WO2004102086A1 - 冷凍装置 - Google Patents
冷凍装置 Download PDFInfo
- Publication number
- WO2004102086A1 WO2004102086A1 PCT/JP2004/006764 JP2004006764W WO2004102086A1 WO 2004102086 A1 WO2004102086 A1 WO 2004102086A1 JP 2004006764 W JP2004006764 W JP 2004006764W WO 2004102086 A1 WO2004102086 A1 WO 2004102086A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat exchanger
- refrigerant
- air
- pressure
- air heat
- Prior art date
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 179
- 239000007788 liquid Substances 0.000 claims description 94
- 238000005057 refrigeration Methods 0.000 claims description 33
- 238000001514 detection method Methods 0.000 claims description 12
- 210000000689 upper leg Anatomy 0.000 claims description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 136
- 238000001816 cooling Methods 0.000 abstract description 13
- 238000007664 blowing Methods 0.000 abstract description 2
- 238000010438 heat treatment Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- VGGSQFUCUMXWEO-UHFFFAOYSA-N Ethene Chemical compound C=C VGGSQFUCUMXWEO-UHFFFAOYSA-N 0.000 description 1
- 239000005977 Ethylene Substances 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 239000012267 brine Substances 0.000 description 1
- NBVXSUQYWXRMNV-UHFFFAOYSA-N fluoromethane Chemical compound FC NBVXSUQYWXRMNV-UHFFFAOYSA-N 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
-
- 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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B49/027—Condenser control arrangements
-
- 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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
- F25B2600/111—Fan speed control of condenser fans
-
- 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
- F25B2700/195—Pressures of the condenser
-
- 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
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Definitions
- the present invention relates to a refrigeration system having a liquid heat exchanger and an air heat exchanger.
- a refrigerating apparatus that simultaneously supplies cold water and hot water includes a compressor that compresses a refrigerant, a hot water heat exchanger, an expander, a cold water heat exchanger, and air heat exchange.
- a compressor in which a three-way discharge valve is provided on the discharge side of the compressor, and a three-way suction valve is provided on the suction side of the compressor (Japanese Patent Application Laid-Open No. 56-97555).
- the conventional refrigeration apparatus adjusts the opening of the discharge-side three-way valve to increase the discharge side of the compressor. While communicating with the hot water heat exchange and air heat exchange, the opening of the three-way valve on the suction side is adjusted to communicate the suction side of the compressor with the cold water heat exchange m ⁇ .
- the air heat exchanger functions as a condenser to balance the heat load between the cold water heat exchanger with a relatively large heat load and the hot water heat exchange with a relatively small heat load. Like that.
- the opening of the three-way valve on the discharge side is adjusted so that the discharge side of the compressor is only the hot water heat exchanger. While adjusting the opening of the suction side three-way valve, the suction side of the compressor is communicated with the chilled water heat exchanger and air heat exchange. This allows the air heat exchanger to function as an evaporator to balance the heat load between the hot water heat exchanger with a relatively large heat load and the chilled water heat exchanger with a relatively small heat load. I do it.
- the air for the air heat exchange when the air heat exchange functions as a condenser, the air for the air heat exchange is generally lower in temperature than the hot water for the heat exchange in the hot water heat exchange.
- the condensing pressure of the refrigerant in the air heat exchanger is lower than the condensing pressure of the refrigerant in the hot water heat exchanger. Therefore, the above hot water heat exchanger Since the flow rate of the refrigerant in the air heat exchanger is smaller than the flow rate of the refrigerant in the air heat exchanger, a so-called stagnation phenomenon occurs in which the refrigerant stays in the air heat exchanger.
- the conventional refrigeration system has a problem that the amount of refrigerant that needs to be held in the refrigerant circuit is larger than that of a normal refrigeration system having only the chilled water heat exchange and the air heat exchanger.
