat between soil and a heat medium, and a first heat pump chiller that exchanges heat between the heat medium and a working fluid. A control device is provided that determines the output of the first pump that feeds the working fluid to the first heat pump chiller based on the temperature of the heat medium flowing into the heat exchanger.

  ADVANTAGE OF THE INVENTION According to this invention, the heat source system which can drive | operate stably the 1st heat pump chiller which heat-exchanges with the heat | fever refrigerant | coolant and working fluid which exchange heat with soil, and can reduce energy consumption can be provided.

1 is a configuration diagram of a heat source system of Example 1. FIG. (A) is a figure which shows the state of a geothermal heat pump chiller in case a heat source system operate | moves as a cooling device, (b) is a figure which shows the state of the air cooling heat pump chiller in case a heat source system operate | moves as a cooling device. (A) is a figure which shows the state of a geothermal heat pump chiller in case a heat source system operate | moves as a heating apparatus, (b) is a figure which shows the state of the air cooling heat pump chiller in case a heat source system operate | moves as a heating apparatus. It is a block diagram of the heat source system of Example 2. It is an example of the table for cooling water pumps. It is an example of the table for 1st cold / hot water pumps. It is an example of the table for 2nd cold / hot water pumps. It is a flowchart (the 1) which shows the procedure in which a control apparatus produces each data table. It is a flowchart (the 2) which shows the procedure in which a control apparatus produces each data table. It is a block diagram of the heat source system of Example 3. It is a block diagram of the heat source system of Example 4.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings as appropriate.

FIG. 1 is a configuration diagram of a heat source system according to the first embodiment.
As shown in FIG. 1, the heat source system 10 includes two heat pump chillers, a first heat pump chiller (ground heat pump chiller 3) and a second heat pump chiller (air-cooled heat pump chiller 4).
A geothermal heat exchanger 1 is connected to the geothermal heat pump chiller 3 via an outgoing pipe 30a and a return pipe 30b, and cooling water (cooling water Wc) is connected between the geothermal heat pump chiller 3 and the geothermal heat exchanger 1. ) Circulates as a heat medium. That is, the cooling water Wc is sent from the geothermal heat pump chiller 3 to the underground heat exchanger 1 through the outgoing pipe 30a, and the cooling water Wc is supplied from the underground heat exchanger 1 through the return pipe 30b to the underground heat pump. Water is sent to the chiller 3.
In the underground heat exchanger 1, a pipe through which the cooling water Wc sent from the underground heat pump chiller 3 flows is piped in the underground 2, and the cooling water Wc flowing through the pipe is in the underground 2 and heats the soil. Configured to replace. The cooling water Wc functions as a heat medium that conveys the heat of the soil to the underground heat pump chiller 3.

  Note that a second pump (cooling) that circulates the cooling water Wc between the geothermal heat exchanger 1 and the geothermal heat pump chiller 3 by supplying the cooling water Wc to the geothermal heat exchanger 1 is provided in the outgoing pipe 30a. A water pump 12) is provided. Further, the outgoing pipe 30a is provided with temperature measuring means (temperature sensor 41) for measuring the water temperature of the cooling water Wc fed from the geothermal heat pump chiller 3 to the geothermal heat exchanger 1, and the measured value of the temperature sensor 41 is provided. Is transmitted to the control device 100. And the control apparatus 100 is comprised so that calculation of the water temperature of the cooling water Wc sent to the underground heat exchanger 1 based on the measurement signal transmitted from the temperature sensor 41 is possible.

The geothermal heat pump chiller 3 is connected to the return header 7 via the first water supply pipe 51a, and is connected to the forward header 8 via the first drain pipe 51b. Then, the working fluid (cold hot water Wa) is fed from the return header 7 to the geothermal heat pump chiller 3 via the first water supply pipe 51a, and underground to the forward header 8 via the first drain pipe 51b. Cold / hot water Wa is sent from the heat heat pump chiller 3.
Therefore, the first water supply pipe 51a is provided with a first pump (first cold / hot water pump 11) that feeds the cold / hot water Wa from the return header 7 to the underground heat pump chiller 3. The first cold / hot water pump 11 includes an inverter (first inverter 11a), and the frequency of the first cold / hot water pump 11 is controlled by the first inverter 11a. That is, it is configured such that the discharge amount (output) of the cold / hot water Wa from the first cold / hot water pump 11 is changed by changing the frequency set in the first inverter 11a by the control device 100.

The control device 100 includes a communication unit 100a, a calculation unit 100b, a storage unit 100c, and an interface unit 100d. The control device 100 controls the heat source system 10 by executing a predetermined program stored in the storage unit 100c by the calculation unit 100b. Moreover, the control apparatus 100 receives the measurement signal transmitted from the temperature sensor 41 by the communication part 100a, and calculates the water temperature of the cold / hot water Wa by the calculating part 100b based on the received measurement signal.
Further, the control device 100 determines the frequency of the first inverter 11a by the calculation unit 100b as described later, and controls the interface unit 100d to control the first inverter 11a so that the first cold / hot water pump 11 is driven at the determined frequency. Send a signal.

The air-cooled heat pump chiller 4 is connected to the return header 7 via the second water supply pipe 52a, and is connected to the forward header 8 via the second drain pipe 52b. And the cold / hot water Wa is sent from the return header 7 to the air-cooled heat pump chiller 4 via the second water supply pipe 52a, and the cold / hot water Wa is sent from the air-cooled heat pump chiller 4 to the forward header 8 via the second drain pipe 52b. Water is sent.
For this reason, the second water supply pipe 52a is provided with a third pump (second cold / hot water pump 13) for feeding the cold / hot water Wa from the return header 7 to the air-cooled heat pump chiller 4.

The return header 7 and the forward header 8 are connected to the air conditioners 5 and 6 arranged in parallel via the pipe 60, and the hot and cold water Wa is supplied to the air conditioners 5 and 6 from the forward header 8 via the pipe 60. Water is sent. For this reason, a fourth pump (cold water supply pump 14) that supplies cold / hot water Wa to the air conditioners 5, 6 is provided between the forward header 8 and the air conditioners 5, 6.
The cold / warm water Wa sent from the forward header 8 exchanges heat with the outside air by the air conditioners 5 and 6 to adjust the temperature of the outside air around the air conditioners 5 and 6 (outside air temperature). That is, the facilities and the like are air-conditioned (cooling or heating) by the air conditioners 5 and 6.
And the cold / hot water Wa heat-exchanged with external air in the air conditioners 5 and 6 distribute | circulates the piping 60, and is sent to the return header 7. FIG.
The return header 7 and the forward header 8 are connected by a bypass pipe 60a, and the bypass pipe 60a is provided with a flow rate adjusting valve 60b for adjusting the flow rate of the cold / hot water Wa flowing through the bypass pipe 60a.

  The pipe 60 connecting the return header 7 and the air conditioner 5 is provided with a flow rate adjusting valve 32 for adjusting the flow rate of the cold / hot water Wa, and the pipe 60 connecting the return header 7 and the air conditioner 6 has the flow rate of the cold / hot water Wa. A flow rate adjusting valve 33 for adjusting the flow rate is provided.

The heat source system 10 of Example 1 is configured as shown in FIG. 1, and the underground heat pump chiller 3 and the air-cooled heat pump chiller 4 function as a cold heat source or a heat source, respectively.
When the heat source system 10 operates as a cooling device, the underground heat pump chiller 3 and the air-cooled heat pump chiller 4 function as a cold heat source, and the cold / warm water Wa sent to the air conditioners 5 and 6 cools the surrounding outside air. In this case, ambient ambient air becomes a cooling target of the cold / hot water Wa.
On the other hand, when the heat source system 10 operates as a heating device, the underground heat pump chiller 3 and the air-cooled heat pump chiller 4 function as heat sources, and the cold / warm water Wa fed to the air conditioners 5 and 6 heats the surrounding outside air. To do. In this case, ambient ambient air becomes a heating target of the cold / hot water Wa.

