WO2018105702A1 - Système de source de chaleur, dispositif de commande, procédé de commande et programme - Google Patents

Système de source de chaleur, dispositif de commande, procédé de commande et programme Download PDF

Info

Publication number
WO2018105702A1
WO2018105702A1 PCT/JP2017/044061 JP2017044061W WO2018105702A1 WO 2018105702 A1 WO2018105702 A1 WO 2018105702A1 JP 2017044061 W JP2017044061 W JP 2017044061W WO 2018105702 A1 WO2018105702 A1 WO 2018105702A1
Authority
WO
WIPO (PCT)
Prior art keywords
path
load
heat
cooling tower
heat source
Prior art date
Application number
PCT/JP2017/044061
Other languages
English (en)
Japanese (ja)
Inventor
正頌 坂井
智 谷
清一 辻
Original Assignee
三菱重工サーマルシステムズ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱重工サーマルシステムズ株式会社 filed Critical 三菱重工サーマルシステムズ株式会社
Priority to US16/467,011 priority Critical patent/US20190301777A1/en
Priority to CN201780075444.3A priority patent/CN110036248A/zh
Publication of WO2018105702A1 publication Critical patent/WO2018105702A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D13/00—Stationary devices, e.g. cold-rooms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/29—High ambient temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves

Definitions

  • the present invention relates to a heat source system, a control device, a control method, and a program.
  • This application claims priority based on Japanese Patent Application No. 2016-237379 filed in Japan on December 7, 2016, the contents of which are incorporated herein by reference.
  • Patent Document 1 describes a heat source apparatus system that aims to stabilize the operation state by always operating a heat source apparatus in a rated operation region regardless of the heat demand on the heat load side.
  • a cooling tower or a heating tower is connected to the heat source apparatus via an outward path and a return path.
  • a heat load is connected to the heat source machine via an outward path and a return path.
  • the return path from the cooling tower or heating tower and the return path from the heat load are connected to the heat exchanger. This heat exchanger performs heat exchange between the return path from the cooling tower or heating tower and the return path from the heat load.
  • the temperature control of the cooling water supplied to the heat source apparatus is complicated in that the temperature of the cooling water from the cooling tower or the heating tower changes due to heat exchange.
  • the accuracy of the temperature control of the cooling water decreases, the accuracy of the temperature control of the cold water supplied by the heat source system may decrease.
  • the lower limit value is set for the temperature of the cooling water supplied to the heat source unit, the temperature of the cooling water may be lower than the lower limit value and the heat source unit may stop.
  • the present invention provides a heat source system, a control device, and a control method capable of continuing the operation of the heat source device even when the amount of cooling energy required by the heat load is small and performing the cooling water temperature control relatively easily. And provide programs.
  • a heat source system includes a heat source unit, a cooling tower side outward path and a cooling tower side return path connected to the heat source apparatus, and a load side outbound path and a load side connected to the heat source apparatus.
  • the heat source system includes a cooling tower bypass path that connects the cooling tower side forward path and the cooling tower return path, and a cooling tower bypass valve that can adjust a circulation amount of the cooling tower bypass path, and the heat exchange system A path may be provided in the load-side return path, and the heat exchanger may be disposed closer to the heat source unit than the cooling tower bypass path in the cooling tower side forward path.
  • the heat source system includes a cooling tower bypass path that connects the cooling tower side forward path and the cooling tower return path, and a cooling tower bypass valve that can adjust a circulation amount of the cooling tower bypass path, and the heat exchange system
  • the path may be provided closer to the heat source unit than the cooling tower bypass path in the cooling tower side forward path.
  • the heat source system includes a load determination unit that determines whether or not a load of cold supply from the heat source unit is less than a load lower limit value, and the load determination unit includes a load of cold supply from the heat source unit that is the load lower limit value.
  • An operation control unit that controls the heat exchange regulating valve to cause the heat exchanger to perform heat exchange.
  • the control device includes: a heat source unit; a cooling tower side outbound path and a cooling tower side return path connected to the heat source unit; a load side outbound path and a load side connected to the heat source unit.
  • a control device for controlling a heat source system comprising a heat exchanger for heat exchange and a heat exchange control valve capable of adjusting a flow rate of the heat exchange path, wherein a load of the heat source machine is less than a load lower limit value
  • the heat exchanger control valve is controlled to the heat exchanger.