- the outdoor water temperature is 15 ° C and the hot-water heat exchanger performs heat exchange of hot water of about 45 ° C
- an object of the present invention is to provide a refrigeration apparatus in which a stagnation phenomenon hardly occurs in an air heat exchanger.
- a refrigeration apparatus includes: a compressor for compressing a refrigerant;
- a first liquid heat exchanger that performs heat exchange between the refrigerant and the first liquid heat medium
- An air heat exchanger that performs heat exchange between the refrigerant and air
- Refrigerant flow rate adjusting means for adjusting the refrigerant flow rates of the first liquid heat exchanger, the second liquid heat exchanger, and the air heat exchanger;
- a pressure sensor for detecting the pressure of the refrigerant of the air heat exchanger
- Target pressure value setting means for setting a target pressure value of the refrigerant of the air heat exchanger according to a target temperature value of the first liquid heat medium; Blower control means for controlling the blower so that the detection value of the pressure sensor becomes the target pressure value;
- the refrigerant compressed by the compressor is adjusted by controlling the flow rate of each heat exchanger by the refrigerant flow rate adjusting means, and the first liquid heat exchanger, the expansion means,
- the second liquid heat exchanger is circulated sequentially.
- the first liquid heat exchange works as a condenser to heat the first liquid heat medium
- the second liquid heat exchange! ⁇ Works as an evaporator to cool the second liquid heat medium.
- the flow rate of the refrigerant to the air heat exchanger is adjusted by the refrigerant flow rate adjusting means, and the air heat exchange functions as a condenser or an evaporator.
- the heat load balance between the first liquid heat exchange and the second liquid heat exchanger is adjusted.
- the target pressure value of the refrigerant of the air heat exchanger is set by the target pressure value setting means according to the target temperature value of the first liquid heat medium. Then, the blower control means controls, for example, the number of rotations and the number of operating fans of the blower, so that the detection value of the pressure sensor becomes the target pressure value.
- the refrigerant does not easily stay in the air heat exchange, and the so-called stagnation phenomenon of the refrigerant does not easily occur.
- the amount of refrigerant to be held in the refrigerant circuit can be significantly reduced, and the risk of liquid compression of the compressor can be avoided.
- the amount of air blown by the blower By appropriately increasing the flow rate of the refrigerant, the flow rate of the refrigerant to any of the heat exchangers can be reduced, so that the refrigerant discharge amount of the compressor can be minimized. Therefore, this refrigeration apparatus can effectively reduce the power consumption of, for example, the motor that drives the compressor.
- the discharge pressure of the compressor supplying the refrigerant to the air heat exchanger is adjusted.
- the output pressure may be any pressure that matches the target temperature value of the first liquid heating medium. Therefore, for example, rather than fixing the discharge pressure of the compressor to a discharge pressure corresponding to the maximum target temperature value that can be set for the first liquid heat medium, the discharge pressure of the compressor is set to the target temperature. It can be reduced according to the value. As a result, for example, the power consumption of the motor for driving the compressor can be effectively reduced.
- the cooling power in the air heat exchanger is reduced by 1% in the first liquid heat exchanger. It is possible to prevent the refrigerant pressure from being greatly reduced with respect to the refrigerant pressure, and, consequently, to reduce the flow rate of the refrigerant supplied to the air heat exchanger to a necessary minimum. Therefore, the refrigerant having a larger flow rate than before can be supplied to the first liquid heat exchanger to which the refrigerant is supplied together with the air heat exchange by the refrigerant flow rate adjusting means.
- the temperature control of the heat medium can be performed with higher precision than before.
- the pressure of the refrigerant in the air heat exchanger means the pressure of the refrigerant in the air heat exchanger, the pressure of the refrigerant near the inlet of the air heat exchanger, or the pressure of the air heat exchanger. It is defined to mean any of the pressures of the refrigerant near the outlet.
- the refrigerant flow rate adjusting means may be a three-way valve or a combination of a plurality of two-way valves.
