WO2022224689A1 - 冷凍式チラー - Google Patents
冷凍式チラー Download PDFInfo
- Publication number
- WO2022224689A1 WO2022224689A1 PCT/JP2022/013819 JP2022013819W WO2022224689A1 WO 2022224689 A1 WO2022224689 A1 WO 2022224689A1 JP 2022013819 W JP2022013819 W JP 2022013819W WO 2022224689 A1 WO2022224689 A1 WO 2022224689A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- temperature
- coolant
- load
- refrigerant
- target temperature
- Prior art date
Links
- 239000002826 coolant Substances 0.000 claims abstract description 75
- 238000005057 refrigeration Methods 0.000 claims abstract description 23
- 239000003507 refrigerant Substances 0.000 claims description 86
- 239000000110 cooling liquid Substances 0.000 claims description 36
- 238000001816 cooling Methods 0.000 claims description 9
- 239000007788 liquid Substances 0.000 claims description 9
- 238000010438 heat treatment Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000007423 decrease Effects 0.000 description 3
- 235000013405 beer Nutrition 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000032683 aging Effects 0.000 description 1
- 239000003990 capacitor Substances 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000000855 fermentation Methods 0.000 description 1
- 230000004151 fermentation Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000004043 responsiveness Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 239000011550 stock solution Substances 0.000 description 1
Images
Classifications
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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
- 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
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or 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
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D23/00—Control of temperature
- G05D23/19—Control of temperature characterised by the use of electric means
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D23/00—Control of temperature
- G05D23/19—Control of temperature characterised by the use of electric means
- G05D23/1917—Control of temperature characterised by the use of electric means using digital means
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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
- 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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
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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
- 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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
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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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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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
- F25B2700/191—Pressures near an expansion valve
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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
- F25B2700/2115—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
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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
- F25B2700/2115—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
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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
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
Definitions
- the present invention relates to a refrigeration chiller that adjusts the temperature of a load by supplying temperature-controlled coolant to the load.
- Refrigeration chillers or coolant circulation devices that keep the temperature of a load constant by supplying a temperature-regulated coolant to the load are known, for example, as described in US Pat.
- This known coolant circulation system includes a coolant circuit that supplies coolant to a load, a refrigeration circuit that adjusts the temperature of the coolant through heat exchange between the coolant and the coolant, and a circuit that connects the coolant and the coolant. and a heat exchanger for heat exchange.
- the refrigeration circuit includes a compressor that compresses the refrigerant, a condenser that cools the high-temperature refrigerant discharged from the compressor, and a first electronic expansion valve that sends the low-temperature refrigerant sent from the condenser to the heat exchanger.
- the temperature of the cooling liquid is maintained at a constant temperature suitable for cooling or heating the load, and the cooling liquid The temperature of the load is kept constant by cooling or heating the load.
- the known cooling liquid circulation system is suitable for cooling or heating the load. Since it is configured to keep the temperature of the load constant by keeping the temperature constant, it cannot be immediately applied to usage in which the temperature of the load is gradually changed, and some improvement is required to apply it. I needed to do it.
- a technical problem of the present invention is to provide a refrigeration chiller suitable for gradually changing the temperature of the load to the target temperature over a certain period of time.
- a refrigeration chiller includes a cooling liquid circuit that supplies temperature-controlled cooling liquid to a load, and adjusts the temperature of the cooling liquid by heat exchange between the cooling liquid and refrigerant.
- a calculation unit that calculates the gradient of the temperature change as a target temperature gradient from the It is characterized by having a part.
- the refrigeration circuit includes a compressor that compresses refrigerant, a condenser that cools high-temperature refrigerant discharged from the compressor, and a first refrigerant that sends low-temperature refrigerant sent from the condenser to the heat exchanger.