  • An operation control unit that performs heat exchange.
  • the control method includes a heat source unit, a cooling tower side forward path and a cooling tower side return path connected to the heat source unit, and a load side outbound path and a load side connected to the heat source unit.
  • the program includes a heat source unit, a cooling tower side forward path and a cooling tower side return path connected to the heat source unit, and a load side outbound path and a load side return path connected to the heat source unit. And heat exchange between the heat exchange path provided in one of the load side return path and the cooling tower side outbound path, and the other of the heat exchange path and the load side return path and the cooling tower side outbound path A heat exchanger that includes a heat exchanger and a heat exchange regulating valve capable of adjusting a flow rate of the heat exchange path, wherein the load of the heat source machine is a load If it is determined whether or not the load of the heat source unit is less than the lower limit of the load, if the load of the heat source unit is determined to be less than the lower limit of the load, the heat exchanger is controlled to perform heat exchange by controlling the adjustment valve for heat exchange It is a program.
  • the operation of the heat source unit can be continued even when the amount of cooling heat required by the heat load is small, and the temperature control of the cooling water is relatively easy. It can be carried out.
  • FIG. It is a schematic block diagram which shows the function structure of the heat-source system which concerns on embodiment. It is a schematic block diagram which shows the example of an apparatus structure of the refrigerator plant main body 200 which concerns on embodiment. It is a graph which shows the operating range of the turbo refrigerator 300 which concerns on embodiment. It is a flowchart which shows the example of the process sequence which the control apparatus 100 which concerns on embodiment controls the refrigerator plant main body 200. FIG. It is a schematic block diagram which shows another example of the apparatus structure of the refrigerator plant main body 200 which concerns on embodiment.
  • FIG. 1 is a schematic block diagram illustrating a functional configuration of the heat source system according to the embodiment.
  • the heat source system 1 includes a control device 100 and a refrigerator plant main body 200.
  • the control device 100 includes a communication unit 110, a storage unit 180, and a control unit 190.
  • the control unit 190 includes a load determination unit 191 and an operation control unit 192.
  • the heat source system 1 supplies cold heat to the heat load.
  • the heat source system supplies cold water to the heat load. That is, the heat source system 1 supplies cold heat using water as a medium to the heat load.
  • the cold water that the heat source system 1 supplies to the heat load corresponds to an example of cold heat.
  • the heat source system 1 stably supplies cold water even when the amount of cold water required by the heat load suddenly increases from a small amount of cold water. . If the refrigerator stops at a light load, it takes time to restart, and if the amount of chilled water required by the heat load increases rapidly, there is a possibility that the amount of chilled heat that can be supplied will be insufficient or the chilled water at the temperature required by the heat load. May not be able to supply. Therefore, the heat source system 1 has a mechanism and mode that do not stop the refrigerator even with a light load.
  • the control device 100 controls the refrigerator plant main body 200.
  • the operation mode in which the control device 100 controls the refrigerator plant body 200 includes a normal mode and a simulated load mode.
  • the operation mode in which the control device 100 controls the refrigerator plant main body 200 is also referred to as the operation mode of the refrigerator plant main body 200.
  • In the normal mode the refrigerator of the refrigerator plant body 200 is stopped when the load is light, whereas in the simulated load mode, the operation of the refrigerator is continued even when the load is light.
  • the control device 100 is configured using a computer such as a PLC (Programmable Logic Controller) or a general-purpose workstation (Work Station).
  • the communication unit 110 communicates with the refrigerator plant main body 200.
  • the communication unit 110 transmits a control signal to the refrigerator plant main body 200 and receives measurement values from various sensors of the refrigerator plant main body 200.
  • the storage unit 180 stores various data.
  • the storage unit 180 is configured using a storage device provided in the control device 100.
  • the control unit 190 controls each unit of the control device 100 and executes various processes.
  • the control unit 190 is configured by, for example, a CPU (Central Processing Unit) included in the control device 100 reading out a program from the storage unit 180 and executing the program.
  • a CPU Central Processing Unit
  • the load determination unit 191 determines whether or not the load of the heat source unit of the refrigerator plant main body 200 is less than the load lower limit value.