- the refrigeration apparatus according to claim 2 is the refrigeration apparatus according to claim 1,
- a temperature sensor that detects the temperature of the first liquid heat medium that has been heat-exchanged with the refrigerant in the first liquid heat exchange
- target pressure value correcting means for correcting the target pressure value based on the detection value of the temperature sensor.
- the target pressure value of the air-heat exchange refrigerant is corrected based on the actual temperature of the first liquid heat medium detected by the temperature sensor. Therefore, in the air heat exchanger, a significant decrease in the condensing pressure of the refrigerant is reliably prevented according to the actual condensing pressure of the refrigerant in the first liquid heat exchanger. As a result, the stagnation of the refrigerant in the air heat exchanger is effectively prevented, and the stagnation phenomenon of the refrigerant is effectively prevented.
- the pressure of the refrigerant in the air heat exchanger is equal to the actual temperature of the first liquid heat medium. Since the pressure is adjusted according to the pressure, the discharge pressure of the compressor that supplies the refrigerant to the air heat exchanger may be a pressure that matches the actual temperature of the first liquid heat medium. Therefore, the discharge pressure of the compressor can be reduced according to the actual temperature of the first liquid heat medium, so that the power consumption of, for example, a motor for driving the compressor can be effectively reduced. can do.
- a refrigeration apparatus comprises a compressor for compressing a refrigerant
- a first liquid heat exchanger that performs heat exchange between the refrigerant and the first liquid heat medium
- a second liquid heat exchanger that performs heat exchange between the refrigerant and the second liquid heat medium
- An air heat exchanger that performs heat exchange between the refrigerant and air
- a blower for blowing air heat exchange A blower for blowing air heat exchange
- Refrigerant flow rate adjusting means for adjusting the refrigerant flow rates of the first liquid heat exchanger, the second liquid heat exchanger, and the air heat exchanger;
- a pressure sensor that detects the pressure of the refrigerant of the air heat exchange ⁇
- Target pressure value setting means for setting a target pressure value of the refrigerant of the air heat exchanger according to a detection value of the temperature sensor
- Blower control means for controlling the blower so that the detection value of the pressure sensor becomes the target pressure value
- the refrigerant compressed by the compressor is adjusted by adjusting the flow rate of each heat exchanger by the refrigerant flow rate adjusting means, so that the first liquid heat exchanger, the expansion means, The second liquid heat exchanger is circulated sequentially.
- the first liquid heat exchange crane works as a condenser to heat the first liquid heat medium
- the second liquid heat exchanger works as an evaporator to cool the second liquid heat medium.
- the refrigerant flow rate to the air heat exchanger is adjusted by the refrigerant flow rate adjusting means, and the air heat exchanger functions as a condenser or an evaporator.
- the heat load balance between the first liquid heat exchange and the second liquid heat exchanger is adjusted.
- the target pressure value of the refrigerant of the air heat exchanger sets the temperature of the first liquid heat medium detected by the temperature sensor. Then, the blower control means controls, for example, the number of rotations and the number of operating fans of the blower so that the detection value of the pressure sensor becomes the target pressure value. This prevents the refrigerant pressure in the air heat exchange from significantly lowering than the refrigerant pressure in the first liquid heat exchange. That is, it is possible to prevent the condensing pressure of the refrigerant in the air heat exchanger from being significantly reduced with respect to the condensing pressure of the refrigerant in the first liquid heat exchanger.
- the refrigerant is less likely to stay in the air heat exchanger, and the so-called stagnation phenomenon of the refrigerant is less likely to occur.
- the amount of refrigerant to be held in the refrigerant circuit can be significantly reduced, and the risk of liquid compression of the compressor can be avoided.
- the amount of air blown by the blower is appropriate.
- the flow rate of the refrigerant to any of the heat exchangers can be reduced, so that the refrigerant discharge amount of the compressor can be minimized. Therefore, this refrigeration apparatus can effectively reduce the power consumption of, for example, a motor that drives the compressor.