<< When the heat source system 10 operates as a cooling device >>
(A) of FIG. 2 is a figure which shows the state of a geothermal heat pump chiller in case a heat source system operate | moves as a cooling device, (b) shows the state of the air cooling heat pump chiller in case a heat source system operate | moves as a cooling device. FIG.

When the heat source system 10 (see FIG. 1) operates as a cooling device, that is, when the heat source system 10 performs a cooling operation, as shown in FIG. 2 (a), the compressor is disposed inside the underground heat pump chiller 3. The high-temperature and high-pressure refrigerant (first refrigerant Co1) compressed by 3a is introduced into the condenser 3b. Then, the first refrigerant Co1 is cooled and condensed by the cooling water Wc having a relatively low water temperature sent from the underground heat exchanger 1 by the condenser 3b, depressurized by the expansion valve 3d, and then introduced into the evaporator 3c. Is done. In the evaporator 3c, the first refrigerant Co1 is vaporized by exchanging heat with the cold / warm water Wa sent from the return header 7, and at this time, the cold / warm water Wa is cooled by taking heat of vaporization from the cold / warm water Wa. The vaporized first refrigerant Co1 is compressed by the compressor 3a.
As described above, when the heat source system 10 is cooled, the first refrigerant Co1 circulates in the order of the compressor 3a, the condenser 3b, the expansion valve 3d, and the evaporator 3c to cool the cold / hot water Wa. The cold / hot water Wa stores cold energy. That is, the cooling operation of the heat source system 10 is a heat storage operation in which cold heat is stored in the cold / hot water Wa (working fluid).

The cold / warm water Wa cooled by the evaporator 3c of the geothermal heat pump chiller 3 is sent to the air conditioners 5 and 6 (see FIG. 1) via the forward header 8.
Further, the cooling water Wc whose temperature has risen due to heat exchange in the condenser 3b is sent to the underground heat exchanger 1 and cooled in the relatively low temperature underground 2, and then again in the underground heat pump chiller 3. Water is sent to the condenser 3b.

  When the heat source system 10 (see FIG. 1) performs a cooling operation, as shown in FIG. 2 (b), a high-temperature and high-pressure refrigerant (second refrigerant) compressed by the compressor 4a is inside the air-cooled heat pump chiller 4. Co2) is introduced into the condenser 4b. Then, the second refrigerant Co2 is cooled and condensed by a relatively low temperature outside air in the condenser 4b, and after being decompressed by the expansion valve 4d, is introduced into the evaporator 4c. In the evaporator 4c, the second refrigerant Co2 is vaporized by heat exchange with the cold / warm water Wa fed from the return header 7, and at this time, the cold / warm water Wa is cooled by taking the heat of vaporization from the cold / warm water Wa. The vaporized second refrigerant Co2 is compressed by the compressor 4a. In this way, the second refrigerant Co2 circulates in the order of the compressor 4a, the condenser 4b, the expansion valve 4d, and the evaporator 4c to cool the cold / hot water Wa.

<< When heat source system 10 operates as a heating device >>
(A) of Drawing 3 is a figure showing the state of a geothermal heat pump chiller when a heat source system operates as a heating device, and (b) shows the state of an air cooling heat pump chiller when a heat source system operates as a heating device. FIG.

When the heat source system 10 (see FIG. 1) operates as a heating device, that is, when the heat source system 10 performs a heating operation, as shown in FIG. 3 (a), a compressor is installed inside the underground heat pump chiller 3. The high-temperature and high-pressure first refrigerant Co1 compressed by 3a is introduced into the condenser 3b. Then, the first refrigerant Co1 is cooled and condensed by exchanging heat with the cold / hot water Wa fed from the return header 7 by the condenser 3b, and after being decompressed by the expansion valve 3d, is introduced into the evaporator 3c. The first refrigerant Co1 gives the heat of condensation to the cold / hot water Wa in the condenser 3b to heat the cold / hot water Wa. Further, the first refrigerant Co1 is vaporized by exchanging heat with the cooling water Wc sent from the underground heat exchanger 1 in the evaporator 3c, and at this time, the first refrigerant Co1 takes the heat of vaporization from the cooling water Wc and cools it. Water Wc is cooled. The vaporized first refrigerant Co1 is compressed by the compressor 3a.
As described above, when the heat source system 10 is heated, the first refrigerant Co1 circulates in the order of the compressor 3a, the condenser 3b, the expansion valve 3d, and the evaporator 3c to heat the cold / hot water Wa. And warm heat is stored in the cold / hot water Wa. That is, the heating operation of the heat source system 10 is a heat storage operation in which heat is stored in the cold / hot water Wa.

Cold / warm water Wa heated by the condenser 3b of the underground heat pump chiller 3 is sent to the air conditioners 5 and 6 (see FIG. 1) via the forward header 8.
In addition, the cooling water Wc whose temperature has decreased due to heat exchange in the condenser 3b is sent to the underground heat exchanger 1 and heated in the relatively high temperature underground 2, and then the evaporation of the underground heat pump chiller 3 is evaporated. Water is sent to the vessel 3c.

  When the heat source system 10 (see FIG. 1) performs a heating operation, as shown in FIG. 3B, the high-temperature and high-pressure second refrigerant Co2 compressed by the compressor 4a is contained inside the air-cooled heat pump chiller 4. It is introduced into the condenser 4b. Then, the second refrigerant Co2 is cooled and condensed by exchanging heat with the cold / hot water Wa fed from the return header 7 by the condenser 4b, and after being decompressed by the expansion valve 4d, is introduced into the evaporator 4c. The second refrigerant Co2 heats the cold / warm water Wa by applying condensation heat to the cold / warm water Wa in the condenser 4b. The second refrigerant Co2 is vaporized by exchanging heat with the outside air in the evaporator 4c and compressed by the compressor 4a. In this way, the second refrigerant Co2 circulates in the order of the compressor 4a, the condenser 4b, the expansion valve 4d, and the evaporator 4c to heat the cold / hot water Wa.

When the heat source system 10 configured as shown in FIGS. 1 to 3 is air-cooled, when the cooling load in the air conditioners 5 and 6 is increased, the water temperature of the cold / warm water Wa returning to the return header 7 is increased. Hot hot / cold water Wa is fed to the heat heat pump chiller 3. Then, the amount of heat received by the first refrigerant Co1 from the cold / warm water Wa is increased by the evaporator 3c, and the amount of heat received by the cooling water Wc from the first refrigerant Co1 is increased by the condenser 3b, and the cooling water sent to the underground heat exchanger 1 is cooled. The water temperature of the water Wc increases.
When the water temperature of the cooling water Wc sent to the underground heat exchanger 1 becomes high, heat exchange in the underground 2 becomes insufficient and the cooling water Wc is not sufficiently cooled. Then, the first refrigerant Co1 is not sufficiently condensed by the condenser 3b of the underground heat pump chiller 3, and the pressure of the first refrigerant Co1 in the condenser 3b is increased. As a result, the underground heat pump chiller 3 may stop.

Therefore, the control device 100 included in the heat source system 10 of the first embodiment is supplied with water from the geothermal heat pump chiller 3 to the underground heat exchanger 1 based on a measurement signal transmitted from the temperature sensor 41 to the communication unit 100a. The water temperature of the cooling water Wc is calculated by the calculation unit 100b.
When the temperature of the cooling water Wc fed from the underground heat pump chiller 3 to the underground heat exchanger 1 rises and becomes equal to or higher than a predetermined temperature, the control device 100 The frequency set to the 1st inverter 11a of the 1st cold / hot water pump 11 is made lower than when the water temperature of Wc is lower than predetermined temperature, and the discharge amount of the cold / hot water Wa from the 1st cold / hot water pump 11 is reduced.
That is, the control device 100 determines the frequency of the first inverter 11a based on the measurement value of the temperature sensor 41. More specifically, when the measured value of the temperature sensor 41 is equal to or higher than a predetermined temperature that is set in advance, the control device 100 includes the first inverter than when the measured value of the temperature sensor 41 is lower than the predetermined temperature. The frequency of 11a is lowered.