- an electronic expansion valve and a second electronic expansion valve for sending high-temperature refrigerant discharged from the compressor to the heat exchanger, wherein the control unit divides the adjustment time into a plurality of time zones, For each zone, the current target temperature in the time zone is calculated from the target temperature gradient and the elapsed time in the time zone, and the current target temperature is compared with the current temperature of the coolant measured by the temperature sensor.
- the temperature of the refrigerant supplied to the heat exchanger is adjusted by adjusting the opening degrees of the first electronic expansion valve and the second electronic expansion valve based on the comparison result.
- a refrigeration chiller includes a coolant circuit that supplies a temperature-controlled coolant to a load, a refrigeration circuit that adjusts the temperature of the coolant by heat exchange between the coolant and the refrigerant, and the It has a heat exchanger that exchanges heat between the cooling liquid and the refrigerant, and a control unit that controls the entire chiller.
- control unit includes a temperature setting unit that sets an initial setting temperature and an adjustment target temperature of the load, and a time setting unit for setting an adjustment time for changing the temperature from the initial temperature to the adjustment target temperature; a calculation unit for calculating a gradient of temperature change as a target temperature gradient from the set initial temperature, the adjustment target temperature, and the adjustment time; and a temperature control unit that adjusts the temperature of the coolant supplied to the heat exchanger so that the temperature of the load changes following the target temperature gradient to change the temperature of the cooling liquid. do.
- the refrigerating circuit includes a compressor for compressing refrigerant, a condenser for cooling high-temperature refrigerant discharged from the compressor, and a first electronic circuit for sending low-temperature refrigerant sent from the condenser to the heat exchanger.
- control unit divides the adjustment time into a plurality of time zones, each time, the current target temperature in the time domain is calculated from the target temperature gradient and the elapsed time in the time domain, and the current target temperature is compared with the current temperature of the load measured by the load temperature sensor, It is desirable that the temperature of the refrigerant supplied to the heat exchanger is adjusted by adjusting the opening degrees of the first electronic expansion valve and the second electronic expansion valve based on the comparison result.
- the target temperature gradient is calculated from the adjustment target temperature and the adjustment time when adjusting the temperature of the load, and the load is adjusted to the target temperature by changing the coolant temperature following this target temperature gradient. Since the temperature is changed, the temperature of the load can be changed gradually and precisely over a long period of time to the target temperature.
- Fig. 1 shows one embodiment of a refrigeration chiller according to the present invention.
- This chiller 1 changes the temperature of the load 2 from the temperature at the start of adjustment to a target temperature, and supplies the load 2 with a cooling liquid whose temperature is adjusted to suit the temperature adjustment of the load 2.
- a circuit 3 a refrigeration circuit 4 that adjusts the temperature of the cooling liquid by heat exchange between the cooling liquid and the refrigerant, a heat exchanger 5 that exchanges heat between the cooling liquid and the refrigerant, and a control that controls the entire chiller a part 6;
- the heat exchanger 5 has a refrigerant pipe 5a (evaporator) through which the refrigerant flows, and a cooling liquid pipe 5b through which the cooling liquid flows.
- the coolant not only cools the load 2, but also heats the load 2 by making the temperature of the coolant higher than the temperature of the load 2.
- the load 2 is a liquid, such as a concentrate of craft beer.
- the cooling liquid circuit 3 includes a tank 7 containing the cooling liquid, a pump 8 for supplying the cooling liquid in the tank 7 to the load 2, and a supply line for connecting a supply side load pipe 2a of the load 2.
- a return-side connection port 9b for connecting the side connection port 9a and the return-side load pipe 2b, a supply-side temperature sensor 10 for detecting the temperature of the cooling liquid supplied to the load 2, and the cooling returned from the load 2. and a return-side temperature sensor 11 for detecting the temperature of the liquid.
- the suction port 8a of the pump 8 is connected to the outlet 7b of the tank 7 by a first supply pipe 12, the discharge port 8b of the pump 8 is connected to the supply side connection port 9a by a second supply pipe 13, The supply-side temperature sensor 10 and the pressure sensor 14 are connected to the second supply pipe 13 .