- the refrigerant pressure in the air heat exchange is the same as the refrigerant pressure detected by the temperature sensor.
- the discharge pressure of the compressor that supplies the refrigerant to the air heat exchanger m3 ⁇ 4 matches the actual temperature of the first liquid heat medium. Pressure. Therefore, the discharge pressure of the compressor can be reduced according to the actual temperature of the first liquid heat medium, so that the power consumption of, for example, a motor for driving the compressor can be effectively reduced. it can.
- the amount of air blown to the air heat exchanger is controlled so as to be the target pressure value of the air heat exchanger, the refrigerant pressure in the air heat exchanger is changed to the refrigerant pressure in the first liquid heat exchanger. It is possible to prevent the pressure from dropping significantly with respect to the pressure, and thus the flow rate of the refrigerant supplied to the air heat exchange can be reduced to a necessary minimum. Therefore, the refrigerant having a larger flow rate than before can be supplied to the first liquid heat exchanger to which the refrigerant is supplied together with the air heat exchanger by the refrigerant flow rate adjusting means.
- the temperature control of the liquid heating medium can be performed with higher precision than before.
- FIG. 1 is a schematic diagram showing a refrigeration apparatus according to an embodiment of the present invention.
- FIG. 2 is a diagram showing a refrigerant circuit when the refrigeration apparatus performs a cooling main mode operation.
- FIG. 1 is a schematic diagram showing a refrigeration apparatus according to an embodiment of the present invention.
- This refrigeration system is a refrigeration system that simultaneously supplies cold water and hot water, and includes a compressor 1 that compresses refrigerant, hot water heat exchange 3 as first liquid heat exchange, and cold water as second liquid heat exchange.
- a heat exchanger 4 and an air heat exchanger 6 are provided.
- the refrigerant for example, 407 is used. Use «:? ⁇ (Hide mouth fluorocarbon) refrigerant.
- the discharge three-way valve 8 By connecting a discharge three-way valve 8 to the discharge pipe of the compressor 1 and changing the opening of the discharge three-way valve 8, the high-pressure refrigerant from the compressor 1 is exchanged with the hot water heat exchanger 3 by air and air. The ratio of the flow rate to the container 6 is changed.
- the suction three-way valve 9 By connecting the suction three-way valve 9 to the suction pipe of the compressor 1 and changing the opening of the suction three-way valve 9, the low-pressure refrigerant from the air heat exchange 6 and the low pressure from the cold water heat The refrigerant and are supplied to the compressor 1 at different flow rate ratios. That is, the discharge three-way valve 8 and the suction three-way valve 9 function as refrigerant flow rate adjusting means.
- the hot water heat exchanger 3 heats the water by exchanging heat between the high-temperature and high-pressure refrigerant from the compressor 1 and water as the first liquid heat medium.
- the cold water heat exchange 4 exchanges heat between the low-temperature low-pressure refrigerant expanded by the first electronic expansion valve 11 as expansion means and water as the second liquid heat medium, and this water is exchanged. Cooling.
- the air heat exchanger 6 functions as a condenser or an evaporator according to the opening degree of the discharge three-way valve 8 and the suction three-way valve 9.
- the air heat exchanger 6 When operating as a condenser, the air heat exchanger 6 is supplied with a high-temperature / high-pressure refrigerant from the compressor 1 via a discharge three-way valve 8, and exchanges heat between the refrigerant and air.
- the heat-exchanged refrigerant is guided to the liquid receiver 14 via a refrigerant pipe provided with a check valve.
- the refrigerant introduced from the hot water heat exchanger 3 to the liquid receiver 14 serves as expansion means.
- the refrigerant is supplied after being expanded and decompressed by all the second electronic expansion valves 12, and exchanges heat with the refrigerant.
- the heat-exchanged refrigerant is sucked into the compressor 1 through the suction three-way valve 9.