  • the load lower limit value here is a threshold value that is a criterion for determining whether or not to stop the operation of the refrigerator at a light load in the normal mode.
  • the operation control unit 192 performs various calculations for controlling the refrigerator plant main body 200. When the operation mode of the refrigerator plant main body 200 is the simulated load mode and the load determination unit 191 determines that the load of the heat source device of the refrigerator plant main body 200 is less than the load lower limit value, the operation control unit 192 The refrigerator plant body 200 is controlled so that the refrigerator of the refrigerator plant body 200 is not stopped.
  • the refrigerator plant body 200 includes a heat exchanger that receives heat from the refrigerator as a simulated heat load, and the operation control unit 192 adjusts for heat exchange connected to the heat exchanger.
  • the valve is controlled to cause the heat exchanger to exchange heat. This heat exchange increases the load that the refrigerator supplies cold water, and the refrigerator continues to operate without stopping light load.
  • FIG. 2 is a schematic configuration diagram showing an example of the device configuration of the refrigerator plant main body 200.
  • the refrigerator plant body 200 includes a turbo refrigerator 300, a cooling tower 410, a cooling water pump 420, a cooling tower side three-way valve 430, a heat exchanger 500, a cold water pump 620, A load side three-way valve 630, an outward path temperature sensor 711, a return path temperature sensor 712, and a flow rate sensor 721 are provided.
  • the turbo refrigerator 300 includes an evaporator 310, an evaporator pump 320, a turbo compressor 330, a condenser 340, a refrigerant pump 350, and an expansion valve 360.
  • the refrigerator plant body 200 is connected to the heat load 610.
  • the refrigerator plant body 200 operates according to the control of the control unit 190 and supplies cold water to the heat load 610.
  • the turbo chiller 300 corresponds to an example of a heat source machine, and supplies cold water to the heat load 610 in response to a request from the heat load 610.
  • the turbo chiller 300 is designed to stop at light loads. When the load of the turbo chiller 300 is the load lower limit value, the turbo chiller 300 stops under the control of the control device 100.
  • the heat source device included in the refrigerator plant main body 200 is not limited to the turbo refrigerator, and may be a heat source device that stops at a light load.
  • the refrigerator plant body 200 may include a heat source device that can supply both hot water and cold water to the heat load 610 instead of the turbo refrigerator 300.
  • the evaporator 310 performs heat exchange between the refrigerant of the turbo chiller 300 and the cold water supplied to the heat load 610.
  • the evaporator 310 evaporates the refrigerant and lowers the temperature of the cold water by the heat of vaporization.
  • the evaporator 310 sprays the refrigerant from the spray port provided above the pipe through which the cold water flows toward the pipe.
  • the refrigerant first path W31 is a path that connects the lower portion of the evaporator 310 and the spray port.
  • An evaporator pump 320 is provided in the refrigerant first path W31, and the evaporator pump 320 allows the liquid refrigerant accumulated in the evaporator 310 to flow to the spray port.
  • the refrigerant that has become a gas in the evaporator 310 flows into the turbo compressor 330 via the refrigerant second path W32 and is compressed.
  • the gaseous refrigerant whose pressure and temperature are increased by the compression flows into the condenser 340 via the refrigerant third path W33.
  • the condenser 340 cools and liquefies the refrigerant by exchanging heat between the gaseous refrigerant compressed by the turbo compressor 330 and the cooling water.
  • the refrigerant that has become liquid returns to the evaporator 310 via the refrigerant fourth path W34.
  • the refrigerant fourth path W34 is provided with a refrigerant pump 350 and an expansion valve 360.
  • the refrigerant pump 350 conveys liquid refrigerant from the condenser 340 to the evaporator 310.
  • the refrigerant is easily evaporated by being depressurized by the expansion valve 360.
  • FIG. 3 is a graph showing the operating range of the turbo chiller 300.
  • the horizontal axis of the graph in FIG. 3 shows the load factor of the turbo chiller 300.
  • the vertical axis indicates whether the turbo chiller 300 can be operated.
  • the turbo chiller 300 can be operated at a load factor of 30% or more. That is, the operating range of the turbo chiller 300 is a load factor of 30% or more.
  • the centrifugal chiller 300 stops.
  • the heat exchanger 500 receives cold water supplied to the turbo refrigerator 300 when the turbo refrigerator 300 is lightly loaded, thereby increasing the load of the turbo refrigerator 300.
  • the turbo chiller 300 can continue to operate even with a light load, and can supply the required amount of cold water to the heat load.
  • the turbo chiller 300 is connected to the cooling tower 410 via the cooling tower side forward path W11 and the cooling tower side return path W12.
  • the cooling tower 410 cools the cooling water heated by exchanging heat with the refrigerant in the condenser 340 of the turbo refrigerator 300.