- the return-side connection port 9b is connected to one end of the coolant pipe 5b of the heat exchanger 5 via a first return pipe 15, and the other end of the coolant pipe 5b is connected to the tank via a second return pipe 16. 7 and the return side temperature sensor 11 is connected to the first return pipe 15 .
- a level switch 17 for monitoring the liquid level of the coolant is provided inside the tank 7.
- a drain discharge pipe 18 is connected to the first supply pipe 12, and the drain discharge pipe 18 is connected to a drain discharge port. 19 are provided.
- the pump 8, supply-side temperature sensor 10, return-side temperature sensor 11, pressure sensor 14, and level switch 17 are electrically connected to the control unit 6, and the control unit 6 controls or monitors each device.
- the coolant in the tank 7 is supplied to the load 2 by the pump 8 through the second supply pipe 13 and the supply-side load pipe 2a to adjust the temperature of the load 2.
- the coolant whose temperature is changed by adjusting the temperature of the load 2 flows back to the first return pipe 15 through the return side load pipe 2b, and the heat exchanger 5 performs heat exchange with the refrigerant to adjust the temperature. After that, it returns to the inside of the tank 7 .
- the refrigerating circuit 4 includes a compressor 20 that compresses a gaseous refrigerant and discharges it as a high-temperature, high-pressure gaseous refrigerant, and a compressor 20 that cools the gaseous refrigerant sent through a first pipe 21 from the compressor 20 to a low temperature.
- a first electronic expansion valve 24 that expands the refrigerant sent from the condenser 22 through a second pipe 23 and converts it into a low-temperature and low-pressure liquid refrigerant; 3.
- the evaporator 5a evaporates the liquid refrigerant sent through the pipe 25 by heat exchange with the cooling liquid to produce a low-pressure gaseous refrigerant.
- the gaseous refrigerant coming out of the evaporator 5a is returned to the compressor 20 through the fourth pipe 26.
- the first pipe 21 and the third pipe 25 are connected by a bypass pipe 27, through which the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 20 is sent to the evaporator 5a.
- a two-electron expansion valve 28 is connected.
- the condenser 22 is an air-cooled condenser that cools the refrigerant by a fan 22b driven by an electric motor 22a, and its rotation speed is controlled according to the pressure of the refrigerant measured by a first refrigerant pressure sensor 31, which will be described later. .
- the pump 8 and the compressor 20 are fully operated at a fixed number of revolutions by a commercial power source.
- a first refrigerant temperature sensor 29 for detecting the temperature of the refrigerant discharged from the compressor 20 is connected to the first pipe 21, and gaseous refrigerant returning to the compressor 20 is connected to the fourth pipe 26.
- a second refrigerant temperature sensor 30 is connected to detect the temperature.
- the first refrigerant pressure sensor 31 for measuring the pressure of the high-pressure refrigerant is connected to the second pipe 23, and the second refrigerant pressure sensor for measuring the pressure of the low-pressure refrigerant is connected to the fourth pipe 26. 32 are connected.
- the refrigerant temperature sensor 30 is electrically connected to the control section 6, and the control section 6 controls or monitors each device.
- the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 20 is sent to the condenser 22 through the first pipe 21, and cooled by the condenser 22 to become a low-temperature and high-pressure liquid refrigerant.
- the refrigerant is sent through the second pipe 23 to the first electronic expansion valve 24, where the refrigerant is expanded at a flow rate corresponding to the opening degree of the first electronic expansion valve 24.
- the refrigerant becomes a low-temperature, low-pressure liquid refrigerant and is sent to the evaporator 5 a of the heat exchanger 5 through the third pipe 25 .
- a part of the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 20 is also sent to the second electronic expansion valve 28 through the bypass pipe 27.
