WO2019021406A1 - 空調システムおよび熱媒体封入方法 - Google Patents
空調システムおよび熱媒体封入方法 Download PDFInfo
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- WO2019021406A1 WO2019021406A1 PCT/JP2017/027142 JP2017027142W WO2019021406A1 WO 2019021406 A1 WO2019021406 A1 WO 2019021406A1 JP 2017027142 W JP2017027142 W JP 2017027142W WO 2019021406 A1 WO2019021406 A1 WO 2019021406A1
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- heat medium
- gas
- load
- side heat
- circuit
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- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/003—Indoor unit with water as a heat sink or heat source
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- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0315—Temperature sensors near the outdoor heat exchanger
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
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- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
Definitions
- the present invention relates to an air conditioning system in which a heat transfer medium transports heat and cold generated by a refrigerant circuit to a use side, and a heat transfer medium enclosing method.
- a direct expansion system in which refrigerant is circulated between a heat source and a user-side heat exchanger, the procedure is generally such that the refrigerant is injected into the pipe after the air in the pipe is evacuated at the time of piping construction.
- An indirect system is another type of system that is contrasted with a direct expansion system.
- a water air conditioning system and a hot water supply system for circulating a heat medium such as water and antifreeze liquid correspond to indirect systems.
- a procedure is generally used in which water or the like supplied from a water supply is injected into the piping without vacuuming air in the piping. In this procedure, when water is sealed in the pipe, air is not evacuated, so air density may remain in the pipe due to the influence of air density and surface tension.
- Torii-like piping is known as an example of piping in which an air mass tends to remain.
- the torii shaped pipe is configured to have two pipes standing in parallel in the vertical direction with respect to the ground, and a horizontal pipe connecting the upper end of the two pipes.
- the torii shaped pipe is referred to as a refractive pipe.
- Patent Document 1 discloses an example of a method of not leaving air lumps in piping in an indirect system.
- Patent Document 1 discloses that an air vent valve is provided at a position where the position of the pipe is higher than the surrounding with respect to the above-mentioned refraction pipe, and when the water is sealed in the pipe, the air is vented from the valve. .
- FIG. Patent Document 2 discloses that the water is pressurized to push the foreign matter out of the circulating hot water circuit.
- Patent Document 3 proposes a method of evacuating a pipe as in the direct expansion method. The method disclosed in Patent Document 3 is easy for the worker to work because the operation of sealing water in the pipe is similar to the case of filling the refrigerant.
- Patent Document 1 it is necessary to consider the installation position of the air vent valve at the time of piping design. If there are many refracted pipes where a part of the pipes is higher than the surrounding pipes, it is necessary to attach a large number of air vent valves.
- the present invention has been made to solve the above-mentioned problems, and provides an air conditioning system and a heat medium sealing method for reducing the amount of residual air and improving the heat transport efficiency in the load side heat medium circuit. It is.
- a heat source side refrigerant circuit provided with a heat source side heat exchanger, a load side heat medium circuit provided with a load side heat exchanger, the heat source side refrigerant circuit, and the load side heat medium
- the heat medium includes: an intermediate heat exchanger for exchanging heat with the circuit; and a heat medium sealing mechanism provided in the load-side heat medium circuit and supplying the heat medium to the load-side heat medium circuit.
- An encapsulation mechanism is connected to the load-side heat medium circuit, and is connected to a supply port through which the heat medium and a gas that is more soluble in air than the heat medium flow, and the load-side heat medium circuit.
- An outlet from which the gas is discharged by being pushed by the heat medium a circuit for causing the gas or the heat medium to flow from the supply port to the outlet at the time of supply of the gas and at the time of supply of the gas.
- a rectifying device to be connected.
- the heat medium sealing method according to the present invention is provided between a heat source side refrigerant circuit including a heat source side heat exchanger, a load side heat exchanger, a supply port, a discharge port, and the supply port and the discharge port.
- Heat to the load side heat medium circuit in an air conditioning system having a load side heat medium circuit including a rectifying device, and an intermediate heat exchanger that exchanges heat between the heat source side refrigerant circuit and the load side heat medium circuit
- a medium enclosing method wherein the gas is supplied to the load side heat medium circuit from the supply port until air is dissolved in the load side heat medium circuit, the gas being more soluble in the heat medium than air.
- the gas which is more soluble in the heat medium than air is sealed in the pipe while pushing out the air, whereby the sealed gas is contained in the pipe. Even if it remains, it is suppressed that a big lump like an air lump is formed in piping. As a result, the flow path resistance due to the gas lump is reduced, and the heat transport efficiency of the load side heat medium circuit is improved.
- FIG. 1 It is a refrigerant circuit figure showing an example of 1 composition of an air-conditioning system concerning Embodiment 1 of the present invention. It is a figure which shows the example of installation of the air-conditioning system shown in FIG. It is an enlarged view which shows one structural example of the heat-medium enclosure mechanism shown in FIG. It is a block diagram which shows one structural example of the control apparatus shown in FIG. It is a flowchart which shows the procedure which encloses water in a load side heat-medium circuit in the air conditioning system of Embodiment 1 of this invention. It is the figure which showed typically the load side heat-medium circuit shown in FIG. FIG.
- FIG. 7 is a graph showing the relationship between the distance from the supply port and the concentration of gas X in the load-side heat medium circuit shown in FIG. 6. It is a figure which shows that piping shape disturbs the flow of gas in T-shaped pipe
- FIG. 1 is a refrigerant circuit diagram showing one configuration example of the air conditioning system according to Embodiment 1 of the present invention.
- FIG. 2 is a view showing an installation example of the air conditioning system shown in FIG.
- the air conditioning system 100 performs a primary side cycle that generates cold and warm heat using a refrigeration cycle and a secondary side cycle that heats and transports cold and warm heat generated in the primary side cycle.
- the case of the refrigeration air conditioner will be described.
- the air conditioning system 100 includes a heat source unit 10 and a plurality of load side units 50-1 to 50-3.
- the load side units 50-1 to 50-3 are connected in parallel with the heat source unit 10.
- the heat source unit 10 is installed on the roof of a building, and the load side units 50-1 to 50-3 are installed on the ceiling of a room to be air conditioned in the building.
- FIG. 1 shows the configuration in which three load side units are connected to one heat source unit 10, but in the load side units connected to the heat source unit 10, The number is not limited to three.
- FIG. 2 shows the case where three load side units are connected to the heat source unit 10 in addition to the load side units 50-1 to 50-3.
- the air conditioning system 100 may have a configuration in which two or more load-side units are connected to two or more heat source units.
- the load side units 50-1 to 50-3 are connected to the heat source unit 10 through the forward pipe 64 and the return pipe 65.
- the forward pipe 64 serves to supply a heat medium from the heat source unit 10 to the load side units 50-1 to 50-3.
- the return pipe 65 serves to return the heat medium from the load side units 50-1 to 50-3 to the heat source unit 10.