  For example, when the measured value of the temperature sensor 41 is lower than a predetermined temperature, the control device 100 sets the frequency of the first inverter 11a as the rated frequency, and when the measured value of the temperature sensor 41 becomes equal to or higher than the predetermined temperature, The frequency of the inverter 11a is set lower than the rated frequency.

  Thereby, the flow rate per unit time of the cold / warm water Wa fed to the geothermal heat pump chiller 3 by the first cold / hot water pump 11 is reduced. And the amount of exchange heat of the cold / hot water Wa and the 1st refrigerant | coolant Co1 in the evaporator 3c reduces, and the temperature of the 1st refrigerant | coolant Co1 which circulates through the underground heat pump chiller 3 falls. As a result, the amount of heat exchanged between the first refrigerant Co1 and the cooling water Wc in the condenser 3b is reduced, the water temperature of the cooling water Wc sent to the underground heat exchanger 1 is lowered, and the cooling water Wc is exchanged with the ground. The vessel 1 is sufficiently cooled in the ground 2.

  In addition, the water temperature (predetermined temperature) of the cooling water Wc that serves as a threshold for lowering the frequency set by the control device 100 in the first inverter 11 a may be a water temperature set in advance as a characteristic value of the heat source system 10. And the control apparatus 100 sets the rated frequency to the 1st inverter 11a, and when the 1st cold / hot water pump 11 is driven, the water temperature of the cooling water Wc sent to the underground heat exchanger 1 is predetermined. What is necessary is just to make the frequency set to the 1st inverter 11a lower than a rated frequency when it becomes more than temperature.

As a result, the temperature of the cooling water Wc sent to the condenser 3b can be kept low, and the condensation of the first refrigerant Co1 in the condenser 3b is promoted. Therefore, the pressure increase of the first refrigerant Co1 in the condenser 3b is suppressed, and the stop of the underground heat pump chiller 3 is prevented. And the underground heat pump chiller 3 is operated stably.
Moreover, when the water temperature of the cooling water Wc sent to the underground heat exchanger 1 becomes equal to or higher than a predetermined temperature, the frequency set in the first inverter 11a is lowered, so the output of the first cold / hot water pump 11 is lowered. And the power consumption (energy consumption) in the 1st cold / hot water pump 11 reduces.

For example, the water temperature of the cooling water Wc sent to the underground heat exchanger 1 (water temperature of the cooling water Wc flowing through the forward pipe 30a) and the frequency of the first inverter 11a that drives the first cold / hot water pump 11 The map data indicating the relationship may be set in advance by experimental measurement or the like, and the map data may be stored in the storage unit 100c of the control device 100. The calculation unit 100b of the control device 100 calculates the water temperature of the cooling water Wc flowing through the forward piping 30a based on the measurement signal transmitted from the temperature sensor 41 to the communication unit 100a, and further calculates the water temperature of the calculated cooling water Wc. Based on this map data, the frequency of the first inverter 11a can be determined.
With such a configuration, the control device 100 can drive the first cold / hot water pump 11 based on the water temperature of the cooling water Wc fed from the underground heat pump chiller 3 to the underground heat exchanger 1. The intermediate heat pump chiller 3 can be operated stably.

On the other hand, when the heat source system 10 shown in FIG. 1 is operated for heating, the water temperature of the cooling water Wc fed from the geothermal heat pump chiller 3 to the underground heat exchanger 1 is lower than a predetermined temperature set in advance. When it becomes, the control apparatus 100 reduces the frequency set to the 1st inverter 11a of the 1st cold / hot water pump 11, and reduces the discharge amount of the cold / hot water Wa from the 1st cold / hot water pump 11. FIG.
With this configuration, the cooling water Wc is sufficiently heated in the underground heat exchanger 1, and the first refrigerant Co1 is suitably evaporated in the evaporator 3c. And the underground heat pump chiller 3 is operated stably.

  FIG. 4 is a configuration diagram of the heat source system according to the second embodiment. In addition, in the heat source system 10a shown in FIG. 4, the same code | symbol is attached | subjected to the same component as the heat source system 10 of Example 1 shown in FIG. 1, and the structure different from the heat source system 10 of Example 1 is demonstrated.

The cooling water pump 12 provided in the heat source system 10a of the second embodiment includes an inverter (second inverter 12a), and the cooling water pump 12 is frequency-controlled by the second inverter 12a. Further, in the heat source system 10a of the second embodiment, water is sent from the underground heat exchanger 1 to the underground heat pump chiller 3 to the return pipe 30b connecting the underground heat exchanger 1 and the underground heat pump chiller 3. A temperature sensor 42 for measuring the water temperature of the cooling water Wc and a flow rate sensor 47 for measuring the flow rate of the cooling water Wc flowing through the return pipe 30b are provided. The measurement signal indicating the measurement value of the temperature sensor 42 is transmitted to the communication unit 100a of the control device 100, and the calculation unit 100b of the control device 100 is transmitted from the underground heat exchanger 1 to the underground by the measurement signal transmitted from the temperature sensor 42. It is comprised so that calculation of the water temperature of the cooling water Wc sent to the thermal heat pump chiller 3 is possible. Similarly, the measurement signal indicating the measurement value of the flow sensor 47 is transmitted to the communication unit 100 a of the control device 100, and the calculation unit 100 b of the control device 100 uses the measurement signal transmitted from the flow sensor 47 to perform the underground heat exchanger 1. The flow rate of the cooling water Wc fed to the geothermal heat pump chiller 3 can be calculated.
Further, the cooling water pump 12 is configured such that a frequency for driving the cooling water pump 12 is set by a control signal transmitted from the interface unit 100d of the control device 100 to the second inverter 12a.

Furthermore, the 2nd cold / hot water pump 13 arrange | positioned by the 2nd water supply pipe | tube 52a is provided with the inverter (3rd inverter 13a), and the 2nd cold / hot water pump 13 is frequency-controlled by the 3rd inverter 13a. That is, it is configured that the discharge amount (output) of the cold / hot water Wa by the second cold / hot water pump 13 is changed by changing the frequency set in the third inverter 13a by the control device 100.
For example, the 2nd cold / hot water pump 13 is comprised so that the frequency which drives the said 2nd cold / hot water pump 13 with the control signal transmitted to the 3rd inverter 13a from the interface part 100d of the control apparatus 100 may be set.

A pipe 60 connecting the forward header 8 and the air conditioners 5 and 6 is provided with a temperature sensor 43 for measuring the temperature of the cold / hot water Wa and a flow sensor 48 for measuring the flow rate of the cold / hot water Wa. A pipe 60 connecting the machines 5 and 6 is provided with a temperature sensor 44 for measuring the temperature of the cold / hot water Wa.
Based on the measurement signal transmitted from the temperature sensor 43 to the communication unit 100a, the calculation unit 100b of the control device 100 can calculate the water temperature of the cold / warm water Wa fed from the forward header 8 to the air conditioners 5 and 6. Based on the measurement signal transmitted from the temperature sensor 44 to the communication unit 100a, the water temperature of the cold / warm water Wa sent from the air conditioners 5 and 6 to the return header 7 can be calculated. Further, the calculation unit 100b of the control device 100 can calculate the flow rate of the cold / warm water Wa fed from the forward header 8 to the air conditioners 5 and 6 based on the measurement signal transmitted from the flow rate sensor 48 to the communication unit 100a. Configured.