  • the cooling tower side forward path W ⁇ b> 11 is a path through which the cooling water heated by the condenser 340 flows to the cooling tower 410.
  • the cooling tower side return path W 12 is a path through which the cooling water cooled by the cooling tower 410 flows to the condenser 340.
  • the cooling water pump 420 circulates cooling water between the turbo chiller 300 and the cooling tower 410. In the example of FIG. 2, the cooling water pump 420 is provided in the cooling tower side return path W ⁇ b> 12, and flows cooling water from the cooling tower 410 to the turbo refrigerator 300.
  • the turbo chiller 300 is connected to the thermal load 610 via a load side forward path W21 and a load side return path W22.
  • the load side forward path W ⁇ b> 21 is a path through which the cold water cooled by the evaporator 310 of the turbo chiller 300 flows to the thermal load 610.
  • the load-side return path W ⁇ b> 22 is a path through which cold water that has been used in the thermal load 610 and has increased in temperature flows to the evaporator 310.
  • the cold water pump 620 circulates cold water between the turbo chiller 300 and the heat load 610. In the example of FIG. 2, the chilled water pump 620 is provided in the load-side return path W ⁇ b> 22 and flows chilled water from the heat load 610 to the turbo chiller 300.
  • the heat load 610 may return all the cold water supplied from the evaporator 310 to the evaporator 310.
  • the heat load 610 may take part or all of the cold water and not return it to the evaporator 310.
  • water may be supplied to the evaporator 310 from a water supply source such as a water supply instead of the cold water taken in by the heat load 610.
  • the supplied water may be room temperature water.
  • a heat exchanger 500 is provided in the cooling tower side forward path W11.
  • the heat exchanger 500 is connected to the load side return path W22 via the heat exchange path W23.
  • the heat exchanger 500 performs heat exchange between the cooling tower side forward path W11 and the load side return path W22 by performing heat exchange between the cooling tower side forward path W11 and the heat exchange path W23.
  • the cold water that is diverted from the load-side return path W22 to the heat exchange path W23 absorbs heat from the cooling water that flows through the cooling tower-side forward path W11.
  • the temperature of the cold water returning to the turbo chiller 300 is increased by this heat absorption, and the load at which the turbo chiller 300 supplies cold water to the heat load 610 is increased. Thereby, even when the amount of cold water required by the heat load 610 is small, the load on the turbo chiller 300 becomes equal to or greater than the load lower limit value, and the turbo chiller 300 continues to operate.
  • the load side return path W22 and the heat exchange path W23 are connected via a heat load side three-way valve 630.
  • the heat load side three-way valve 630 is a flow rate adjustment valve corresponding to an example of a heat exchange adjustment valve, and adjusts the amount of cold water branched from the load side return path W22 to the heat exchange path W23.
  • the heat load side three-way valve 630 can set the flow rate from the load side return path W22 to the heat exchange path W23 to zero. As a result, the branch of cold water from the load-side return path W22 to the heat exchange path W23 is blocked.
  • two two-way valves may be used to perform the same control as the three-way valve. The same applies to the other three-way valves.
  • a cooling tower bypass path W13 is provided between the cooling tower side forward path W11 and the cooling tower side return path W12.
  • the temperature of the cooling water flowing to the condenser 340 can be adjusted by bypassing a part of the cooling water flowing through the cooling tower side forward path W11 by the cooling tower bypass path W13 to the cooling tower side return path W12.
  • the cooling tower side forward path W11 and the cooling tower bypass path W13 are connected via a cooling tower side three-way valve 430.
  • the cooling tower side three-way valve 430 is a flow rate adjustment valve corresponding to an example of the cooling tower bypass valve, and adjusts the amount of cooling water bypassed from the cooling tower side forward path W11 to the cooling tower side return path W12.
  • the cooling tower side three-way valve 430 can make the flow rate of the cooling water from the cooling tower side forward path W11 to the cooling tower bypass path W13 zero. As a result, the bypass of the cooling water from the cooling tower side forward path W11 to the cooling tower side return path W12 is blocked.
  • the cooling tower side three-way valve 430 is provided on the downstream side of the heat exchanger 500 in the cooling tower side forward path W11.
  • the downstream side of the heat exchanger 500 is a side close to the cooling tower 410 when viewed from the condenser 340.
  • the cooling water flows through the cooling tower side three-way valve 430 after heat exchange in the heat exchanger 500. For this reason, the cooling water that has passed through the cooling tower side three-way valve 430 does not change in temperature via the heat exchanger 500 before reaching the condenser 340.