- the forward pipe 64 branches into first connection pipes 64c-1 to 64c-3 inside the building.
- the first connection pipes 64c-1 to 64c-3 are respectively connected to the load side units 50-1 to 50-3.
- the second connection pipes 65c-1 to 65c-3 are connected to the load side units 50-1 to 50-3, respectively.
- the second connection pipes 65c-1 to 65c-3 merge with the return pipe 65.
- the air conditioning system 100 has a heat source side refrigerant circuit 110 in which a primary side cycle is performed, and a load side heat medium circuit 120 in which a secondary side cycle is performed.
- the heat source side refrigerant circuit 110 is configured such that the compressor 1, the heat source side heat exchanger 3, the expansion device 4, the intermediate heat exchanger 5 and the liquid collecting mechanism 6 are connected by piping.
- the load side heat exchangers 52c-1 to 52c-3 are respectively provided to the load side units 50-1 to 50-3.
- the load-side heat medium circuit 120 has a configuration in which the pump 51, the intermediate heat exchanger 5, and the load-side heat exchanger 52c-1 are connected by piping. In the configuration example shown in FIG.
- the load-side heat medium circuit 120 is also formed in a circuit in which the pump 51, the intermediate heat exchanger 5, and the load-side heat exchanger 52c-2 are connected by piping. Furthermore, the load-side heat medium circuit 120 is also formed in a circuit in which the pump 51, the intermediate heat exchanger 5, and the load-side heat exchanger 52c-3 are connected by piping.
- the air conditioning system 100 of the first embodiment has a heat medium sealing mechanism 54 for sealing the heat medium in the load-side heat medium circuit 120.
- the primary side cycle is performed in the heat source side refrigerant circuit 110 of the heat source unit 10, and cold heat and heat generated by the primary side cycle go through the load pipe 64 and the return pipe 65 50-3.
- refrigerants used for the primary side cycle there are fluorocarbon refrigerant, HFO refrigerant, CO 2 refrigerant, HC refrigerant, and ammonia refrigerant.
- the fluorocarbon refrigerants include R32, R125 and R134a of the HFC refrigerant, or R410A, R407c and R404A which are mixed refrigerants of these.
- HFO refrigerants include HFO-1234yf, HFO-1234ze (E), HFO-1234ze (Z), and HFO-1123.
- HC refrigerants include propane and isobutane refrigerants.
- the refrigerant used in the primary side cycle may be a mixed refrigerant obtained by mixing a plurality of refrigerants.
- a mixed refrigerant in addition to the mixed refrigerant of the HFC refrigerant, there is a refrigerant used in a vapor compression type heat pump.
- the mixed refrigerant may be a mixed refrigerant of R32, HFO-1234yf and R125.
- the heat medium used for the secondary side cycle includes water and antifreeze.
- Antifreeze is a mixture of ethylene glycol, propylene glycol and methanol in water.
- the air conditioning system is a refrigeration air conditioner
- any device that requires an operation of sealing the heat medium in the load side heat medium circuit 120 may be used, and the air conditioning system may be a refrigeration air conditioner It is not limited to.
- the heat source side refrigerant circuit 110 is not limited to the circuit that performs the refrigeration cycle.
- the heat source in the heat source side refrigerant circuit 110 may be a heat source device such as a boiler that obtains warm heat by burning fuel.
- the relationship between the sizes of the respective components may be different from actual ones.
- the application of the heat is hot water use such as hot water supply and floor heating
- the use of cold heat may be cold water use such as floor cooling.
- FIG. 1 shows a configuration in which a plurality of load side units 50-1 to 50-3 are connected in parallel to the heat source unit 10, but according to the load design of the space to be air conditioned, the load side unit 50-1 You may change the connection method of ⁇ 50-3.
- the load side units 50-1 to 50-3 may be arranged along the piping of the load side heat medium circuit 120 and connected in series. Usually, when the temperature conditions of the load side units 50-1 to 50-3 do not greatly differ, they are installed in parallel as shown in FIG. 1 and FIG. Furthermore, the capacities of the load-side units to be air-conditioned may be the same or may be different from each other.
- the heat source unit 10 is generally disposed in a space outside a building such as a building, and supplies cold heat and heat to the load side units 50-1 to 50-3.
- the space outside the building is, for example, the rooftop.
- FIG. 2 shows the case where the heat source unit 10 is installed on the roof of a building.
- the heat source unit 10 may be installed, for example, in an enclosed space such as a ceiling and a machine room with a vent.
- the heat source unit 10 may be installed inside a building as long as waste heat can be exhausted to the outside of the building by an exhaust duct.
- the heat source unit 10 may be installed inside a building using a water-cooled heat source side heat exchanger.
- the heat source unit 10 may be installed at any location as long as it can exchange heat with the outside air.
- the heat source unit 10 includes a compressor 1, a four-way valve 2, a heat source side heat exchanger 3, a throttling device 4, an intermediate heat exchanger 5, and a liquid storage mechanism 6.
- the heat source unit 10 is provided with an outdoor fan 3-m for supplying the outside air to the heat source side heat exchanger 3.
- the heat source unit 10 further includes a pump 51 and a heat medium sealing mechanism 54 provided in the load-side heat medium circuit 120.
- the heat source unit 10 is provided with a control device 91a that controls the primary side cycle and the secondary side cycle.
- the heat source unit 10 is provided with the pump 51, the intermediate heat exchanger 5, the heat medium sealing mechanism 54, and the pipes 61, 62 and 63.
- the pipe 61 is connected to the load side units 50-1 to 50-3 via the return pipe 65.
- the pipe 62 connects the pump 51 and the intermediate heat exchanger 5.
- the pipe 63 is connected to the load side units 50-1 to 50-3 via the forward pipe 64. The heat and cold generated in the primary side cycle are thermally transferred to the load side units 50-1 to 50-3 via the intermediate heat exchanger 5, the forward pipe 64, and the return pipe 65.
- the configuration provided in the heat source unit 10 will be described.
- the components provided in the load-side heat medium circuit 120 the components provided in the load-side units 50-1 to 50-3 will be described later.
- the refrigerant discharge port of the compressor 1 is connected to the four-way valve 2 via a discharge pipe 11.
- the refrigerant suction port of the compressor 1 is connected to the liquid storage mechanism 6 and the four-way valve 2 via a suction pipe 15.
- the heat source side heat exchanger 3 is connected to the four-way valve 2 via a gas side pipe 12.
- the heat source side heat exchanger 3 is connected to the expansion device 4 and the intermediate heat exchanger 5 via the liquid side pipe 13.
- the intermediate heat exchanger 5 is connected to the four-way valve 2 via a gas side pipe 14. Further, pipes 62 and 63 are connected to the intermediate heat exchanger 5.
- FIG. 3 is an enlarged view showing one configuration example of the heat medium sealing mechanism shown in FIG.