- the air heat exchanger 6 receives the air blown by the blower 16 to adjust the condensation pressure of the refrigerant inside.
- the blower JM 16 includes a fan and a variable speed motor that drives the fan. The rotation speed of the variable speed motor is controlled to control the amount of air blown to the air heat exchanger 6.
- This refrigeration apparatus is a control device that controls the operation of the refrigeration apparatus according to the target temperature of the water to be heated by the hot water heat exchange 3 and the target temperature of the water to be cooled by the cold water heat exchanger 4.
- the controller 19 includes a hot water temperature sensor 17 for detecting the temperature of the water discharged from the hot water heat exchanger 3, a cold water temperature sensor for detecting the temperature of the water discharged from the cold water heat exchanger 4, Each of the air heat exchangers 6 is connected to a pressure sensor 18 for detecting a cooling force of 1 in the air heat exchanger 6.
- the control device 19 controls the opening of the discharge three-way valve 8, the opening of the suction three-way valve 9, and the opening of the first electronic expansion valve 11 based on signals from the sensors. And the opening of the second electronic expansion valve 12 is controlled.
- the discharge three-way valve 8 and the suction three-way valve 9 are housed in three housings and housed in the housing to communicate two or all of the three ports with each other.
- a valve body and a solenoid or a motor for driving the valve body are provided.
- Driving power is supplied to the solenoid or the motor by driving devices 8a and 9a.
- the driving devices 8a and 9a change the power supplied to the solenoid or the motor based on the signal from the control device 19 to control the position of the valve body with respect to the housing. This controls the communication between the three ports and the fluid flow rate between the connected ports.
- the first and second electronic expansion valves 11 and 12 include a needle valve, a fluid passage formed between an inflow port and an outflow port, and accommodating the needle valve, and the needle valve.
- the solenoid is supplied with driving power by driving devices 11a and 12a.
- the driving devices 11 a and 12 a are configured to supply power to the solenoid based on a signal from the control device 19.
- the force is changed to control the position of the Udle valve relative to the fluid passage.
- the distance between the outer peripheral surface of the dollar valve and the inner peripheral surface of the fluid passage is changed to control the pressure difference of the fluid between the inflow port and the outflow port. Has become.
- control device 19 is connected to an inverter 1 a for supplying drive power to the compressor 1, and controls an operating frequency of the inverter 1 a to control the operating frequency of the inverter 1 a to transmit the compressor 1 to the compressor 1. Change the frequency of the power supplied to one motor. Thereby, the rotation speed of the motor of the compressor 1 is controlled, the rotation speed of the compression element driven by this motor is controlled, and the amount of refrigerant discharged from the compressor 1 is controlled. I have.
- control device 19 is connected to an inverter 16a for supplying drive power to the blower 16 and controls the operating frequency of the inverter 16a to control the operation frequency of the inverter 16a.
- the frequency of the power supplied to the motor of the blower 16 is changed.
- the control device 19 also functions as a blower control unit.
- the control device 19 performs approximately five modes of operation according to the target temperature and heat load of the hot water heat exchange 3 and the target temperature and heat load of the chilled water heat exchanger 4.
- the first mode is a cooling-only mode, and is an operation mode in which the target temperature is set only in the chilled water heat exchanger 4.
- the opening degree of the discharge three-way valve 8 is set to an opening degree at which all of the refrigerant discharged from the compressor 1 is supplied to the air heat exchanger 6.
- the opening degree of the suction three-way valve 9 is set to the opening degree at which the refrigerant is supplied to the compressor 1 only from the chilled water heat exchanger 4.
- the second mode is a cooling main mode, in which a target temperature is set in both the chilled water heat exchanger 4 and the hot water heat exchange 6, and the heat of the chilled water heat exchanger 4 is increased.
- This mode is used when the load is larger than the heat load of Heat Exchange »6.