- the refrigerant with a flow rate corresponding to the opening degree of the electronic expansion valve 28 is expanded into a high-temperature and low-pressure gaseous refrigerant, it is sent to the third pipe 25, and the low-temperature liquid refrigerant from the first electronic expansion valve 24 is supplied. and then sent to the evaporator 5 a of the heat exchanger 5 .
- the refrigerant which has become a low-pressure gas by exchanging heat with the cooling liquid in the heat exchanger 5 , returns to the compressor 20 through the fourth pipe 26 . Therefore, the first electronic expansion valve 24 and the second electronic expansion valve 28 constitute a refrigerant temperature adjusting mechanism for adjusting the temperature of the refrigerant supplied to the heat exchanger 5 .
- the control unit 6 includes a microcomputer (not shown), which adjusts the temperature of the coolant from a set initial temperature (set initial temperature) to a target temperature (adjusted target temperature ) over a certain period of time to gradually change (rise or decrease) the temperature of the load 2 to the same target temperature over a certain period of time.
- a microcomputer not shown
- the temperature of the load 2 is raised to the same target temperature by raising the temperature of the coolant from the set initial temperature (for example, 0°C) to the adjustment target temperature (for example, 30°C).
- the control unit 6 includes a temperature setting unit 33 for setting the initial setting temperature Ho and the adjustment target temperature Hg of the cooling liquid, and a temperature setting unit 33 for setting the temperature of the cooling liquid to the initial setting
- a time setting unit 34 for setting an adjustment time Tg for changing the temperature from the temperature Ho to the adjustment target temperature Hg, and the gradient of the temperature change is calculated as the target temperature gradient from the set initial temperature Ho, the adjustment target temperature Hg, and the adjustment time Tg.
- a temperature control unit 36 that adjusts the opening degrees of the first electronic expansion valve 24 and the second electronic expansion valve 28 so that the temperature of the coolant changes following the target temperature gradient. have.
- FIG. 3 shows a flow chart when the temperature control of the load 2 is performed by the control section 6 .
- step S1 the set initial temperature Ho and the adjustment target temperature Hg of the coolant are input to the temperature setting unit 33, and the time setting unit 34 sets the An adjustment time Tg (for example, 24 hours) is entered, after which temperature control is started.
- the set initial temperature Ho may be the one that has been previously set, and the input here may be omitted.
- the set initial temperature Ho, the adjustment target temperature Hg, and the adjustment time Tg are determined based on the relationship between the temperature change of the cooling liquid and the temperature change of the load 2, which is obtained in advance through experiments, calculations, or the like. can be determined by Further, the adjustment time Tg is divided into a plurality of time zones ta as shown in FIG. It has become.
- the time ranges ta may have the same time width or different time widths.
- step S1 When the temperature control is started after step S1, the process proceeds to step S2, and the calculation unit 35 calculates the target temperature gradient from the set initial temperature Ho, the adjustment target temperature Hg, and the adjustment time Tg. Calculated as ⁇ H.
- the target temperature gradient ⁇ H is 0.02° C./min.
- step S3 for the first time region ta in the adjustment time Tg, the current target temperature at the end of the time region ta is calculated from the target temperature gradient ⁇ H and the elapsed time t of the time region ta,
- step S4 the current temperature of the coolant supplied to load 2 is measured by said supply temperature sensor 10, and this current temperature is compared with said current target temperature in step S5.
- step S6 the temperature control unit 36 reduces the degree of opening of the first electronic expansion valve 24.
- the degree of opening of the second electronic expansion valve 28 is increased, and as a result, the flow rate of the low-temperature refrigerant supplied to the heat exchanger 5 decreases and the flow rate of the high-temperature refrigerant increases, thereby increasing the temperature of the refrigerant. rises and the heating capacity of the heat exchanger 5 increases, so that the temperature of the coolant rises.
- step S5 the process proceeds from step S5 to step S7, where the temperature control unit 36 increases the opening of the first electronic expansion valve 24 and increases the opening of the first electronic expansion valve 24.