  • control unit 190 calculates the bypass amount of the cooling water based on the temperature of the cooling water in the cooling tower side three-way valve 430, it is not necessary to consider the temperature change of the cooling water by the heat exchanger 500. In this respect, it is possible to avoid an increase in load for the control unit 190 to calculate the bypass amount of the cooling water.
  • the outward path temperature sensor 711 is provided in the load-side outbound path W21, and measures the temperature of the cold water flowing through the load-side outbound path W21.
  • the return side temperature sensor 712 is provided in the load side return path W22 and measures the temperature of the cold water flowing through the load side return path W22.
  • the flow rate sensor 721 is provided in the load side forward path W21 and measures the flow rate of the cold water flowing through the load side forward path W21.
  • a value obtained by multiplying a temperature difference obtained by subtracting the temperature measured by the forward path temperature sensor 711 from the temperature measured by the return path temperature sensor 712 and the flow rate measured by the flow sensor 721 indicates the amount of cold water consumed by the heat load 610. Can be considered. In other words, the amount of cold water heat QI_CH consumed by the heat load 610 is expressed as in Expression (1).
  • TI_CHo indicates the cold water outlet temperature.
  • the temperature of the cold water in the load-side outward path W21 measured by the outward-path temperature sensor 711 can be used.
  • TI_CHi indicates the cold water inlet temperature.
  • the temperature of the cold water in the load side return path W22 measured by the return side temperature sensor 712 can be used.
  • FI_CH indicates the cold water flow rate.
  • the chilled water flow rate the chilled water flow rate in the load-side outward path W21 measured by the flow rate sensor 721 can be used.
  • FIG. 4 is a flowchart illustrating an example of a processing procedure in which the control device 100 controls the refrigerator plant main body 200.
  • the control device 100 performs the process of FIG. 4 when an operation start operation that is a user operation instructing the operation start of the heat source system 1 is performed.
  • the operation control unit 192 of the control device 100 activates the turbo chiller 300 (step S ⁇ b> 101).
  • the operation control unit 192 waits for elapse of t2 time from the start of the start of the turbo chiller 300 (step S102), and further waits for elapse of t1 time (step S103).
  • the t1 time is a control determination cycle in the control device 100.
  • the control determination cycle is a cycle in which the operation control unit 192 repeats the process of determining the operation mode of the refrigerator plant main body 200 and controlling the refrigerator plant main body 200.
  • the time t2 is the startup time of the turbo chiller 300. Specifically, the time t2 is an effect waiting time from the start of the start of the turbo chiller 300 until the cooling effect appears.
  • step S103 is not essential. Therefore, the operation control unit 192 may transition to step S104 without waiting for the time in step S103 after waiting for t2 time in step S102.
  • the operation control unit 192 determines the operation mode of the refrigerator plant main body 200 (step S104). For example, the operation control unit 192 calculates the amount of chilled water heat QI_CH consumed by the heat load 610 based on the above equation (1). Then, the operation control unit 192 determines the operation mode by comparing the calculated amount of cold water heat QI_CH with the heat amount lower limit Qmin. When Expression (2) is satisfied, the operation control unit 192 determines that the operation mode of the refrigerator plant body 200 is the normal mode.
  • h1 represents a coefficient for preventing hunting.
  • the operation control unit 192 determines that the operation mode of the refrigerator plant main body 200 is the simulated load mode.
  • h2 represents a coefficient for preventing hunting.
  • the heat amount lower limit Qmin may be determined in advance as a constant value. Or when the range of the load factor which can be drive
  • the operation control unit 192 may determine the operation mode based on the cold water inlet temperature Ti_CHi and the temperature lower limit value Tmin instead of the cold water heat amount QI_CH and the heat lower limit value Qmin. For example, when Formula (4) is materialized, the operation control unit 192 determines that the operation mode of the refrigerator plant body 200 is the normal mode.
  • h3 represents a coefficient for preventing hunting.
  • the operation control unit 192 determines that the operation mode of the refrigerator plant body 200 is the simulated load mode.
  • step S104 determines whether the operation mode is the simulated load mode (step S104: simulated load mode).
  • the operation control unit 192 performs simulated load operation control (step S111).
  • the operation control unit 192 controls the heat load side three-way valve 630 so that the chilled water calorie QI_CH obtained by the equation (1) is equal to or greater than the calorie lower limit Qmin, and the chilled water flowing into the heat exchanger 500 Adjust the flow rate.