- the heat medium sealing mechanism 54 has a supply port 44, a discharge port 54-4, and an on-off valve 54-1 provided between the supply port 44 and the discharge port 54-4.
- the supply port 44, the discharge port 54-4 and the on-off valve 54-1 are provided in the pipe 61.
- the pipe 45 is connected to the supply port 44 of the pipe 61, and the pipe 45 is branched into a gas pipe 45a and a heat medium pipe 45b.
- a gas supply port 54-2 is provided in the gas pipe 45a, and a heat medium supply port 54-3 is provided in the heat medium pipe 45b.
- the gas supply port 54-2 is a supply port of the gas X to be replaced with the air in the load-side heat medium circuit 120.
- the heat medium supply port 54-3 is a heat medium supply port that flows into the load-side heat medium circuit 120.
- a gas valve 46 is provided in the gas pipe 45a.
- a heat medium valve 47 is provided in the heat medium pipe 45b.
- the exhaust port 54-4 exhausts the air and the gas X from the load side heat medium circuit 120.
- a discharge valve 48 is provided in the pipe leading to the discharge port 54-4.
- the on-off valve 54-1, the gas valve 46, the heat medium valve 47, and the discharge valve 48 are two-way valves.
- the heat medium circulating through the load side heat medium circuit 120 is water, antifreeze, or the like.
- the gas X is a gas that is more soluble in water than air. That is, the amount of gas X dissolved in water is larger than the amount of air dissolved in water. The details of the gas X will be described later.
- the case where the heat medium sealed in the load-side heat medium circuit 120 is water will be described.
- the on-off valve 54-1 functions as a backflow prevention device that prevents the gas X and water supplied from the supply port 44 from flowing out through the discharge port 54-4 without passing through the load-side heat medium circuit 120.
- the on-off valve 54-1 serves to make the flow of the gas X and water one direction in the heat medium sealing operation described later.
- thermometers 31 to 37, 81 and 82, and pressure gauges 41 and 42 are provided with thermometers 31 to 37, 81 and 82, and pressure gauges 41 and 42.
- the thermometer 31 is provided on the discharge pipe 11 on the refrigerant discharge side of the compressor 1.
- the thermometer 31 measures the discharge temperature of the refrigerant in the compressor 1.
- the thermometer 32 is provided on the suction pipe 15 on the refrigerant suction side of the compressor 1.
- the thermometer 32 measures the suction temperature of the refrigerant in the compressor 1.
- thermometer 33 is provided on the gas side pipe 12 of the heat source side heat exchanger 3.
- the thermometer 33 measures the temperature of the refrigerant on the gas side of the heat source side heat exchanger 3.
- the thermometer 34 is provided on the liquid side pipe 13 of the heat source side heat exchanger 3.
- the thermometer 34 measures the temperature of the refrigerant on the liquid side of the heat source side heat exchanger 3.
- a thermometer 35 is provided in the heat source unit 10. The thermometer 35 measures the temperature of the outside air taken in by the outdoor fan 3-m.
- the thermometer 36 is provided on the liquid side pipe 13 of the intermediate heat exchanger 5.
- the thermometer 36 measures the temperature of the refrigerant on the liquid side of the intermediate heat exchanger 5.
- the thermometer 37 is provided on the gas side pipe 14 of the intermediate heat exchanger 5.
- the thermometer 37 measures the temperature of the refrigerant on the gas side of the intermediate heat exchanger 5.
- the pressure gauge 41 is provided on the discharge pipe 11 on the refrigerant discharge side of the compressor 1.
- the pressure gauge 41 measures the discharge pressure of the refrigerant of the compressor 1.
- the pressure gauge 42 is provided on the suction pipe 15 on the refrigerant suction side of the compressor 1.
- the pressure gauge 42 measures the suction pressure of the refrigerant of the compressor 1.
- the thermometer 81 is provided in the pipe 62 of the intermediate heat exchanger 5.
- the thermometer 81 measures the temperature of the water flowing into the intermediate heat exchanger 5.
- the thermometer 82 is provided in the pipe 63 of the intermediate heat exchanger 5.
- the thermometer 82 measures the temperature of the water flowing out of the intermediate heat exchanger 5.
- FIG. 4 is a block diagram showing one configuration example of the control device shown in FIG.
- the control device 91a has a memory 95 for storing a program, and a CPU (Central Processing Unit) 96 for executing processing in accordance with the program.
- the control device 91a is connected to the thermometers 31 to 37, 81 and 82 by signal lines.
- the control device 91a is connected to the pressure gauges 41 and 42 by a signal line.
- the control device 91a is connected to the compressor 1, the outdoor fan 3-m, the four-way valve 2, and the pump 51 by signal lines.
- the control device 91a is connected to the open / close valve 54-1, the gas valve 46, the heat medium valve 47, and the discharge valve 48 by signal lines. The illustration of these signal lines in FIG. 1 is omitted.
- control device 91a is connected to each of the control units 91c-1 to 91c-3 provided in each of the load side units 50-1 to 50-3 by a signal line.
- control units 91c-2 and 91c-3 are not shown.
- the controller 91a controls the refrigeration cycle of the primary side cycle.
- the control device 91a receives the request for the heating operation from the control units 91c-1 to 91c-3
- the control device 91a controls the four-way valve 2 to connect the discharge piping 11 to the gas side piping 14 and the suction piping 15 for the gas side piping. Connect with 12
- the control device 91a causes the intermediate heat exchanger 5 to generate heat.
- the control device 91a receives a request for cooling operation from the control units 91c-1 to 91c-3
- the control device 91a controls the four-way valve 2 to connect the discharge pipe 11 to the gas side pipe 12 and the suction pipe 15 to the gas side pipe Connect with 14.
- the control device 91a causes the intermediate heat exchanger 5 to generate cold heat.
- the control device 91a controls the actuators including the compressor 1 and the expansion device 4 based on the measurement values obtained from the thermometers 31 to 37 and the measurement values obtained from the pressure gauges 41 and 42. Specifically, the control device 91a controls the operating frequency of the compressor 1 to adjust the capacity of the refrigeration cycle. Further, the control device 91 a controls the degree of opening of the expansion device 4 to adjust superheat and subcooling of the heat source side heat exchanger 3 and the intermediate heat exchanger 5.
- the control device 91a controls the heat medium sealing mechanism 54 when an instruction to seal water into the load-side heat medium circuit 120 is input after piping is performed. A specific example of control at the time of heat medium sealing will be described later.
- Each of the load side units 50-1 to 50-3 is installed at a position where air conditioning air can be supplied to an air conditioning target space such as a room.
- Each of the load side units 50-1 to 50-3 supplies cooling air to the air conditioning target space when cold energy is supplied from the heat source unit 10.
- Each of the load side units 50-1 to 50-3 supplies heating air to the air conditioning target space when the heating source is supplied with heat from the heat source unit 10. Since the load side units 50-1 to 50-3 have the same configuration, in the following, the configuration of the load side unit 50-1 will be described in detail, and the description of the configuration of the load side units 50-2 and 50-3 will be omitted.