- the degree of opening of the second electronic expansion valve 28 is reduced, and as a result, the flow rate of the low-temperature refrigerant supplied to the heat exchanger 5 increases and the flow rate of the high-temperature refrigerant decreases, thereby lowering the temperature of the refrigerant. Since the cooling capacity of the heat exchanger 5 is enhanced, the temperature of the coolant drops.
- step 8 When the operation of step 6 or step 7 is completed, it is determined in step 8 whether or not the adjustment time Tg has passed. , the operations of steps 3, 4, 5, 6 or 7, and 8 are sequentially repeated.
- step 9 the temperature adjustment of the cooling liquid is completed, and the temperature of the cooling liquid is maintained at the adjustment target temperature Hg.
- the temperature of the load 2 is also maintained at substantially the same temperature as the adjustment target temperature Hg.
- the temperature of the load 2 can be constantly monitored and the temperature of the load 2 can be compared with the current temperature of the coolant. Further, an electric heater may be provided in the tank 7 so that the temperature of the coolant can be increased by using the heater as an auxiliary means when the cooling liquid is insufficiently heated by the coolant.
- the temperature of the load 2 is increased by one step from 0° C. to 30° C.
- the temperature of the load 2 can be adjusted in a plurality of steps. can. For example, by setting the adjustment target temperature Hg to two levels of 30° C. and 60° C., the temperature of the load 2 is raised to 30° C., maintained at that temperature for the required time, and then further raised to 60° C. It is also possible to perform control such as allowing
- the temperature of the load 2 is raised, but control to lower the temperature of the load 2 can also be performed.
- the set initial temperature Ho of the coolant is set to 30° C. and the adjustment target temperature Hg is set to 0° C., as shown in FIG.
- the control should be performed according to the flow chart.
- the current temperature of the coolant is equal to the current target temperature in step 5, it is necessary to lower the temperature of the coolant along the target temperature gradient.
- the opening degree of the first electronic expansion valve 24 is enlarged and the opening degree of the second electronic expansion valve 28 is reduced.
- the temperature of the load 2 is adjusted by adjusting the temperature of the coolant supplied from the coolant circuit 3 to the load 2. It is also possible to adjust the temperature of the load 2 by adjusting the temperature of the refluxing coolant. In this case, in the flow chart shown in FIG. 3, the current temperature of the coolant in step 4 is measured by the return side temperature sensor 11 connected to the first return pipe 15 .
- the set initial temperature Ho and the adjustment target temperature Hg of the cooling liquid are set, and the temperature of the cooling liquid is adjusted along the temperature gradient, thereby increasing the temperature of the load 2 to the target temperature.
- the set initial temperature Ho and adjustment target temperature Hg of the load 2 are set, and the temperature of the coolant is adjusted so that the temperature of the load 2 changes along the temperature gradient.
- the load temperature sensor 37 is provided for the load 2, and the load temperature sensor 37 measures the temperature of the load 2 as the current temperature. is compared with The opening degrees of the first electronic expansion valve 24 and the second electronic expansion valve 28 are adjusted so that the current temperature of the load 2 follows the target temperature gradient, whereby the temperature of the coolant is is adjusted.
- the pump 8, the compressor 20, and the electric motor 22a used in the refrigeration chiller 1 of FIG. 1 can be inverter-controlled. By doing so, in step S6 and step S7 of the flowchart shown in FIG.
- inverter-controlling the rotation speed of the compressor 20 to change the circulation amount of the refrigerant responsiveness can be improved, and at the same time, energy can be saved by reducing the circulation amount of the refrigerant.