  Furthermore, the heat source system 10a according to the second embodiment includes an outside air temperature sensor 45 that measures the outside air temperature. The outside air temperature sensor 45 is configured to be able to transmit a measurement signal indicating a measured value to the communication unit 100a of the control device 100, and the calculation unit 100b of the control device 100 is based on the measurement signal transmitted from the outside air temperature sensor 45. Can be calculated.

  The heat source system 10a of the second embodiment is configured in the same way as the heat source system 10 of the first embodiment shown in FIG. 1 except for the configuration described above.

When the heat source system 10a is in a cooling operation, the control device 100 provided in the heat source system 10a according to the second embodiment illustrated in FIG. 4 is based on the cooling load in the air conditioners 5 and 6 and the outside air temperature. The discharge amounts of the first cold / hot water pump 11 and the second cold / hot water pump 13 are determined. That is, the control device 100 determines the frequency of each inverter (the first inverter 11a, the second inverter 12a, and the third inverter 13a) based on the cooling load (cooling load factor) in the air conditioners 5 and 6 and the outside air temperature. Are configured to set each.
Therefore, a map-format data table showing the relationship between the outside air temperature, the cooling load (cooling load factor) in the air conditioners 5 and 6, and the frequency of each inverter 11a, 12a, 13a is stored in the storage unit 100c of the control device 100. A stored configuration is preferred.

5 is an example of a cooling water pump table, FIG. 6 is an example of a first cold / hot water pump table, and FIG. 7 is an example of a second cold / hot water pump table.
The calculation unit 100b included in the control device 100 according to the second embodiment illustrated in FIG. 4 is cold / hot water that is sent from the forward header 8 to the air conditioners 5 and 6 based on a measurement signal transmitted from the temperature sensor 43 to the communication unit 100a. Wa temperature (incoming temperature T1) is calculated. In addition, the calculation unit 100b calculates the temperature (exit temperature T2) of the cold / warm water Wa sent from the air conditioners 5 and 6 to the return header 7 based on the measurement signal transmitted from the temperature sensor 44 to the communication unit 100a. To do. Furthermore, the calculation unit 100b calculates the flow rate (water supply flow rate V1) of the cold / warm water Wa supplied from the forward header 8 to the air conditioners 5 and 6 based on the measurement signal transmitted from the flow rate sensor 48 to the communication unit 100a.
And the calculating part 100b calculates the cooling load in the air conditioners 5 and 6 from the calculated inlet side temperature T1, outlet side temperature T2, and water supply flow volume V1.
For example, the arithmetic unit 100b sets a value obtained by multiplying the difference (T1-T2) between the inlet side temperature T1 and the outlet side temperature T2 by the water supply flow rate V1 per unit time as the cooling load in the air conditioners 5 and 6.
In this case, the cooling load of the heat source system 10 is measured including the temperature sensor 43 that measures the inlet side temperature T1, the temperature sensor 44 that measures the outlet side temperature T2, and the flow rate sensor 48 that measures the water supply flow rate V1. A cooling load measuring means is configured.

Further, the calculation unit 100b calculates a value obtained by dividing the calculated cooling load by the total cooling capacity of the underground heat pump chiller 3 and the air cooling heat pump chiller 4 as a “cooling load factor CW”.
In addition, the calculation unit 100b calculates the outside air temperature Tout based on the measurement signal transmitted from the outside air temperature sensor 45. And the calculating part 100b sets the frequency of each inverter 11a, 12a, 13a based on the calculated outside temperature Tout and the calculated cooling load factor CW, respectively. That is, the control device 100 included in the heat source system 10a of the second embodiment is based on the measured value of the outside air temperature sensor 45 and the measured value of the cooling load measuring means (the temperature sensor 43, the temperature sensor 44, and the flow rate sensor 48). The frequency of each inverter 11a, 12a, 13a is set.

Further, in the storage unit 100c (see FIG. 4) of the control device 100, the relationship among the outside air temperature Tout, the cooling load factor CW, and the frequency set in the second inverter 12a of the cooling water pump 12 is shown in FIG. It is preferable that the second data table shown (hereinafter, the cooling water pump table 121) is stored.
And the calculating part 100b refers to the table 121 for cooling water pumps memorize | stored in the memory | storage part 100c based on the calculated outside temperature Tout and the calculated cooling load factor CW. In the cooling water pump table 121, the calculation unit 100b determines the frequency indicated by the intersection of the outside air temperature Tout and the cooling load factor CW as the frequency set in the second inverter 12a.
As shown in FIG. 5, the cooling water pump table 121 minimizes power consumption when the heat source system 10a (see FIG. 4) is in cooling operation for each combination of the outside air temperature Tout and the cooling load factor CW. 2 is a data table in which the frequency of the inverter 12a is determined.

That is, the control device 100 included in the heat source system 10a of the second embodiment is based on the measured value of the outside air temperature sensor 45 and the measured value of the cooling load measuring means (the temperature sensor 43, the temperature sensor 44, and the flow rate sensor 48). With reference to the cooling water pump table 121, the frequency of the second inverter 12a is determined.
The calculation unit 100b calculates the frequency of the second inverter 12a with a predetermined function based on the calculated outside air temperature Tout and the calculated cooling load factor CW without using the cooling water pump table 121. There may be.

Further, in the storage unit 100c (see FIG. 4) of the control device 100, the outside air temperature Tout, the cooling load factor CW, and the frequency set in the first inverter 11a of the first cold / hot water pump 11 shown in FIG. It is preferable that a first data table (hereinafter referred to as a first cold / hot water pump table 111) indicating the relationship is stored.
And the calculating part 100b refers to the table 111 for 1st cold / hot water pumps memorize | stored in the memory | storage part 100c based on the calculated outside temperature Tout and the calculated cooling load factor CW. In the first cold / hot water pump table 111, the calculation unit 100b determines the frequency indicated by the intersection of the outside air temperature Tout and the cooling load factor CW as the frequency set in the first inverter 11a.
As shown in FIG. 6, the first cold / hot water pump table 111 minimizes power consumption when the heat source system 10a (see FIG. 4) is in cooling operation for each combination of the outside air temperature Tout and the cooling load factor CW. This is a data table in which the frequency of the first inverter 11a is determined.

That is, the control device 100 included in the heat source system 10a of the second embodiment is based on the measured value of the outside air temperature sensor 45 and the measured value of the cooling load measuring means (the temperature sensor 43, the temperature sensor 44, and the flow rate sensor 48). The frequency of the 1st inverter 11a is determined with reference to the table 111 for 1st cold / hot water pumps.
Note that the calculation unit 100b calculates the frequency of the first inverter 11a with a predetermined function based on the calculated outside air temperature Tout and the calculated cooling load factor CW without using the first chilled water pump table 111. It may be a configuration.

Similarly, in the storage unit 100c (see FIG. 4) of the control device 100, the outside air temperature Tout, the cooling load factor CW, and the third inverter 13a of the second cold / hot water pump 13 shown in FIG. It is preferable to store a third data table (hereinafter referred to as a second cold / hot water pump table 131) indicating the frequency relationship.
And the calculating part 100b refers to the 2nd cold / hot water pump table 131 memorize | stored in the memory | storage part 100c based on the calculated outside air temperature Tout and the calculated cooling load factor CW. The calculating part 100b determines in the 2nd cold / hot water pump table 131 the frequency which the intersection of the outside temperature Tout and the cooling load factor CW shows to the frequency set to the 3rd inverter 13a.
As shown in FIG. 7, the second cold / hot water pump table 131 minimizes power consumption when the heat source system 10a (see FIG. 4) is in cooling operation for each combination of the outside air temperature Tout and the cooling load factor CW. This is a data table in which the frequency of the third inverter 13a is determined.