- the control units 91c-1 to 91c-3 like the control device 91a, have a CPU and a memory (not shown).
- the load side unit 50-1 includes a load side heat exchanger 52c-1, an indoor fan 52c-1m, and a controller 91c-1.
- a flow control valve 53c-1 is provided on the water inflow side of the load side heat exchanger 52c-1.
- the flow control valve 53c-1 adjusts the flow rate of water flowing into the load-side heat exchanger 52c-1.
- the load side unit 50-1 is provided with an indoor fan 52c-1m that sucks in air from the air conditioning target space and supplies the air to the load side heat exchanger 52c-1.
- a thermometer 84c-1 for measuring the temperature of water is provided on the water inflow side of the load-side heat exchanger 52c-1.
- a thermometer 83c-1 for measuring the temperature of water is provided on the water outflow side of the load side heat exchanger 52c-1.
- the load side unit 50-1 is provided with a thermometer 85c-1 that measures the temperature of the air in the air conditioning target space.
- the control unit 91c-1 is connected to the indoor fan 52c-1m, the flow control valve 53c-1, the thermometers 83c-1, 84c-1, and 85c-1 by signal lines.
- the control unit 91c-1 transmits information on the driving condition to the control device 91a when an instruction on the driving condition is input from the user.
- the control unit 91c-1 controls the number of rotations of the indoor fan 52c-1m and the flow rate control valve 53c based on the set temperature and the set humidity and the measurement values acquired from the thermometers 83c-1, 84c-1 and 85c-1. Control the opening of -1.
- control device 91a performs the heating operation in the primary side cycle.
- the control device 91a controls the four-way valve 2 to connect the discharge piping 11 to the gas side piping 14 and the suction piping 15 for the gas side piping. Connect with 12
- the high-temperature and high-pressure refrigerant discharged from the compressor 1 flows into the intermediate heat exchanger 5.
- the intermediate heat exchanger 5 functions as a condenser.
- the high temperature and high pressure refrigerant exchanges heat with the water circulating in the load side heat medium circuit 120 in the intermediate heat exchanger 5.
- the water exchanges heat with the refrigerant to become hot water.
- the hot water is sent by the pump 51 to the load side units 50-1 to 50-3.
- the hot water reaches the load side heat exchangers 52c-1 to 52c-3, it exchanges heat with the indoor air supplied by the indoor fans 52c-1m to 52c-3m to warm the room.
- control device 91a performs the cooling operation in the primary side cycle.
- the control device 91a controls the four-way valve 2 to connect the discharge pipe 11 to the gas side pipe 12 and the suction pipe 15 to the gas side pipe Connect with 14.
- the high temperature and high pressure refrigerant discharged from the compressor 1 flows into the heat source side heat exchanger 3.
- the heat source side heat exchanger 3 functions as a condenser.
- the high-temperature and high-pressure refrigerant exchanges heat with the outside air in the heat source side heat exchanger 3 to become a medium-temperature and high-pressure refrigerant.
- the medium-temperature and high-pressure refrigerant is decompressed by the expansion device 4 and becomes a low-temperature and low-pressure refrigerant.
- the low temperature and low pressure refrigerant flows into the intermediate heat exchanger 5.
- the intermediate heat exchanger 5 functions as an evaporator.
- the low-temperature low-pressure refrigerant exchanges heat with water circulating in the load-side heat medium circuit 120 in the intermediate heat exchanger 5. In the intermediate heat exchanger 5, the water exchanges heat with the refrigerant to become cold water.
- the cold water is sent by the pump 51 to the load side units 50-1 to 50-3.
- the cold water reaches the load side heat exchangers 52c-1 to 52c-3, it exchanges heat with the indoor air supplied by the indoor fans 52c-1m to 52c-3m to cool the room.
- the heat source unit 10 and the load side units 50-1 to 50-3 are arranged at a place designed as an air conditioner. Subsequently, the forward piping 64 and the return piping 65 are connected to the heat source unit 10.
- the first connection pipes 64c-1 to 64c-3 are connected to the forward pipe 64.
- the second connection pipes 65 c-1 to 65 c-3 are connected to the return pipe 65. In this manner, the load side units 50-1 to 50-3 are connected in parallel to the heat source unit 10.
- FIG. 5 is a flow chart showing a procedure for sealing water in the load side heat medium circuit in the air conditioning system according to the first embodiment of the present invention.
- a cylinder of gas X not shown, is connected to the gas supply port 54-2. Further, a tap water supply pipe not shown in the figure is connected to the heat medium supply port 54-3.
- the gas valve 46, the heat medium valve 47 and the on-off valve 54-1 are closed, and the discharge valve 48 is open.
- Each of the flow control valves 53c-1 to 53c-3 is fully opened.
- the control device 91a executes the process according to the procedure shown in FIG. 5 when an instruction to enclose water in the load-side heat medium circuit 120 is input.
- step S1 shown in FIG. 5 the control device 91a controls the gas valve 46 and the on-off valve 54-1 to replace the air in the load-side heat medium circuit 120 with the gas X. Specifically, the control device 91a supplies the gas X to the load-side heat medium circuit 120 by switching the gas valve 46 from the closed state to the open state while maintaining the on-off valve 54-1 in the closed state. The controller 91a determines whether the air in the load-side heat medium circuit 120 has been replaced by the gas X (step S2).
- the controller 91a continues the supply of the gas X until the process of displacing air into the gas X is completed, and when the process of displacing air from the gas X is completed, the process proceeds to the next step S3.
- the process of replacing the air in the load-side heat medium circuit 120 with the gas X is referred to as a first replacement process.
- the gas X is a gas which is more soluble in water than air in a gas state at ambient temperature of about 0 ° C. to 50 ° C. and atmospheric pressure.
- the gas X is a gas having a smaller Henry's constant than air.
- the gas X is, for example, a gas such as carbon dioxide, ammonia, hydrogen chloride, chlorine and hydrogen sulfide.
- the gas X may leak into the atmosphere. Therefore, it is desirable that the gas X is a gas that is not only easily available but also has a small impact on the environment and is also less harmful to the human body, such as carbon dioxide.
- a mechanism for recovering air and gas X such as a recovery cylinder, may be provided at the outlet 54-4. If the gas X is carbon dioxide, the outlet 54-4 may be open to the atmosphere.
- FIG. 6 is a view schematically showing the load-side heat medium circuit shown in FIG.
- the load-side heat medium circuit 120 is shown in a simple piping configuration, but in addition to the piping, the reference numerals of the configuration that becomes the flow path resistance are shown.
- FIG. 7 is a graph showing the relationship between the distance from the supply port and the concentration of gas X in the load-side heat medium circuit shown in FIG.
- the horizontal axis of FIG. 7 indicates the distance x from the supply port 44, and the vertical axis indicates the concentration of the gas X.