- the opening degree of the discharge three-way valve 8 is set such that the refrigerant discharged from the compressor 1 is guided to the hot water heat exchange 3 and the air heat exchange 6 at a predetermined ratio.
- the opening degree of the suction three-way valve 9 is set to an opening degree at which only the refrigerant from the cold water heat exchange 4 is guided to the compressor 1.
- both the hot water heat exchanger 3 and the air heat exchanger 6 work as condensers, and heat the water with the hot water heat exchanger 3 and cool the water with the cold water heat exchanger 4. .
- the opening degree of the discharge three-way valve 8 is adjusted to an opening degree at which the air heat exchanger 6 balances the heat load of the hot water heat exchange 6 and the heat load of the chilled water heat exchanger 4.
- the third mode is a uniform cooling / heating mode in which the target temperature is set in both the chilled water heat exchanger 4 and the hot water heat exchange, and the heat load of the chilled water heat exchange 4 and the hot water heat exchange m3 ⁇ 4.
- This is an operation mode in the case where the heat load is substantially the same as the heat load of FIG.
- the opening degree of the discharge three-way valve 8 is set such that all of the refrigerant discharged from the compressor 1 is supplied to the hot water heat exchanger 3.
- the opening degree of the suction three-way valve 9 is set such that only the refrigerant from the cold water heat exchange is guided to the compressor 1.
- the fourth mode is a heating main mode, in which the target temperature is set in both the chilled water heat exchanger 4 and the hot water heat exchanger 6, and the heat load of the chilled water heat exchanger 4 is the hot water heat exchange.
- This is the operation mode when the heat load is smaller than the heat load of the vessel 6.
- the opening degree of the discharge three-way valve 8 is set such that all of the refrigerant discharged from the compressor 1 is supplied to the hot water heat exchanger 3.
- the opening degree of the suction three-way valve 9 is set such that the refrigerant from the air heat exchanger 6 and the refrigerant from the chilled water heat exchanger 4 are guided to the compressor 1 at a predetermined ratio.
- both the cold water heat exchanger 4 and the air heat exchanger 6 work as evaporators.
- the opening of the suction three-way valve 9 is adjusted to an opening that balances the heat load of the hot water heat exchange 3 and the heat load of the cold water heat exchange 4 with the air heat exchange crane 6.
- the fifth mode is a heating-only mode, in which only the hot water heat exchanger 3 has the target temperature. Is an operation mode when is set.
- the opening degree of the discharge three-way valve 8 is set to an opening degree at which all of the refrigerant discharged from the compressor 1 is supplied to the hot water heat exchanger 3.
- the opening of the three-way intake valve 9 is set to the opening at which the refrigerant is supplied to the compressor 1 only from the air heat exchanger 6.
- This forms a refrigerant cycle that circulates through the compressor 1, the hot water heat exchanger 3, the liquid receiver 14, the second electronic expansion valve 12, and the air heat exchanger 6. Only works as an evaporator, and only heats water in the hot water heat exchange 3 described above.
- FIG. 2 is a diagram showing a refrigerant circuit formed in the refrigeration apparatus when the control device 19 performs the cooling main mode, which is the second operation mode.
- the cooling main mode the high-temperature high-pressure refrigerant discharged from the compressor 1 is divided into the hot water heat exchange 3 and the air heat exchange 6 by the discharge three-way valve 8, and the hot water heat exchanger 3
- the heat is exchanged with the air in the air heat exchange 6 to lower the temperature.
- the refrigerant in the receiver 14 is adiabatically expanded by the first electronic expansion valve 11, becomes low temperature and low pressure, cools the water by the cold water heat exchange, raises the temperature, and sucks it into the compressor 1. Is done.
- the control device 19 determines the target pressure value Ps of the refrigerant in the air heat exchanger 6 according to the target temperature value Ts of the water to be heat-exchanged in the hot water heat exchange 3. That is, it works as a target pressure value setting means. Then, the rotation speed of the motor of the blower 16 is adjusted so that the detection value Pm of the refrigerant pressure in the air heat exchanger 6 by the pressure sensor 18 approaches the target pressure value Ps.