- the number of rotations of the pump 8 can also be reduced according to the load, which leads to energy saving.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
Description
また、本実施形態において、前記負荷2は、例えばクラフトビールの原液のような液体である。
また、前記戻り側接続口9bは、第1戻り管15によって前記熱交換器5の冷却液管5bの一端に接続され、該冷却液管5bの他端は、第2戻り管16によって前記タンク7の入口7aに接続され、前記第1戻り管15に前記戻り側温度センサ11が接続されている。
一方、前記ポンプ8、圧縮機20は、商用電源による固定の回転数でフル運転されるものである。
従って、前記第1電子膨張弁24及び第2電子膨張弁28は、前記熱交換器5に供給される冷媒の温度を調整する冷媒温度調整機構を構成するものである。
また、前記調整時間Tgは、図2に示すように複数の時間域taに区分されていて、時間域ta毎に冷却液の温度変化が確認され、確認結果に基づいた温度制御が行われるようになっている。前記時間域taは、互いに同じ時間幅であっても、異なる時間幅であっても良い。
また、前記タンク7内に電気ヒーターを設け、前記冷媒による冷却液の加熱が不十分である場合に、このヒーターを補助的に使用して冷却液の温度を上昇させるようにすることもできる。
更に、前述したように負荷2の温度を上昇させるか又は低下させるだけではなく、温度を上昇させる制御と、温度を低下させる制御と、温度を一定時間維持する制御とを、組み合わせて行うこともできる。
2 負荷
3 冷却液回路
4 冷凍回路
5 熱交換器
6 制御部
7 タンク
8 ポンプ
10 供給側温度センサ
11 戻り側温度センサ
20 圧縮機
22 コンデンサ
24 第1電子膨張弁
28 第2電子膨張弁
33 温度設定部
34 時間設定部
35 演算部
36 温度制御部
37 負荷温度センサ
Hg 調整目標温度
Ho 初期温度
Tg 調整時間
ta 時間域
t 経過時間
ΔH 目標温度勾配
Claims (4)
- 温度調整された冷却液を負荷に供給する冷却液回路と、前記冷却液の温度を該冷却液と冷媒との熱交換により調整する冷凍回路と、前記冷却液と冷媒との熱交換を行う熱交換器と、チラー全体を制御する制御部とを有し、
前記冷却液回路は、前記冷却液を収容するタンクと、該タンク内の冷却液を負荷に供給するポンプと、前記冷却液の温度を測定する温度センサとを有し、
前記制御部は、負荷の温度を目標温度まで変化させるための冷却液の設定初期温度及び調整目標温度を設定する温度設定部と、前記冷却液の温度を設定初期温度から調整目標温度まで変化させるための調整時間を設定する時間設定部と、前記設定初期温度と調整目標温度及び調整時間とから温度変化の勾配を目標温度勾配として算出する演算部と、前記目標温度勾配に追従して前記冷却液の温度が変化するように前記熱交換器に供給される冷媒の温度を調整する温度制御部とを有する、
ことを特徴とする冷凍式チラー。 - 前記冷凍回路は、冷媒を圧縮する圧縮機と、該圧縮機から吐出された高温の冷媒を冷却するコンデンサと、該コンデンサから送られる低温の冷媒を前記熱交換器に送る第1電子膨張弁と、前記圧縮機から吐出された高温の冷媒を前記熱交換器に送る第2電子膨張弁とを有し、
前記制御部は、前記調整時間を複数の時間域に区分し、時間域毎に、前記目標温度勾配と時間域での経過時間とからその時間域における現在目標温度を算出すると共に、該現在目標温度と前記温度センサで測定された冷却液の現在温度とを比較し、比較結果に基づいて前記第1電子膨張弁及び第2電子膨張弁の開度を調整することにより前記熱交換器に供給される冷媒の温度を調整する、
ことを特徴とする請求項1に記載の冷凍式チラー。 - 温度調整された冷却液を負荷に供給する冷却液回路と、前記冷却液の温度を該冷却液と冷媒との熱交換により調整する冷凍回路と、前記冷却液と冷媒との熱交換を行う熱交換器と、チラー全体を制御する制御部とを有し、
前記冷却液回路は、前記冷却液を収容するタンクと、該タンク内の冷却液を負荷に供給するポンプと、前記負荷の温度を測定する負荷温度センサとを有し、
前記制御部は、負荷の設定初期温度及び調整目標温度を設定する温度設定部と、前記負荷の温度を前記設定初期温度から前記調整目標温度まで変化させるための調整時間を設定する時間設定部と、前記設定初期温度と調整目標温度及び調整時間とから温度変化の勾配を目標温度勾配として算出する演算部と、前記目標温度勾配に追従して前記負荷の温度が変化するように前記熱交換器に供給される冷媒の温度を調整して前記冷却液の温度を変化させる温度制御部とを有する、
ことを特徴とする冷凍式チラー。 - 前記冷凍回路は、冷媒を圧縮する圧縮機と、該圧縮機から吐出された高温の冷媒を冷却するコンデンサと、該コンデンサから送られる低温の冷媒を前記熱交換器に送る第1電子膨張弁と、前記圧縮機から吐出された高温の冷媒を前記熱交換器に送る第2電子膨張弁とを有し、