- the vertical axis in FIG. 7 indicates 1 when the ratio of gas X occupied per unit volume is 100%.
- the controller 91a closes the on-off valve 54-1 so that the flow of the gas X is in one direction, and then the gas X is supplied from the gas supply port 54-2. It flows into the load side heat medium circuit 120. Thereby, as shown in FIG. 6, the gas X is supplied from the gas supply port 54-2 to the pipes 61 and 62, the intermediate heat exchanger 5, the pipe 63, the forward pipe 64, and the load side units 50-1 to 50-3. And flow back to the pipe 61 via the return pipe 65.
- the concentration distribution after time t [sec] has elapsed since the supply of the gas X is started is as shown in FIG.
- the flow control valves 53c-1 to 53c-3 are in an open state so that the gas X can push out the air.
- the flow path resistance can be further reduced by fully opening the flow control valves 53c-1 to 53c-3.
- each of the flow control valves 53c-1 to 53c-3 By making each of the flow control valves 53c-1 to 53c-3 fully open, the flow resistance of each flow control valve can be further reduced, but the opening of each flow control valve is limited to the case of full opening. Absent.
- the flow control valves 53c-1 to 53c-1 are arranged so that the time from the supply start of the gas X to the gas X divided into the first connection pipes 64c-1 to 64c-3 merges with the return pipe 65. It is conceivable to adjust the opening degree of each valve of 53c-3. Specific examples will be described below.
- each piping When piping the load side heat medium circuit 120, the worker connects the forward piping 64 and the first connection piping 64c-1 to 64c-3, the return piping 65 and the second connection piping 65c-1 to 65c-.
- the length and the cross-sectional area of each piping can be grasped about 3. Further, the relationship between the opening degree of each of the flow control valves 53c-1 to 53c-3 and the flow rate of the gas X can be obtained in advance from the specification of these control valves.
- the operator inputs the information on the length and the cross-sectional area of each of the above-mentioned pipes and the information indicating the relationship between the opening degree of the flow control valves 53c-1 to 53c-3 and the flow rate of the gas X to the control device 91a. .
- the control device 91a calculates the flow path resistance of each pipe according to the determined flow path resistance model from the length and the cross-sectional area of each pipe.
- the control device 91a determines the flow of the gas X divided into the first connection pipes 64c-1 to 64c-3 to the return pipe 65 based on the flow path resistance of each pipe and the relationship between the opening degree and the flow rate of the gas X.
- the opening degree of each flow control valve is set so that the deviation of the arrival time does not exceed the determined range.
- the flow control valves 53c-1 to 53c-3 are opened so that the time for replacing air with the gas X in each branch pipe of the first connection pipes 64c-1 to 64c-3 matches.
- the degree By adjusting the degree, the replacement process can be completed in a short time.
- the operator should know the volume of the piping of the load-side heat medium circuit 120 at the time of piping installation, so the piping volume of the load-side heat medium circuit 120 is input to the control device 91 a.
- the control device 91a obtains the replacement time based on the piping volume of the load-side heat medium circuit 120 and the inflow rate of the gas X.
- the control device 91a sets a time when (inflow volume / (pipe volume + mixed bed volume))> 1 as the replacement time.
- the mixed bed volume is represented by (length L) ⁇ (pipe cross-sectional area).
- the mixed layer is defined as a range in which the concentration of gas X is larger than 0 and smaller than 1.
- the value serving as a guideline for the upper limit is not limited to 1. It is an ideal case that the inside of the pipe completely changes from air to gas X, and it is conceivable that the case does not completely change. Even if air remains in part of the piping of the load-side heat medium circuit 120, if the air mass due to the remaining air does not cause a problem, considering the work efficiency, a value that becomes an indication of the upper limit is, for example , 0.99.
- FIG. 8 is a diagram showing that the pipe shape disturbs the flow of gas in the T-shaped tube.
- FIG. 9 is a diagram showing that the pipe shape disturbs the flow of gas in the L-shaped tube.
- FIG. 8 shows, as an example of a T-shaped pipe, an enlarged view of a portion where the forward piping 64 and the first connection piping 64c-1 are connected.
- FIG. 9 shows an enlarged part of the return pipe 65 as an example of the L-shaped pipe.
- the centrifugal force acting on the air flow generates a secondary flow, causing separation of the air flow and a stagnation point of the air flow.
- the flow rate of the gas X is limited by molecular diffusion at the stagnation point, and the length L of the mixed layer becomes long. In other words, the displacement time for the gas X to expel the air may be long.
- a pressure regulator not shown is provided in advance in a cylinder of gas X.
- the pressure control valve of the pressure regulator is connected to the control device 91a by a signal line.
- the controller 91a starts supplying the gas X to the load-side heat medium circuit 120 after opening the pressure control valve to the determined opening degree. Thereafter, the controller 91a changes the degree of opening of the pressure control valve at regular intervals. In this manner, the supply pressure of the gas X can be varied in the first replacement step.
- the first replacement step it is conceivable to set the supply pressure of the gas X such that the average flow velocity of the gas X in the load-side heat medium circuit 120 is larger than the diffusion rate of air to the gas X.
- the method using the above-described pressure regulator may be applied. If the average flow velocity of the gas X in the load-side heat medium circuit 120 is larger than the diffusion velocity of air to the gas X, the pressure difference between the gas supply port 54-2 and the discharge port 54-4 becomes large. As a result, the air in the load-side heat medium circuit 120 can be easily expelled from the exhaust port 54-4.
- the gas may flow into the load-side heat medium circuit 120 at a pressure higher than the atmospheric pressure. Even in this case, since the pressure of the gas supply port 54-2 becomes larger than that of the discharge port 54-4, the air in the load-side heat medium circuit 120 can be easily expelled from the discharge port 54-4.
- the time for replacing the air with the gas X is shortened.
- a pressure regulator to increase the supply pressure of the gas X.
- the source pressure of the gas X is low
- a configuration for increasing the supply pressure of the gas X is required. Therefore, the operator may determine the optimum supply pressure and configuration by comparing the time for replacing the air with the gas X with the difficulty of the configuration for increasing the supply pressure of the gas X.
- step S3 shown in FIG. 5 the controller 91a controls the gas valve 46 and the heat medium valve 47 to replace the gas X in the load side heat medium circuit 120 with water. Specifically, the controller 91 a switches the gas valve 46 from the open state to the closed state, switches the heat medium valve 47 from the closed state to the open state, and supplies water to the load-side heat medium circuit 120. The controller 91a determines whether the gas X in the load-side heat medium circuit 120 has been replaced by water (step S4).
- the control device 91a continues the supply of water until the replacement process from gas X to water ends, and when it is determined that the replacement process from gas X to water ends, the water sealing process ends.
- the process of replacing the gas X in the load-side heat medium circuit 120 with water is referred to as a second replacement process.
- the second replacement step water is supplied from the heat medium supply port 54-3 to the load-side heat medium circuit 120.