- the amount of air blown to the air heat exchanger 6 by the fan of the blower 16 is adjusted, and the refrigerant pressure in the air heat exchanger 6 and the refrigerant pressure in the hot water heat exchanger 3 are adjusted.
- the difference between. Therefore, it is possible to prevent the refrigerant pressure in the air heat exchanger 6 from dropping significantly below the refrigerant pressure in the hot water heat exchanger 3.
- this refrigeration apparatus can prevent the stagnation phenomenon of the refrigerant in the air heat exchanger 6.
- the amount of refrigerant to be held in the refrigerant circuit can be significantly reduced as compared with the conventional case. Further, when the mode is changed from the cooling main mode to the heating main mode, the liquid refrigerant staying in the air heat exchange 6 flows into the compressor 1, and the compressor 1 causes liquid compression to cause a failure. Can be effectively prevented.
- the refrigeration apparatus variably sets the target pressure Ps of the refrigerant of the air heat exchanger according to the target temperature Ts of the hot water heat exchange 3, for example, the target temperature Ts is relatively low. If both the condensing pressure of the hot water heat exchange m3 ⁇ 43 and the condensing pressure of the air heat exchange 6 can be low, the amount of air blown by the blower 16 can be appropriately increased. As a result, the compressor 1 The refrigerant discharge amount can be suppressed to a necessary minimum. Therefore, this refrigeration apparatus can effectively reduce the power consumption of the motor of the compressor 1.
- the target pressure P s of the air heat exchanger 6 is set to a relatively high value corresponding to the condensing pressure at the maximum target temperature T s at which the load of the hot water heat exchange 3 becomes the maximum.
- the power consumption of the compressor 1 can be significantly reduced as compared with the case of the first embodiment.
- the pressure of the refrigerant in the air heat exchanger 6 is adjusted to a pressure according to the target temperature Ts of the hot water heat exchanger 3, the pressure of the compressor 1 that supplies the refrigerant to the air heat exchange is increased.
- the discharge pressure may be a pressure corresponding to the target temperature Ts of the hot water heat exchanger 3. Therefore, it is not necessary to fix the discharge pressure of the compressor to a discharge pressure corresponding to the maximum target temperature that can be set for the hot water heat exchanger.
- the refrigeration apparatus of the present embodiment can minimize the discharge pressure of the compressor 1 according to the target temperature T s, thereby effectively reducing the power consumption of the motor of the compressor 1. be able to.
- the refrigerant pressure in the air heat exchanger 6 is It is possible to prevent the refrigerant pressure from being greatly reduced with respect to the refrigerant pressure, and, consequently, to reduce the flow rate of the refrigerant supplied to the air-to-air heat exchanger 6 to a necessary minimum. Accordingly, a larger flow rate of refrigerant than before can be supplied to the hot water heat exchange 3 to which the refrigerant is supplied together with the air heat exchanger 6 by the discharge three-way valve 8. As a result, the temperature control of the water by the hot water heat exchanger 3 can be performed with higher precision than before.
- the control device 19 performs heat exchange in the hot water heat exchange 3.
- the target pressure value P s of the refrigerant in the air heat exchanger 6 is determined according to the target temperature value T s of the water to be discharged.
- the target temperature T s is determined based on the detection value Tm of the hot water temperature sensor 17. And make modifications. Thereby, for example, when the heat load of the hot water heat exchanger 3 fluctuates, the pressure of the air heat exchange m3 ⁇ 46 is appropriately controlled in accordance with the actual condensation pressure of the hot water heat exchange 3. be able to.