前記制御部は、前記調整時間を複数の時間域に区分し、時間域毎に、前記目標温度勾配と時間域での経過時間とからその時間域における現在目標温度を算出すると共に、該現在目標温度と前記負荷温度センサで測定された負荷の現在温度とを比較し、比較結果に基づいて前記第1電子膨張弁及び第2電子膨張弁の開度を調整することにより前記熱交換器に供給される冷媒の温度を調整する、
ことを特徴とする請求項3に記載の冷凍式チラー。
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BR112023021689A BR112023021689A2 (pt) | 2021-04-21 | 2022-03-24 | Resfriador do tipo refrigeração |
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AU2022262472A AU2022262472A1 (en) | 2021-04-21 | 2022-03-24 | Refrigeration-type chiller |
CA3215599A CA3215599A1 (en) | 2021-04-21 | 2022-03-24 | Refrigeration-type chiller |
CN202280029433.2A CN117178153A (zh) | 2021-04-21 | 2022-03-24 | 制冷式冷却器 |
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JP2691001B2 (ja) * | 1989-03-02 | 1997-12-17 | タバイエスペック株式会社 | 温湿度制御におけるヒータ出力適正化方法 |
JP2816054B2 (ja) * | 1992-06-25 | 1998-10-27 | 三洋電機株式会社 | 恒温庫の温度制御装置 |
JP2008292026A (ja) * | 2007-05-23 | 2008-12-04 | Ats Japan Corp | 恒温維持装置。 |
JP2015014417A (ja) | 2013-07-04 | 2015-01-22 | Smc株式会社 | 恒温液循環装置及びその運転方法 |
JP2019191841A (ja) * | 2018-04-24 | 2019-10-31 | サンデン・リテールシステム株式会社 | 温冷庫の温度制御装置 |
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2021
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- 2022-03-24 WO PCT/JP2022/013819 patent/WO2022224689A1/ja active Application Filing
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- 2022-03-24 KR KR1020237035445A patent/KR20230173665A/ko unknown
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Patent Citations (5)
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JP2691001B2 (ja) * | 1989-03-02 | 1997-12-17 | タバイエスペック株式会社 | 温湿度制御におけるヒータ出力適正化方法 |
JP2816054B2 (ja) * | 1992-06-25 | 1998-10-27 | 三洋電機株式会社 | 恒温庫の温度制御装置 |
JP2008292026A (ja) * | 2007-05-23 | 2008-12-04 | Ats Japan Corp | 恒温維持装置。 |
JP2015014417A (ja) | 2013-07-04 | 2015-01-22 | Smc株式会社 | 恒温液循環装置及びその運転方法 |
JP2019191841A (ja) * | 2018-04-24 | 2019-10-31 | サンデン・リテールシステム株式会社 | 温冷庫の温度制御装置 |
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CA3215599A1 (en) | 2022-10-27 |
CN117178153A (zh) | 2023-12-05 |
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