- the water accumulates in the load-side heat medium circuit 120 while pushing the gas X out of the discharge port 54-4.
- the density difference between the gas X and water and the surface tension of the gas X and water at that high location Gas X may remain.
- the gas X since the gas X has high solubility in water, it is easily absorbed by water even if it remains in the pipe. Therefore, the gas X in the piping can be removed by continuously supplying water to the load-side heat medium circuit 120 from the gas supply port 54-2.
- the amount of water used for the replacement of the second replacement step is considered. Although it is necessary to supply a minimum amount of water capable of removing water containing gas X into the piping, it is necessary to prevent the use of too much water. Therefore, the control device 91a discharges the gas X from the load-side heat medium circuit 120 while suppressing the amount of water used as follows.
- the control device 91 a closes the heat medium valve 47 when water corresponding to the entire volume of the piping of the load side heat medium circuit 120 is supplied to the load side heat medium circuit 120.
- the water supply amount is calculated by multiplying the water supply amount per unit time by the supply time.
- the controller 91a opens the on-off valve 54-1.
- the control device 91a activates the pump 51 to execute the circulation mode in which the water is circulated to the load-side heat medium circuit 120.
- the control device 91a starts the heating operation in the heat source side refrigerant circuit 110.
- the intermediate heat exchanger 5 When the heating operation is performed in the primary side cycle, the intermediate heat exchanger 5 is heated.
- the water circulating in the load-side heat medium circuit 120 is heated as it passes through the intermediate heat exchanger 5, and the gas X tends to be easily degassed from the water. Every time the heated water passes near the outlet 54-4, the gas X is exhausted from the outlet 54-4.
- an open valve that discharges the gas X from the inside of the piping may be provided at a position where the piping position is higher than the position of the surrounding piping.
- the water flow may be changed.
- a method of changing the water flow there is a method such as fluctuating the water supply pressure. Changing the water flow disrupts the interface and reduces the thickness of the concentration boundary layer. As a result, absorption of the gas X into water is promoted. Changing the water flow is effective in promoting absorption of the gas X into water.
- the above-described replacement process including the first replacement step and the second replacement step is a water conditioning system different from the direct expansion type, in which resin-made equipment is often used to prevent water remaining in water piping as much as possible. Can be enclosed.
- the gas X supply port and the water supply port are separately provided.
- the gas X supply port and the water supply port may be common.
- the gas X and water are supplied from the supply port 44 and the gas X is discharged from the discharge port 54-4, the present invention is not limited to this case.
- the discharge port 54-4 may be a water supply port
- the supply port 44 may be a water and gas X discharge port.
- the gas pipe 45a and the heat medium pipe 45b are branched from the pipe 45 in FIGS. 1 and 3, the gas pipe 45a and the heat medium pipe 45b may be directly connected to the pipe 61, respectively.
- the control device 91a performs the first replacement step and the second replacement step after the operator performs piping work.
- the first replacement step the air staying in the piping of the load-side heat medium circuit 120 is replaced with the gas X.
- the gas X enclosed in the piping of the load-side heat medium circuit 120 is replaced with water.
- the air in the pipe is replaced with the gas X in the first replacement step, when the water is supplied in the second replacement step, the air in the pipe remains.
- the amount can be reduced as much as possible.
- the second replacement step even if the gas X remains in the pipe, the formation of a large block such as an air block is suppressed in the pipe. As a result, the flow path resistance due to the gas lump is reduced, and the heat transport efficiency of the load side heat medium circuit 120 is improved.
- the control device 91a controls the heat medium sealing mechanism 54 to refer to FIG. Perform the replacement process described above. As a result, not only the heat medium is sealed in the load-side heat medium circuit 120 but also human errors can be prevented while the remaining amount of air is reduced as much as possible.
- the heat medium sealing mechanism 54 in the load side heat medium circuit 120 includes the heat medium and gas X supply port 44, the gas X discharge port 54-4, and the supply port. It has an on-off valve 54-1 provided between the valve 44 and the discharge port 54-4.
- the gas X when the heat medium is sealed in the load-side heat medium circuit 120, the gas X is supplied while pushing out the air in the pipe from the supply port 44, and then the heat medium is piped from the supply port 44. It is supplied while extruding the gas X inside. Before the heat medium is enclosed in the load side heat medium circuit 120, the gas X is enclosed in the pipe while pushing out the air, so that even if the gas X remains in the pipe, a large lump such as an air lump Is suppressed in the pipe. As a result, the flow path resistance due to the gas lump is reduced, and the heat transport efficiency of the load side heat medium circuit 120 is improved. Also, pump failure and pipe corrosion due to large air masses are suppressed.
- the first embodiment does not need to apply a large pressure when sealing the heat medium in the load-side heat medium circuit 120, it is effective for a water air conditioning system in which resin equipment different from direct expansion type is used. It is. Furthermore, it is not necessary to provide an air vent valve in a refraction pipe or the like in which an air mass is easily formed.
- the air conditioning system of the second embodiment has a configuration in which a check valve is provided as a backflow prevention device in load side heat medium circuit 120.
- FIG. 10 is a refrigerant circuit diagram showing one configuration example of the air conditioning system according to Embodiment 2 of the present invention.
- the detailed description of the same configuration as that of the first embodiment is omitted, and the difference from the first embodiment will be described in detail.
- the heat medium sealing mechanism 54 in the air conditioning system 101 has a check valve 54-6 instead of the on-off valve 54-1 shown in FIG.
- the check valve 54-6 allows the flow from the discharge port 54-4 to the supply port 44 in the load-side heat medium circuit 120, but the flow from the supply port 44 to the discharge port 54-4 Is a valve that blocks
- the pump 51 is provided in the pipe 61 between the heat medium sealing mechanism 54 and the return pipe 65.
- the same effect as that of the first embodiment can be obtained. Further, in the second embodiment, piping is performed from the supply port 44 in the first replacement step without controlling the opening and closing of the on-off valve 54-1 before the control device 91a starts the procedure shown in FIG. It is possible to prevent the gas X which has entered from being exhausted immediately from the exhaust port 54-4. As a result, it is possible to eliminate switching errors in opening and closing of the on-off valve 54-1 in the replacement operation.
- the air conditioning system of the third embodiment has a configuration in which a gas-liquid separation mechanism is provided as a backflow prevention device in the load-side heat medium circuit 120.
- FIG. 11 is a refrigerant circuit diagram showing one configuration example of the air conditioning system according to Embodiment 3 of the present invention.
- the third embodiment the detailed description of the same configuration as that of the first embodiment is omitted, and the difference from the first embodiment will be described in detail.
- the heat medium sealing mechanism 54 in the air conditioning system 102 has a gas-liquid separation mechanism 54-5 as a backflow prevention device instead of the on-off valve 54-1 shown in FIG.
- the gas-liquid separation mechanism 54-5 is a container for separating gas and liquid.