That is, the control device 100 included in the heat source system 10a of the second embodiment is based on the measured value of the outside air temperature sensor 45 and the measured value of the cooling load measuring means (the temperature sensor 43, the temperature sensor 44, and the flow rate sensor 48). The frequency of the 3rd inverter 13a is determined with reference to the table 131 for 2nd cold / hot water pumps.
Note that the calculation unit 100b calculates the frequency of the third inverter 13a with a predetermined function based on the calculated outside air temperature Tout and the calculated cooling load factor CW without using the second chilled water pump table 131. It may be a configuration.

  Then, the calculation unit 100b sets the frequencies of the inverters 11a, 12a, and 13a to the determined frequencies, and the control device 100 sets the cooling water pump 12, the first cold / hot water pump 11, and the second cold / hot at the set frequencies. The water pump 13 is operated.

  Further, the calculation unit 100b of the control device 100 included in the heat source system 10a according to the second embodiment illustrated in FIG. 4 includes the inverters 11a, 12a, and 13a for minimizing power consumption when the heat source system 10a is in the cooling operation. Is provided with a simulation function for simulating a change in the frequency of the air in response to a change in the outside air temperature Tout and a change in the cooling load factor CW. The cooling water pump table 121 (see FIG. 5) and the first cold / hot water pump table 111 are provided. (Refer FIG. 6) and the 2nd cold / hot water pump table 131 (refer FIG. 7) may be comprised.

  8 and 9 are flowcharts showing a procedure for the control device to create each data table. With reference to FIGS. 8 and 9, the procedure by which the control apparatus 100 creates each data table will be described (see FIGS. 4 to 7 as appropriate).

  As shown in FIGS. 8 and 9, the control device 100 (calculation unit 100b) evaluates the frequency of each inverter 11a, 12a, 13a for each combination of the outside air temperature Tout and the cooling load factor CW. Then, for each combination of the outside air temperature Tout and the cooling load factor CW, the control device 100 determines the frequency of each of the inverters 11a, 12a, and 13a that minimizes the power consumption when the heat source system 10a is cooled. Each data table (the 1st cold / hot water pump table 111, the cooling water pump table 121, the 2nd cold / hot water pump table 131) which shows the relationship between temperature Tout, the cooling load factor CW, and the frequency of each inverter 11a, 12a, 13a. ). And the control apparatus 100 memorize | stores each produced data table in the memory | storage part 100c (refer FIG. 4).

When the control device 100 starts a procedure for creating each data table (the first cold / hot water pump table 111, the cooling water pump table 121, the second cold / hot water pump table 131), the outside air temperature Tout and the cooling load factor CW Is set (FIG. 8: step S1). For example, the control device 100 sets the lowest value of the range of the outside air temperature Tout that sets the frequency of each inverter 11a, 12a, 13a in each data table. In the example illustrated in FIGS. 5 to 7, the control device 100 sets the outside air temperature Tout to “10 ° C.”.
Moreover, the control apparatus 100 sets the minimum value of the range of the cooling load factor CW which sets the frequency of each inverter 11a, 12a, 13a in each data table. In the example illustrated in FIGS. 5 to 7, the control device 100 sets the cooling load factor CW to “5%”.

  And the control apparatus 100 sets the frequency of each inverter 11a, 12a, 13a to the maximum frequency (for example, "50Hz") (FIG. 8: step S2). Note that the maximum frequency set by the control device 100 at this time is not limited to “50 Hz” which is the frequency of the AC power supply, for example. For example, in an area where the frequency of the AC power supply is “60 Hz”, the control device 100 sets the frequency of each of the inverters 11a, 12a, and 13a to “60 Hz”.

  Next, the control device 100 calculates the flow rate of the cold / hot water Wa in the geothermal heat pump chiller 3 and the power consumption of the first cold / hot water pump 11 (FIG. 8: step S3), The power consumption of the second cold / hot water pump 13 is calculated (FIG. 8: Step S4). Further, the control device 100 calculates the flow rate of the cooling water Wc in the geothermal heat pump chiller 3 and the power consumption of the cooling water pump 12 (FIG. 8: step S5).

In step S3 of FIG. 8, the control device 100 sets the discharge amount of the cold / warm water Wa discharged from the first cold / hot water pump 11 when the first cold / hot water pump 11 is driven at the frequency set in the first inverter 11a. The flow rate of the cold / hot water Wa in the geothermal heat pump chiller 3 is calculated, and the power consumption when the first cold / hot water pump 11 is driven at the frequency set in the first inverter 11a is calculated.
Similarly, in step S4 of FIG. 8, the control device 100 controls the amount of cold / hot water Wa discharged from the second cold / hot water pump 13 when the second cold / hot water pump 13 is driven at the frequency set in the third inverter 13a. Let the discharge amount be the flow rate of the cold / hot water Wa in the air-cooled heat pump chiller 4, and calculate the power consumption when the second cold / hot water pump 13 is driven at the frequency set in the third inverter 13a.
Further, in step S5 of FIG. 8, the control device 100 sets the discharge amount of the cooling water Wc discharged from the cooling water pump 12 when the cooling water pump 12 is driven at the frequency set in the second inverter 12a. The flow rate of the cooling water Wc in the thermal heat pump chiller 3 is used, and the power consumption when the cooling water pump 12 is driven at the frequency set in the second inverter 12a is calculated.

And the control apparatus 100 calculates each cooling load factor of the geothermal heat pump chiller 3 and the air cooling heat pump chiller 4 (FIG. 8: step S6).
In step S6 of FIG. 8, the control device 100, based on the ratio of the flow rate of the cold / hot water Wa in the geothermal heat pump chiller 3 and the flow rate of the cold / warm water Wa in the air-cooled heat pump chiller 4, and the set cooling load factor CW, The cooling load factor of the underground heat pump chiller 3 and the air cooling heat pump chiller 4 is calculated. For example, when the set cooling load factor CW is “5%”, the ratio of the flow rate of the cold / hot water Wa in the geothermal heat pump chiller 3 to the flow rate of the cold / hot water Wa in the air-cooled heat pump chiller 4 is “1: 1” The cooling load factors of the geothermal heat pump chiller 3 and the air-cooled heat pump chiller 4 are each “2.5%”.

  Next, the control device 100 calculates the amount of heat released to the cooling water Wc in the underground heat pump chiller 3 and the power consumption of the underground heat pump chiller 3 (FIG. 8: Step S7).

In step S7 of FIG. 8, the control device 100 receives the flow rate and the water temperature of the cooling water Wc and the cold / hot water Wa in the geothermal heat pump chiller 3, and the power consumption characteristics of the geothermal heat pump chiller 3 set in advance, Based on the heat transfer characteristics of the underground heat exchanger 1, the amount of heat released to the cooling water Wc and the power consumption of the underground heat pump chiller 3 are calculated.
The control device 100 controls the cooling water Wc in the condenser 3b so that the exchange heat amount of the first refrigerant Co1 and the cooling water Wc in the condenser 3b is equal to the exchange heat amount of the cooling water Wc in the underground heat exchanger 1 and the soil. Set the water temperature. The amount of heat exchanged between the first refrigerant Co1 and the cooling water Wc in the condenser 3b and the amount of heat exchanged between the cooling water Wc and the soil in the underground heat exchanger 1 change according to changes in the water temperature of the cooling water Wc in the condenser 3b. Therefore, the control device 100 changes the temperature of the cooling water Wc in the condenser 3b in a pseudo manner, and exchanges heat between the first refrigerant Co1 and the cooling water Wc in the condenser 3b and cooling in the underground heat exchanger 1. Simulate the exchange heat quantity of water Wc and soil. And the control apparatus 100 is the water temperature (condenser 3b) of the cooling water Wc from which the exchange heat amount of the 1st refrigerant | coolant Co1 and the cooling water Wc in the condenser 3b becomes equal to the cooling water Wc in the underground heat exchanger 1, and the exchange heat amount of soil. The water temperature of the cooling water Wc is determined.
And the control apparatus 100 calculates the power consumption of the geothermal heat pump chiller 3 based on the determined water temperature of the cooling water Wc.