  • step S131 the operation control unit 192 waits for elapse of t2 time (step S112). Then, the operation control unit 192 determines whether an operation end operation has been performed (step S131).
  • the operation end operation here is a user operation that instructs the end of the operation of the heat source system 1.
  • step S131: NO it returns to step S104.
  • step S131: YES the operation control part 192 stops the turbo refrigerator 300 (step S141). And the operation control part 192 complete
  • step S104 when it is determined in step S104 that the operation mode is the normal mode (step S104: normal mode), the operation control unit 192 performs normal operation control (step S121).
  • the operation control unit 192 stops the heat exchanger 500 by controlling the heat load side three-way valve 630 so that the flow rate of the cold water branched from the load side return path W22 to the heat exchange path W23 becomes zero. Let Then, the operation control unit 192 waits for elapse of t2 time (step S122). After step S122, the process proceeds to step S131.
  • the heat exchange path W23 is provided in the load side return path W22, and the heat exchanger 500 exchanges heat between the heat exchange path W23 and the cooling tower side forward path W11. Further, the heat load side three-way valve 630 can adjust the flow rate of the heat exchange path W23.
  • the heat exchanger 500 exchanges heat between the heat exchange path W23 and the cooling tower side forward path W11, so that the temperature of the cooling water does not change due to heat exchange after passing through the cooling tower 410. .
  • the heat source system 1 can relatively easily control the temperature of the cooling water. Therefore, in the heat source system 1, the operation of the turbo chiller 300 can be continued even when the amount of cold water required by the heat load 610 is small, and the temperature control of the cooling water can be performed relatively easily.
  • the cooling tower bypass path W13 connects the cooling tower side forward path W11 and the cooling tower side return path W12, and the cooling tower side three-way valve 430 can adjust the flow rate of the cooling tower bypass path W13.
  • the heat exchanger 500 is arranged on the turbo refrigerator 300 side (upstream side of the cooling water path) of the cooling tower side forward path W11 with respect to the cooling tower bypass path W13.
  • the cooling water flows through the cooling tower side three-way valve 430 after heat exchange in the heat exchanger 500. For this reason, the cooling water that has passed through the cooling tower side three-way valve 430 does not change in temperature via the heat exchanger 500 before reaching the condenser 340.
  • the control unit 190 calculates the bypass amount of the cooling water based on the temperature of the cooling water in the cooling tower side three-way valve 430, it is not necessary to consider the temperature change of the cooling water by the heat exchanger 500. In this respect, it is possible to avoid an increase in load for the control unit 190 to calculate the bypass amount of the cooling water.
  • the cooling water can be effectively utilized in that it is cooled by exchanging heat with the cooling water in the heat exchanger 500.
  • the load determination part 191 determines whether the load of the cold water supply to the heat load 610 is less than a load lower limit value.
  • the operation control unit 192 controls the heat load side three-way valve 630 to exchange heat with the heat exchanger 500. To do. Thereby, the operation of the turbo chiller 300 can be continued even when the amount of cold water required by the heat load 610 is small. And when the load of the cold water supply to the heat load 610 is more than a load lower limit, the heat exchanger can be stopped, and the turbo chiller 300 can be operated efficiently.
  • FIG. 5 is a schematic configuration diagram illustrating another example of the apparatus configuration of the refrigerator plant main body 200.
  • the refrigerator plant main body 200 includes a heat exchange three-way valve 240, a turbo refrigerator 300, a cooling tower 410, a cooling water pump 420, a cooling tower side three-way valve 430, and a heat exchanger 500.
  • the turbo refrigerator 300 includes an evaporator 310, an evaporator pump 320, a turbo compressor 330, a condenser 340, a refrigerant pump 350, and an expansion valve 360.
  • the refrigerator plant body 200 is connected to the heat load 610.
  • the heat exchanger 500 is provided in the cooling tower side forward path W11, whereas in the example of FIG. 5, the heat exchanger 500 is provided in the load side return path W22.
  • the heat load side three-way valve 630 is provided in the load side return path W22, and the heat load side three way valve 630 and the heat exchanger 500 are connected by the heat exchange path W23.
  • the heat exchange three-way valve 240 is provided in the cooling tower side forward path W11, and the heat exchange three-way valve 240 and the heat exchanger 500 are connected by the heat exchange path W14.
  • the other points are the same as in the case of FIG.
  • the heat exchange three-way valve 240 corresponds to an example of a heat exchange three-way valve, and adjusts the amount of cooling water branched from the cooling tower side forward path W11 to the heat exchange path W14.