- the gas-liquid separation mechanism 54-5 is provided in the pipe 61.
- the discharge port 54-4 is connected to the pipe 61 via the gas-liquid separation mechanism 54-5.
- the pump 51 is provided between the supply port 44 and the gas-liquid separation mechanism 54-5.
- the gas X when the heat medium returned from the load side units 50-1 to 50-3 enters the gas-liquid separation mechanism 54-5 in the circulation mode, the gas X is separated from the heat medium and the discharge port It is discharged from 54-4. Even if air remains in the heat medium, the air is separated from the heat medium by the gas-liquid separation mechanism 54-5 and is discharged from the discharge port 54-4.
- the gas-liquid separation mechanism 54-5 may be provided with a heating device.
- the heating device in the second replacement step of steps S3 to S4 shown in FIG. 5, the heating device can heat and gasify the gas X dissolved in the heat medium, and the gas X can be discharged from the discharge port 54-4.
- the air conditioning system of the fourth embodiment has a configuration in which a relay is provided between the heat source unit 10 and the load side units 50-1 to 50-3.
- FIG. 12 is a diagram showing an exemplary configuration of an air conditioning system according to Embodiment 4 of the present invention.
- the detailed description of the same configuration as that of the first embodiment is omitted, and the difference from the first embodiment will be described in detail.
- the air conditioning system 103 has a relay unit 150.
- the relay unit 150 is provided between the heat source unit 10 and the load side units 50-1 to 50-3.
- the relay unit 150 includes an intermediate heat exchanger 5, a heat medium sealing mechanism 54, a pump 51, and pipes 61 to 63.
- the relay unit 150 is installed at a position closer to the load side units 50-1 to 50-3 than the heat source unit 10.
- the lengths of the forward pipe 64 and the return pipe 65 are longer. Becomes shorter.
- thermometers 36, 37, 81 and 82 shown in FIG. 1 are not shown in FIG.
- the air conditioning system 103 performs heat transfer from the heat source unit 10 to the relay unit 150 with the refrigerant, and the relay unit 150 exchanges heat with water to exchange heat with the refrigerant. Heat transport to loading side units 50-1 to 50-3 with water.
- the fourth embodiment can reduce the amount of the heat medium sealed in the load-side heat medium circuit 120 compared to the first embodiment. As a result, the amount of air and gas X remaining in the load side heat medium circuit 120 can be reduced. Further, the amount of heat transfer medium required can be reduced, and if the density of the heat transfer medium changes according to the temperature change of the heat transfer medium, the volume of the expansion tank for storing the heat transfer medium can be reduced.
- the number of load side units is not limited to three.
- the number of intermediate heat exchangers 5 is one has been described, the number of intermediate heat exchangers 5 is not limited to one.
- a plurality of intermediate heat exchangers 5 may be provided as long as the heat medium can be cooled and heated.
- FIG. 13 is a diagram showing another example of the load-side heat medium circuit in the heat source unit shown in FIG.
- the illustration of the configuration of the heat source side refrigerant circuit 110 is omitted.
- a bypass circuit 161 is provided in parallel with the intermediate heat exchanger 5.
- the bypass circuit 161 is provided with a valve 162 for capacity adjustment.
- the valve 162 is controlled in the opening degree when the capacity is excessive, and serves to adjust the load.
- the heat medium is also enclosed in the bypass circuit 161.
- the backflow prevention device has a function as a rectifying device that performs circuit connection so that the gas X or the heat medium flows from the supply port 44 to the discharge port 54-4 when the gas X is supplied and when the heat medium is supplied. Just do it.
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Abstract
Description
実施の形態1.