  In addition, the relationship between the power consumption of the geothermal heat pump chiller 3 and the water temperature of the cooling water Wc is set in advance as a characteristic of the geothermal heat pump chiller 3, and the control device 100 performs underground operation based on this characteristic. The power consumption of the thermal heat pump chiller 3 can be calculated.

  Next, the control device 100 calculates the power consumption of the air-cooled heat pump chiller 4 (FIG. 8: Step S8). The relationship among the power consumption of the air-cooled heat pump chiller 4, the outside air temperature Tout, and the flow rate of the cold / hot water Wa is set as a characteristic of the air-cooled heat pump chiller 4. Therefore, the control device 100 uses the air-cooled heat pump chiller based on the set outside air temperature Tout and the flow rate of the cold / warm water Wa converted from the discharge amount of the second cold / hot water pump 13 set at the frequency of the third inverter 13a. 4 power consumption can be calculated.

And the control apparatus 100 calculates the power consumption of the heat-source system 10 (FIG. 8: step S9).
The control device 100 sets the total power consumption of the underground heat pump chiller 3 calculated in step S7 and the power consumption of the air-cooled heat pump chiller 4 calculated in step S8 as the power consumption of the heat source system 10 (total power consumption PWall). That is, the control device 100 calculates the total power consumption PWall in step S9 of FIG. And the control apparatus 100 advances a procedure to FIG.9 S10 (code | symbol A).

  In step S10 in FIG. 9, the control device 100 determines whether or not the calculated total power consumption PWall is smaller than the minimum value of the total power consumption PWall stored in the storage unit 100c. When the calculated total power consumption PWall is a minimum value smaller than the value of the total power consumption PWall stored in the storage unit 100c (FIG. 9: Step S10 → Yes), the control device 100 The calculated total power consumption PWall and the set frequency of each of the inverters 11a, 12a, and 13a are stored as minimum values in the storage unit 100c (FIG. 9: Step S11), and the procedure proceeds to Step S12.

  Specifically, the control device 100 stores the set frequency of the second inverter 12a in the storage unit 100c as the frequency at the point where the set outside air temperature Tout and the cooling load factor CW intersect in the cooling water pump table 121. Remember. In addition, the control device 100 stores the set frequency of the first inverter 11a as the frequency at the point where the set outside air temperature Tout and the cooling load factor CW of the first cold / hot water pump table 111 intersect. Store in 100c. Similarly, the control device 100 stores the set frequency of the third inverter 13a as the frequency at the point where the set outside air temperature Tout and the cooling load factor CW of the second cold / hot water pump table 131 intersect. Store in 100c.

Note that, when the total power consumption PWall is not stored in the storage unit 100c, such as when the total power consumption PWall is calculated for the first time, the control device 100 minimizes the total power consumption PWall calculated in step S9 in FIG. The value is stored in the storage unit 100c as a value, and the set frequency of each inverter 11a, 12a, 13a is stored in the storage unit 100c as the frequency of each inverter (FIG. 9: Step S11).
On the other hand, when the calculated total power consumption PWall is not the minimum value (FIG. 9: Step S10 → No), the control device 100 advances the procedure to Step S12 of FIG.

The control device 100 determines whether or not the frequency of the second inverter 12a is the minimum frequency (FIG. 9: Step S12), and if the frequency of the second inverter 12a is not the minimum frequency (FIG. 9: Step S12 → No), The frequency of the second inverter 12a is changed (FIG. 9: Step S13). For example, the control device 100 sets the frequency of the second inverter 12a small by “1 Hz” and returns the procedure to step S5 in FIG. 8 (reference B).
On the other hand, when the frequency of the second inverter 12a is the minimum frequency (FIG. 9: Step S12 → Yes), the control device 100 determines whether the frequency of the third inverter 13a is the minimum frequency (FIG. 9: Step S14). .

If the frequency of the third inverter 13a is not the minimum frequency (FIG. 9: Step S14 → No), the control device 100 changes the frequency of the third inverter 13a (FIG. 9: Step S15). For example, the control device 100 sets the frequency of the third inverter 13a small by “1 Hz” and returns the procedure to step S4 in FIG. 8 (reference C).
On the other hand, when the frequency of the third inverter 13a is the minimum frequency (FIG. 9: Step S14 → Yes), the control device 100 determines whether the frequency of the first inverter 11a is the minimum frequency (FIG. 9: Step S16). .

  If the frequency of the first inverter 11a is not the minimum frequency (FIG. 9: Step S16 → No), the control device 100 changes the frequency of the first inverter 11a (FIG. 9: Step S17). For example, the control device 100 sets the frequency of the first inverter 11a small by “1 Hz” and returns the procedure to step S3 in FIG. 8 (reference numeral D).

  On the other hand, when the frequency of the first inverter 11a is the minimum frequency (FIG. 9: Step S16 → Yes), the control device 100 determines that the set cooling load factor CW is the data table (first cold / hot water pump table 111). , The cooling water pump table 121, the second cold / hot water pump table 131) is determined whether it is the maximum value in the range of the cooling load factor CW (FIG. 9: step S18). For example, when setting the frequency of each inverter 11a, 12a, 13a in the range where the cooling load factor CW is 5 to 100%, the control device 100 determines whether or not the cooling load factor CW is set to 100%. To do. Then, when the set cooling load factor CW is not the maximum value (for example, “100%”) (FIG. 9: Step S18 → No), the control device 100 changes to the side where the cooling load factor CW increases (FIG. 9). : Step S19), the procedure is returned to Step S2 in FIG. 8 (reference E). For example, as illustrated in FIGS. 5 to 7, in the case of a data table in which the cooling load factor CW changes at “5%” intervals, the control device 100 increases the cooling load factor CW by “5%” in step S <b> 19.

  On the other hand, when the set cooling load rate CW is the maximum value of the cooling load rate set in the data table (FIG. 9: Step S18 → Yes), the control device 100 determines that the set outside air temperature Tout is the data table. It is determined whether or not the maximum value is within the range of the outside air temperature set in FIG. 9 (step S20). For example, when setting the frequency of each inverter 11a, 12a, 13a in the range where the outside temperature Tout is in the range of 10 to 40 ° C., the control device 100 determines whether or not the outside temperature Tout is set to 40 ° C. When the outside air temperature Tout is not the maximum value (for example, “40 ° C.”) (FIG. 9: Step S20 → No), the control device 100 changes the temperature to the outside air temperature Tout side. Moreover, the control apparatus 100 changes the cooling load factor CW to the minimum value (FIG. 9: step S21), and returns a procedure to step S2 of FIG. 8 (code | symbol E). For example, in the case of a data table in which the outside air temperature Tout changes at intervals of “2 ° C.” as shown in FIGS. 5 to 7, the control device 100 increases the outside air temperature Tout by “2 ° C.” in step S21. Further, the control device 100 sets the cooling load factor CW to the minimum value (for example, “5%”).

  On the other hand, when the set outside temperature Tout is the maximum value of the outside temperature set in each data table (FIG. 9: Step S20 → Yes), the control device 100 ends the procedure for creating each data table.

  As described above, the control device 100 (calculation unit 100b) of the second embodiment changes the outside air temperature Tout, the cooling load factor CW, and the frequency of each of the inverters 11a, 12a, and 13a sequentially, while the entire heat source system 10 in each state The power consumption PWall is simulated, and the frequencies of the inverters 11a, 12a, and 13a are determined so that the total power consumption PWall for each outside air temperature Tout and the cooling load factor CW is minimized. Then, the cooling water pump table 121 in which the frequency of the second inverter 12a for each of the outside air temperature Tout and the cooling load factor CW is determined, and the frequency of the first inverter 11a for each of the outside air temperature Tout and the cooling load factor CW is determined. The 1st cold / hot water pump table 111 and the 2nd cold / hot water pump table 131 by which the frequency of the 3rd inverter 13a for every outside temperature Tout and the cooling load factor CW were determined are produced.