  • the heat exchange three-way valve 240 is provided upstream of the cooling tower side three-way valve 430 in the cooling tower side forward path W11.
  • the upstream side of the cooling tower side three-way valve 430 is closer to the turbo refrigerator 300 than the cooling tower side three way valve 430 when viewed from the turbo refrigerator 300.
  • the heat exchange path W14 is provided in the cooling tower side forward path W11, and the heat exchanger 500 exchanges heat between the heat exchange path W23 and the load side return path W22. Further, the heat exchange three-way valve 240 can adjust the flow rate of the heat exchange path W14.
  • the heat exchanger 500 exchanges heat between the heat exchange path W14 and the load side return path W22, and the heat exchange path W14 is provided in the cooling tower side forward path W11. There is no change in temperature due to heat exchange after passing through the cooling tower 410.
  • the heat source system 1 can relatively easily control the temperature of the cooling water. Therefore, in the heat source system 1, the operation of the turbo chiller 300 can be continued even when the amount of cold water required by the heat load 610 is small, and the temperature control of the cooling water can be performed relatively easily.
  • the heat exchanging path W14 is provided on the turbo chiller 300 side (upstream side of the cooling water path) with respect to the cooling tower bypass path W13 in the cooling tower side forward path W11.
  • the cooling water branched to the heat exchange path W ⁇ b> 14 flows through the cooling tower side three-way valve 430 after heat exchange in the heat exchanger 500.
  • the cooling water that has passed through the cooling tower side three-way valve 430 does not change in temperature via the heat exchanger 500 before reaching the condenser 340. Therefore, when the control unit 190 calculates the bypass amount of the cooling water based on the temperature of the cooling water in the cooling tower side three-way valve 430, it is not necessary to consider the temperature change of the cooling water by the heat exchanger 500. In this respect, it is possible to avoid an increase in load for the control unit 190 to calculate the bypass amount of the cooling water.
  • the cooling water can be effectively utilized in that it is cooled by exchanging heat with the cooling water in the heat exchanger 500.
  • a program for realizing all or part of the functions of the control unit 190 is recorded on a computer-readable recording medium, and the program recorded on the recording medium is read into a computer system and executed. You may perform the process of.
  • the “computer system” includes an OS and hardware such as peripheral devices.
  • the “computer-readable recording medium” refers to a storage device such as a flexible medium, a magneto-optical disk, a portable medium such as a ROM or a CD-ROM, and a hard disk incorporated in a computer system.
  • the program may be a program for realizing a part of the functions described above, and may be a program capable of realizing the functions described above in combination with a program already recorded in a computer system.
  • Embodiments of the present invention include a heat source unit, a cooling tower side outbound path and a cooling tower side return path connected to the heat source unit, a load side outbound path and a load side return path connected to the heat source unit, and the load side return path and A heat exchanger provided in any one of the cooling tower side outbound path, the heat exchange path, and a heat exchanger for exchanging heat between the load side return path and the cooling tower side outbound path,
  • the present invention relates to a heat source system comprising: a heat exchange adjustment valve capable of adjusting a flow rate of the heat exchange path. According to this embodiment, the operation of the heat source device can be continued even when the amount of cooling required by the heat load is small, and the temperature control of the cooling water can be performed relatively easily.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un système de source de chaleur comprenant : un dispositif de source de chaleur; un trajet vers l'extérieur côté tour de refroidissement et un trajet de retour côté tour de refroidissement qui sont reliés au dispositif de source de chaleur; un trajet vers l'extérieur côté charge et un trajet de retour côté charge qui sont reliés au dispositif de source de chaleur; un canal d'échange de chaleur disposé dans un trajet parmi le trajet de retour côté charge et le trajet vers l'extérieur côté tour de refroidissement; un échangeur de chaleur pour échanger de la chaleur entre le canal d'échange de chaleur et l'autre trajet entre le trajet de retour côté charge et le trajet vers l'extérieur côté tour de refroidissement ne contenant pas le canal d'échange de chaleur; et une soupape de régulation d'échangeur de chaleur qui est capable d'ajuster le débit dans le canal d'échange de chaleur.
PCT/JP2017/044061 2016-12-07 2017-12-07 Système de source de chaleur, dispositif de commande, procédé de commande et programme WO2018105702A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US16/467,011 US20190301777A1 (en) 2016-12-07 2017-12-07 Heat source system, control device, control method, and program
CN201780075444.3A CN110036248A (zh) 2016-12-07 2017-12-07 热源系统、控制装置、控制方法以及程序