本実施の形態1の空調システムの構成の概要を説明する。図1は、本発明の実施の形態1に係る空調システムの一構成例を示す冷媒回路図である。図2は、図1に示した空調システムの設置例を示す図である。本実施の形態1では、空調システム100が、冷凍サイクルを利用して冷熱および温熱を生成する一次側サイクルと、一次側サイクルで生成された冷熱および温熱を熱輸送する二次側サイクルとを行う冷凍空調機器の場合で説明する。
熱源機10は、通常、ビル等の建物の外の空間に配置され、負荷側ユニット50-1~50-3に冷熱および温熱を供給する。建物の外の空間とは、屋上などである。図2は、熱源機10がビルの屋上に設置された場合を示す。ただし、熱源機10が設置される場所は、室外に限らない。熱源機10は、例えば、天井裏および換気口付の機械室等の囲まれた空間に設置されてもよい。熱源機10は、排気ダクトで廃熱を建物の外に排気できれば、建物の内部に設置してもよい。水冷式の熱源側熱交換器を用いて、熱源機10を建物の内部に設置してもよい。外気と熱交換ができれば、熱源機10はどのような場所に設置されていてもよい。
負荷側ユニット50-1~50-3のそれぞれは、室内などの空調対象空間に空調空気を供給できる位置に設置されている。負荷側ユニット50-1~50-3のそれぞれは、熱源機10から冷熱が供給されると、空調対象空間に冷房空気を供給する。負荷側ユニット50-1~50-3のそれぞれは、熱源機10から温熱が供給されると、空調対象空間に暖房空気を供給する。負荷側ユニット50-1~50-3は同様な構成であるため、以下では、負荷側ユニット50-1の構成を詳しく説明し、負荷側ユニット50-2および50-3の構成の説明を省略する。制御部91c-1~91c-3は、制御装置91aと同様に、図に示さないCPUおよびメモリを有する。
[暖房運転]
制御装置91aは、制御部91c-1~91c-3から暖房運転の要求を受け付けると、四方弁2を制御して、吐出配管11をガス側配管14と接続させ、吸入配管15をガス側配管12と接続させる。圧縮機1から吐出した高温高圧の冷媒は、中間熱交換器5に流入する。中間熱交換器5は凝縮器として機能する。高温高圧の冷媒は、中間熱交換器5において、負荷側熱媒体回路120を循環する水と熱交換を行う。中間熱交換器5において、水は冷媒と熱交換を行うことで温水になる。温水は、ポンプ51により負荷側ユニット50-1~50-3に送り届けられる。温水は、負荷側熱交換器52c-1~52c-3に到達すると、室内ファン52c-1m~52c-3mが供給する室内空気と熱交換して、室内を温める。
続いて、制御装置91aが、一次側サイクルにおいて、冷房運転を行う場合を説明する。制御装置91aは、制御部91c-1~91c-3から冷房運転の要求を受け付けると、四方弁2を制御して、吐出配管11をガス側配管12と接続させ、吸入配管15をガス側配管14と接続させる。圧縮機1から吐出した高温高圧の冷媒は、熱源側熱交換器3に流入する。熱源側熱交換器3は凝縮器として機能する。高温高圧の冷媒は、熱源側熱交換器3において、外気と熱交換を行って中温高圧の冷媒となる。中温高圧の冷媒は、絞り装置4で減圧し、低温低圧の冷媒になる。低温低圧の冷媒は、中間熱交換器5に流入する。中間熱交換器5は蒸発器として機能する。低温低圧の冷媒は、中間熱交換器5において、負荷側熱媒体回路120を循環する水と熱交換を行う。中間熱交換器5において、水は冷媒と熱交換を行うことで冷水になる。冷水は、ポンプ51により負荷側ユニット50-1~50-3に送り届けられる。冷水は、負荷側熱交換器52c-1~52c-3に到達すると、室内ファン52c-1m~52c-3mが供給する室内空気と熱交換して、室内を冷やす。
熱源機10および負荷側ユニット50-1~50-3は、空調設備として設計された場所に配置される。続いて、熱源機10に往き配管64および戻り配管65が接続される。そして、往き配管64に第1の接続配管64c-1~64c-3が接続される。戻り配管65に第2の接続配管65c-1~65c-3が接続される。このようにして、熱源機10に負荷側ユニット50-1~50-3が並列に接続される。
図5は、本発明の実施の形態1の空調システムにおいて、負荷側熱媒体回路に水を封入する手順を示すフローチャートである。図に示さない、気体Xのボンベが、ガス供給口54-2に接続されている。また、図に示さない、水道水の供給配管が、熱媒体供給口54-3に接続されている。初期状態として、ガス弁46、熱媒体弁47および開閉弁54-1は閉状態であり、排出弁48は開状態であるものとする。流量制御弁53c-1~53c-3のそれぞれの開度は全開状態とする。制御装置91aは、負荷側熱媒体回路120への水の封入の指示が入力されると、図5に示す手順にしたがって処理を実行する。
本実施の形態2の空調システムは、負荷側熱媒体回路120における逆流防止装置として、逆止弁が設けられた構成である。
本実施の形態3の空調システムは、負荷側熱媒体回路120における逆流防止装置として、気液分離機構が設けられた構成である。
本実施の形態4の空調システムは、熱源機10と負荷側ユニット50-1~50-3との間に中継機が設けられた構成である。
Claims (12)
- 熱源側熱交換器が設けられた熱源側冷媒回路と、
負荷側熱交換器が設けられた負荷側熱媒体回路と、
前記熱源側冷媒回路と前記負荷側熱媒体回路との間で熱交換する中間熱交換器と、
前記負荷側熱媒体回路に設けられ、該負荷側熱媒体回路に熱媒体が供給される熱媒体封入機構と、
を有し、
前記熱媒体封入機構は、
前記負荷側熱媒体回路に接続され、前記熱媒体と、該熱媒体に対して空気よりも溶けやすい気体とが流入する供給口と、
前記負荷側熱媒体回路に接続され、前記熱媒体に押されて前記気体が排出される排出口と、
前記気体の供給時、および前記熱媒体の供給時に、前記気体または前記熱媒体が前記供給口から前記排出口に流動するように回路接続する整流装置と、
を有する空調システム。 - 前記整流装置は、
前記供給口と前記排出口との間の前記負荷側熱媒体回路に設けられ、前記気体および前記熱媒体が、前記供給口から前記中間熱交換器を経由せずに、前記供給口から前記排出口に流出することを防止する逆流防止装置である、請求項1に記載の空調システム。 - 前記逆流防止装置は、前記気体を前記熱媒体から分離し、分離した気体を前記排出口から排出させる気液分離機構である、請求項2に記載の空調システム。
- 前記供給口として設けられた、前記気体が供給されるガス配管および前記熱媒体が供給される熱媒体配管と、
前記ガス配管に設けられたガス弁と、
前記熱媒体配管に設けられた熱媒体弁と、
前記ガス弁および前記熱媒体弁と信号線で接続され、該ガス弁および該熱媒体弁の開閉を制御する制御装置とをさらに有し、
前記制御装置は、
前記ガス弁を開状態にして、前記気体が前記排出口から排出されるまで該気体を前記負荷側熱媒体回路に供給し、
前記負荷側熱媒体回路に前記気体が封入されると、前記ガス弁を開状態から閉状態に切り替え、前記熱媒体弁を開状態にして、前記熱媒体を該負荷側熱媒体回路に供給し、
前記負荷側熱媒体回路に前記熱媒体が封入されると、前記熱媒体弁を開状態から閉状態に切り替える、請求項1~3のいずれか1項に記載の空調システム。 - 前記負荷側熱媒体回路に並列に接続される複数の前記負荷側熱交換器が設けられた複数の負荷側ユニットをさらに有し、
前記複数の負荷側ユニットのそれぞれは、前記負荷側熱交換器と、該負荷側熱交換器に流れ込む前記気体の流量を制御する流量制御弁とを有し、
前記制御装置は、
前記負荷側熱媒体回路に前記気体を供給する際、複数の前記流量制御弁を開状態にする、請求項4に記載の空調システム。 - 前記制御装置は、
前記負荷側熱媒体回路への前記気体の供給を開始した時から、前記複数の負荷側熱交換器に分流した該気体が該負荷側熱媒体回路の戻り配管に到達するまでの各時間のずれが決められた範囲を超えないように、複数の前記流量制御弁の開度を調節する、請求項5に記載の空調システム。 - 前記気体は、二酸化炭素である、請求項1~6のいずれか1項に記載の空調システム。
- 熱源側熱交換器を含む熱源側冷媒回路と、負荷側熱交換器、供給口、排出口、および該供給口と該排出口との間に設けられた整流装置を含む負荷側熱媒体回路と、前記熱源側冷媒回路と該負荷側熱媒体回路との間で熱交換する中間熱交換器とを有する空調システムにおける、前記負荷側熱媒体回路への熱媒体封入方法であって、
熱媒体に対して空気よりも溶けやすい気体が前記負荷側熱媒体回路に封入されるまで、前記供給口から該気体を該負荷側熱媒体回路に供給して空気を前記排出口から排出する第1置換工程と、
前記負荷側熱媒体回路に前記気体が封入されると、前記熱媒体が該負荷側熱媒体回路に封入されるまで、前記供給口から該熱媒体を該負荷側熱媒体回路に供給する第2置換工程と、
を有する熱媒体封入方法。 - 前記第1置換工程において、大気圧よりも高い圧力で前記気体が前記負荷側熱媒体回路に流入する、請求項8に記載の熱媒体封入方法。
- 前記第1置換工程において、前記負荷側熱媒体回路内における前記気体の平均流速が、該気体に対する空気の拡散速度よりも速くなるように、該気体が該負荷側熱媒体回路に流入される、請求項8または9に記載の熱媒体封入方法。
- 前記第1置換工程において、前記気体の供給圧力が変動する、請求項8~10のいずれか1項に記載の熱媒体封入方法。
- 前記第2置換工程において、前記熱源側冷媒回路で暖房運転することで、前記熱媒体が前記負荷側熱媒体回路から脱気する、請求項8~11のいずれか1項に記載の熱媒体封入方法。
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