And when the control apparatus 100 controls the heat source system 10a, the frequency of each inverter 11a, 12a, 13a corresponding to the outside temperature Tout and the cooling load factor CW was created for the cooling water pump table 121, The determination is made with reference to the first cold / hot water pump table 111 and the second cold / hot water pump table 131.
As a result, the heat source system 10a is air-cooled (heat storage operation) in a state where the power consumption (energy consumption) is minimized, so that the energy consumed in the air-cooling operation of the heat source system 10a is reduced.

  FIG. 10 is a configuration diagram of a heat source system according to the third embodiment. In addition, in the heat source system 10b shown in FIG. 10, the same code | symbol is attached | subjected to the same component as the heat source system 10a of Example 2 shown in FIG. 4, and the structure different from the heat source system 10a of Example 2 is demonstrated.

In the heat source system 10b of the third embodiment, the air-cooled heat pump chiller 4 and the underground heat pump chiller 3 are connected via the connection pipe 53 so that the cold / warm water Wa flows directly from the air-cooled heat pump chiller 4 into the underground heat pump chiller 3. Configured. That is, the air-cooled heat pump chiller 4 and the underground heat pump chiller 3 are connected in series in the circulation of the cold / hot water Wa. And the geothermal heat pump chiller 3 and the return header 7 are not directly connected, and the air-cooled heat pump chiller 4 and the forward header 8 are not directly connected.
The heat source system 10b according to the third embodiment is configured in the same manner as the heat source system 10a according to the second embodiment illustrated in FIG. 2 except for the configuration described above.

  In the heat source system 10b shown in FIG. 10, the cold / warm water Wa of the return header 7 is sent to the air / cooling heat pump chiller 4 by the second cold / hot water pump 13 to exchange heat with the outside air, and further flows through the connection pipe 53 to generate the underground heat. Water is fed to the heat pump chiller 3. And after exchanging heat with the cooling water Wc with the geothermal heat pump chiller 3, it distribute | circulates the 1st drain pipe 51b and is sent to the forward header 8. FIG.

  In the control device 100 that controls the heat source system 10b according to the third embodiment, when the heat source system 10b is in cooling operation, the cooling load measuring means (the temperature sensor 43, the temperature sensor 44, and the flow rate sensor 48) is provided as in the second embodiment. Based on the measured cooling load (cooling load factor CW) in the air conditioners 5 and 6, and the outside air temperature Tout measured by the outside air temperature sensor 45, the cooling water pump 12, the first cold / hot water pump 11, and the second The discharge amount of the cold / hot water pump 13 is determined. That is, the control device 100 (calculation unit 100b) is configured so that each inverter (first inverter 11a, second inverter 12a, third inverter) is based on the measured value of the cooling load measuring means and the measured value of the outside air temperature sensor 45. The frequency of 13a) is set respectively.

  In addition, the data tables (cooling water pump table 121, first cold / hot water pump table 111, second cold / hot water pump use) shown in FIGS. Table 131) is stored, and calculation unit 100b refers to each data table based on the measured value (outside temperature Tout) of outside temperature sensor 45 and the measured value (cooling load factor CW) of the cooling load measuring means. The frequencies of the inverters 11a, 12a, and 13a are set.

  As in the second embodiment, the calculation unit 100b of the control device 100 may have a function of creating each data table. In this case, the calculation unit 100b creates each data table according to the procedure shown in FIGS. 8 and 9, but in the case of the heat source system 10b of the second embodiment in which the underground heat pump chiller 3 and the air-cooled heat pump chiller 4 are arranged in parallel. And the parameters are different. For example, the power consumption of the underground heat pump chiller 3 and the air-cooled heat pump chiller 4 calculated by the calculation unit 100b in steps S7 and S8 in FIG. 8 is different.

The heat source system 10a of Example 2 shown in FIG. 4 includes the underground heat pump chiller 3 and the air-cooled heat pump chiller 4 in independent systems. Therefore, the power consumption of the geothermal heat pump chiller 3 and the power consumption of the air-cooled heat pump chiller 4 are calculated independently.
On the other hand, the heat source system 10b of Example 3 shown in FIG. 10 includes the underground heat pump chiller 3 and the air-cooled heat pump chiller 4 in the same system. Therefore, the power consumption of the geothermal heat pump chiller 3 and the power consumption of the air-cooled heat pump chiller 4 change with a predetermined correlation, and each power consumption is calculated based on a specific correlation. Such correlation is appropriately determined based on the characteristics of the underground heat pump chiller 3 and the air-cooled heat pump chiller 4.

  FIG. 11 is a configuration diagram of a heat source system according to the fourth embodiment. In addition, in the heat source system 10c shown in FIG. 11, the same code | symbol is attached | subjected to the same component as the heat source system 10a of Example 2 shown in FIG. 4, and the structure different from the heat source system 10a of Example 2 is demonstrated.

In the heat source system 10c of the fourth embodiment, the first water supply pipe 51a is provided with an open / close valve (first cold / hot water valve 54a) between the return header 7 and the first cold / hot water pump 11, and the air-cooled heat pump chiller 4 and the forward header 8 are provided. The second drain pipe 52b is provided with an open / close valve (second cold / hot water valve 54b).
A connection pipe 54 is provided between the first cold / hot water pump 11 and the first cold / hot water valve 54a between the air-cooling heat pump chiller 4 and the second cold / hot water valve 54b. The connection pipe 54 has an open / close valve (connection pipe). A valve 54c) is provided.
The heat source system 10c according to the fourth embodiment is configured in the same manner as the heat source system 10a according to the second embodiment illustrated in FIG. 4 except for the configuration described above.

In the heat source system 10 c shown in FIG. 11, when the first cold / hot water valve 54 a and the second cold / hot water valve 54 b are opened and the connection pipe valve 54 c is closed, the cold / warm water Wa in the return header 7 is grounded by the first cold / hot water pump 11. Water is sent to the heat heat pump chiller 3, and water is sent to the air-cooled heat pump chiller 4 by the second cold / hot water pump 13. The cold / warm water Wa sent to the geothermal heat pump chiller 3 is exchanged with the cooling water Wc and then sent to the forward header 8, and the cold / warm water Wa sent to the air-cooled heat pump chiller 4 is exchanged with the outside air after heat exchange. Water is sent to the header 8.
In this state, the geothermal heat pump chiller 3 and the air-cooled heat pump chiller 4 are connected in parallel in the circulation of the cold / hot water Wa, and the configuration is the same as that of the heat source system 10a (see FIG. 4) of the second embodiment. Hereinafter, a state where the geothermal heat pump chiller 3 and the air-cooled heat pump chiller 4 are connected in parallel is referred to as a “parallel connection state”.

Further, when the first cold / hot water valve 54a and the second cold / hot water valve 54b are closed and the connection pipe valve 54c is opened, the cold / warm water Wa in the return header 7 is sent to the air / cooling heat pump chiller 4 by the second cold / hot water pump 13 to the outside air. Further, the water is exchanged with water, and further, the water is fed to the underground heat pump chiller 3 through the connection pipe 54. And after exchanging heat with the cooling water Wc with the geothermal heat pump chiller 3, it distribute | circulates the 1st drain pipe 51b and is sent to the forward header 8. FIG.
In this state, the geothermal heat pump chiller 3 and the air-cooled heat pump chiller 4 are connected in series in the circulation of the cold / hot water Wa, and the configuration is the same as the heat source system 10b (see FIG. 10) of the third embodiment. Hereinafter, a state where the geothermal heat pump chiller 3 and the air-cooled heat pump chiller 4 are connected in series is referred to as a “series connection state”.

  That is, the heat source system 10c according to the fourth embodiment appropriately sets the opening / closing of the first cold / hot water valve 54a, the second cold / hot water valve 54b, and the connection pipe valve 54c, thereby enabling the “parallel connection state” and the “series connection state”. Can be switched.