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016237379A JP6719370B2 (ja) 2016-12-07 2016-12-07 熱源システム、制御装置、制御方法及びプログラム
JP2016-237379 2016-12-07

Publications (1)

Publication Number Publication Date
WO2018105702A1 true WO2018105702A1 (fr) 2018-06-14

Family

ID=62491864

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/044061 WO2018105702A1 (fr) 2016-12-07 2017-12-07 Système de source de chaleur, dispositif de commande, procédé de commande et programme

Country Status (4)

Country Link
US (1) US20190301777A1 (fr)
JP (1) JP6719370B2 (fr)
CN (1) CN110036248A (fr)
WO (1) WO2018105702A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2019456022B2 (en) * 2019-07-09 2023-10-19 Nec Corporation Cooling system
DE102020110357A1 (de) 2020-04-16 2021-10-21 Wolfram Ungermann Systemkälte GmbH & Co. KG Verfahren zur Regelung eines hybriden Kühlsystems sowie hybrides Kühlsystem

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07280386A (ja) * 1994-04-11 1995-10-27 Toshiba Corp 熱源機器システム
JP2010085010A (ja) * 2008-09-30 2010-04-15 Hitachi Plant Technologies Ltd 空調システム
JP2012132650A (ja) * 2010-12-24 2012-07-12 Ebara Corp 超臨界サイクルヒートポンプ装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6202431B1 (en) * 1999-01-15 2001-03-20 York International Corporation Adaptive hot gas bypass control for centrifugal chillers
US6532754B2 (en) * 2001-04-25 2003-03-18 American Standard International Inc. Method of optimizing and rating a variable speed chiller for operation at part load
CN1247945C (zh) * 2003-07-08 2006-03-29 浙江大学 低温热源热泵系统
JP5777929B2 (ja) * 2011-04-22 2015-09-09 株式会社日立製作所 冷熱源装置の運転制御システム
CN103913005B (zh) * 2013-01-09 2016-05-11 美的集团股份有限公司 制冷系统及其控制方法和具该制冷系统的空调
CN204854097U (zh) * 2015-07-16 2015-12-09 上海出入境检验检疫局机电产品检测技术中心 水冷式冷水机组测试系统
CN205079492U (zh) * 2015-11-02 2016-03-09 艾默生网络能源有限公司 一种空调系统
CN205425322U (zh) * 2015-12-15 2016-08-03 湖南艾迪希网络能源有限公司 一种多源热管节能系统

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07280386A (ja) * 1994-04-11 1995-10-27 Toshiba Corp 熱源機器システム
JP2010085010A (ja) * 2008-09-30 2010-04-15 Hitachi Plant Technologies Ltd 空調システム
JP2012132650A (ja) * 2010-12-24 2012-07-12 Ebara Corp 超臨界サイクルヒートポンプ装置

Also Published As

Publication number Publication date
CN110036248A (zh) 2019-07-19
JP2018091588A (ja) 2018-06-14
JP6719370B2 (ja) 2020-07-08
US20190301777A1 (en) 2019-10-03

Similar Documents

Publication Publication Date Title
US20200158356A1 (en) Heat source system and control method therefor
JP5514787B2 (ja) 環境試験装置
US20160370047A1 (en) Chilling machine
WO2018105702A1 (fr) Système de source de chaleur, dispositif de commande, procédé de commande et programme
JP2012159236A (ja) 排熱回収システムおよび排熱回収方法
JP2007303806A (ja) 冷凍サイクル装置とその運転方法
US20130291575A1 (en) Cooling system and method for operating same
KR20100063680A (ko) 흡수 냉각기에서 온도를 제어하기 위한 방법 및 시스템
JP5088783B2 (ja) 蒸気吸収式冷凍機の省エネルギー制御運転方法及び装置
JP2008025915A (ja) 吸収冷凍機システム
RU2368850C2 (ru) Устройство управления холодильного контура с внутренним теплообменником
JP7213476B2 (ja) 吸収式冷凍機
KR101501175B1 (ko) 반도체 공정용 칠러의 온도제어 방법
JP6262560B2 (ja) 空気調和装置および空気調和装置の制御方法
JP2010007962A (ja) 温度調整装置
KR101120251B1 (ko) 흡수 냉각기에서 방열하기 위한 방법 및 시스템
JP2010007957A (ja) 温度調整装置
JP4721783B2 (ja) 吸収冷温水機の運転制御方法
JP2012245501A (ja) 圧縮空気除湿装置
JP2010007955A (ja) 温度調整装置
JP5696319B2 (ja) 圧縮空気除湿装置
JP2016169891A (ja) 冷凍装置における蒸発器出入口の目標温度差設定方法及び装置、並びに冷凍装置の制御装置
KR101438182B1 (ko) 브라인 온도 및 유량 제어용 부가 장치
US11815298B2 (en) Combined air conditioning and water heating via expansion valve regulation
JP2019152347A (ja) チラーシステム

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17877725

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17877725

Country of ref document: EP

Kind code of ref document: A1