Further, the heat source system 10c of the fourth embodiment includes a data table (cooling water pump table 121 (see FIG. 5), first cold / hot water pump table 111 (see FIG. 6), and second cold / hot water pump table 131 (see FIG. 5). 7))), a data table corresponding to the “parallel connection state” and a data table corresponding to the “series connection state” are preferably stored in the storage unit 100c of the control device 100.
The data table corresponding to “parallel connection state” is a data table created by the control device 100 in the second embodiment, and the data table corresponding to “series connection state” is data created by the control device 100 in the third embodiment. A table can be used.

When the heat source system 10c is switched to the “parallel connection state”, the control device 100 refers to the data table corresponding to the “parallel connection state” based on the outside air temperature Tout and the cooling load factor CW in the air conditioners 5 and 6. Then, the frequency of each inverter (first inverter 11a, second inverter 12a, third inverter 13a) is set.
In addition, when the heat source system 10c is switched to the “series connection state”, the control device 100 uses the data table corresponding to the “series connection state” based on the outside air temperature Tout and the cooling load factor CW in the air conditioners 5 and 6. To determine the frequency of each inverter.

That is, when the heat source system 10c is switched to the “parallel connection state”, the control device 100 (calculation unit 100b) included in the heat source system 10c of the fourth embodiment uses the measured value of the outside air temperature sensor 45 and the cooling load measurement unit ( Based on the measured values of the temperature sensor 43, the temperature sensor 44, and the flow rate sensor 48), the data table corresponding to the “parallel connection state” is referred to, and the frequency of each inverter is determined.
In addition, when the heat source system 10c is switched to the “series connection state”, the control device 100 (calculation unit 100b) performs measurement values of the outside air temperature sensor 45 and cooling load measurement means (temperature sensor 43, temperature sensor 44, The frequency of each inverter is determined by referring to the data table corresponding to the “series connection state” based on the measured value of the flow rate sensor 48).

  With such a configuration, the heat source system 10c has the smallest power consumption (energy consumption) in each state, regardless of whether the state is switched between the “parallel connection state” and the “series connection state”. Since cooling operation (heat storage operation) is performed, energy consumption in the cooling operation of the heat source system 10c is reduced.

In addition, this invention is not limited to an above-described Example. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.
Further, a part of the configuration of a certain embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of a certain embodiment.

For example, the cooling water pump 12 of the heat source system 10 according to the first embodiment shown in FIG. 1 may be provided with the second inverter 12a (see FIG. 4), or the second cold / hot water pump 13 may be provided with the third inverter 13a. (Refer FIG. 4) may be provided.
Further, the heat source system 10 according to the first embodiment may be provided with temperature sensors 42 to 44 (see FIG. 4), flow meters 47 and 48 (see FIG. 4), and an outside air temperature sensor 45 (see FIG. 4).

In addition, the present invention is not limited to the above-described embodiments, and appropriate design changes can be made without departing from the spirit of the invention.
For example, the heat source system 10 of Example 1 shown in FIG. 1, the heat source system 10a of Example 2 shown in FIG. 4, the heat source system 10b of Example 3 shown in FIG. 10, and the heat source system 10c of Example 4 shown in FIG. The two air conditioners 5 and 6 are arranged in parallel. However, the number of air conditioners is not limited to two, and the present invention can be applied to the heat source system 10 (10a to 10c) provided with only one air conditioner, and three or more air conditioners can be used. It is also possible to apply the present invention to the heat source system 10 (10a to 10c) in which the machines are arranged in parallel. Further, the present invention can be applied to the heat source system 10 (10a to 10c) in which two or more air conditioners are arranged in series.

1 underground heat exchanger 2 underground 3 underground heat pump chiller (first heat pump chiller)
4 Air-cooled heat pump chiller (second heat pump chiller)
10, 10a, 10b, 10c Heat source system 11 First cold / hot water pump (first pump)
11a First inverter 12 Cooling water pump (second pump)
12a Second inverter 13 Second cold / hot water pump (third pump)
13a Third inverter 41 Temperature sensor (temperature measuring means)
43, 44 Temperature sensor (cooling load measuring means)
45 Outside temperature sensor 48 Flow meter (cooling load measuring means)
100 Controller 111 First cold / hot water pump table (first data table)
121 Cooling water pump table (second data table)
131 Table for second cold / hot water pump (third data table)
Wa Cold / hot water (working fluid)
Wc Cooling water (heat medium)

Claims (6)

A ground heat exchanger configured to exchange heat between the soil and the heat medium in the ground;
A first heat pump chiller that exchanges heat between the heat medium and the working fluid;
A first pump for feeding the working fluid to the first heat pump chiller;
A first inverter for frequency controlling the first pump;
A second pump for circulating the heat medium between the underground heat exchanger and the first heat pump chiller;
Temperature measuring means for measuring the temperature of the heat medium flowing into the underground heat exchanger by exchanging heat with the working fluid in the first heat pump chiller;
A heat source system comprising: a control device that determines a frequency of the first inverter based on a measurement value of the temperature measurement means during a heat storage operation in which cold energy is stored in the working fluid.   When the measured value of the temperature measuring unit is equal to or higher than a predetermined temperature during the heat storage operation, the control device has a frequency of the first inverter that is lower than when the measured value of the temperature measuring unit is lower than a predetermined temperature. The heat source system according to claim 1, wherein the heat source system is lowered. An outside temperature sensor for measuring the outside temperature;
A cooling load measuring means for measuring a cooling load when the working fluid cools an object to be cooled; and
In the heat storage operation, the control device is configured to reduce the power consumption in the heat storage operation based on the measurement value of the outside air temperature sensor and the measurement value of the cooling load measurement unit. The heat source system according to claim 1, wherein the frequency of the heat source system is determined. The controller is
A simulation function for simulating a change in frequency of the first inverter that minimizes the power consumption during the heat storage operation in response to a change in outside air temperature and a change in the cooling load;
Creating a first data table that determines the frequency of the first inverter that minimizes the power consumption for each combination of outside air temperature and the cooling load;
Further, at the time of the heat storage operation, the frequency of the first inverter is determined with reference to the first data table based on the measured value of the outside air temperature sensor and the measured value of the cooling load measuring means. The heat source system according to claim 3, wherein: A second heat pump chiller configured such that the working fluid can exchange heat with outside air;
A third pump for feeding the working fluid to the second heat pump chiller;
A second inverter for frequency controlling the second pump;
A third inverter for frequency controlling the third pump;
An outside temperature sensor for measuring the outside temperature;
A cooling load measuring means for measuring a cooling load when the working fluid cools an object to be cooled; and
The control device is configured to minimize power consumption in the heat storage operation based on the outside air temperature measured by the outside air temperature sensor and the cooling load measured by the cooling load measuring unit during the heat storage operation. The heat source system according to claim 1 or 2, wherein a frequency of the first inverter, a frequency of the second inverter, and a frequency of the third inverter are determined. The controller is
A change in the frequency of the first inverter, a change in the frequency of the second inverter, and a change in the frequency of the third inverter to minimize the power consumption during the heat storage operation, Having a simulation function of simulating in response to a change in the cooling load;
A first data table that determines a frequency of the first inverter that minimizes the power consumption for each combination of an outside air temperature and the cooling load;
A second data table that determines the frequency of the second inverter that minimizes the power consumption for each combination of outside air temperature and the cooling load;
Creating a third data table that determines the frequency of the third inverter that minimizes the power consumption for each combination of outside air temperature and the cooling load;
Further, during the heat storage operation, the frequency of the first inverter is determined with reference to the first data table based on the measured value of the outside air temperature sensor and the measured value of the cooling load measuring means, The frequency of the second inverter is determined with reference to the second data table, and the frequency of the third inverter is determined with reference to the third data table. Heat source system.

Images