- the difference between the condensing pressure of the hot water heat exchanger 3 and the condensing pressure of the air heat exchanger 6 can be effectively reduced, and the stagnation phenomenon of the refrigerant in the air heat exchanger 6 can be stabilized. It can be reliably prevented. Further, the power consumption of the compressor 1 can be effectively reduced.
- the control device 19 sets the target pressure value Ps of the refrigerant of the air heat exchange 6 in accordance with the target temperature value Ts of the water to be heat-exchanged in the hot water heat exchanger 3.
- the target pressure value Ps may be set according to the detection value Tm of the hot water temperature sensor 17.
- the pressure of the air heat exchanger 6 can be appropriately controlled according to the actual heat load of the hot water heat exchanger 3.
- the difference between the condensing pressure of the hot water heat exchanger 3 and the condensing pressure of the air heat exchanger 6 can be effectively reduced, and the stagnation phenomenon of the refrigerant in the air heat exchanger 6 can be stabilized. It can be reliably prevented.
- the discharge pressure of the compressor 1 is a pressure that matches the actual heat load of the hot water heat exchanger 3 and can be reduced to the minimum necessary discharge pressure, the power consumption of the compressor 1 is effectively reduced. Can be reduced.
- the discharge three-way valve 8 and the suction three-way valve 9 may have any function as long as they have a function of connecting one port to the other two ports by changing the opening degree.
- a format such as Further, a plurality of switching valves and the like may be used in combination so as to perform the same function as the function of the three-way valve.
- water was used as the first liquid heat medium and the second liquid heat medium, but one or both of the first liquid heat medium and the second liquid heat medium may be other than water, for example.
- a brine such as an ethylene dalicol-based solution may be used.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Separation Using Semi-Permeable Membranes (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE602004010095T DE602004010095D1 (de) | 2003-05-15 | 2004-05-13 | Kühlvorrichtung |
US10/556,818 US7426837B2 (en) | 2003-05-15 | 2004-05-13 | Refrigerator |
EP04732772A EP1624262B1 (en) | 2003-05-15 | 2004-05-13 | Refrigerator |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003136941A JP3972860B2 (ja) | 2003-05-15 | 2003-05-15 | 冷凍装置 |
JP2003-136941 | 2003-05-15 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004102086A1 true WO2004102086A1 (ja) | 2004-11-25 |
Family
ID=33447241
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/006764 WO2004102086A1 (ja) | 2003-05-15 | 2004-05-13 | 冷凍装置 |
Country Status (8)
Country | Link |
---|---|
US (1) | US7426837B2 (ja) |
EP (1) | EP1624262B1 (ja) |
JP (1) | JP3972860B2 (ja) |
CN (1) | CN100340827C (ja) |
AT (1) | ATE378559T1 (ja) |
DE (1) | DE602004010095D1 (ja) |
ES (1) | ES2297421T3 (ja) |
WO (1) | WO2004102086A1 (ja) |
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EP1637818A1 (en) * | 2003-06-13 | 2006-03-22 | Daikin Industries, Ltd. | Freezer apparatus |
WO2006100709A1 (en) * | 2005-03-24 | 2006-09-28 | Lambda S.P.A. | Integrated system for the production op hot and cold to be used simultaneously by cooling and heating units |
WO2008079119A1 (en) * | 2006-12-22 | 2008-07-03 | Carrier Corporation | Methods and systems for controlling air conditioning systems having a cooling mode and a free-cooling mode |
EP2730861A2 (en) | 2012-11-05 | 2014-05-14 | Compañia Industrial De Aplicaciones Termicas, S.A. | Refrigeration circuit for an air-conditioning machine. |
EP1684034B1 (en) * | 2004-12-30 | 2014-05-21 | Nakayama Engineering Company Limited | Refrigeration apparatus and method for controlling the same |
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2003
- 2003-05-15 JP JP2003136941A patent/JP3972860B2/ja not_active Expired - Fee Related
-
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- 2004-05-13 EP EP04732772A patent/EP1624262B1/en not_active Expired - Lifetime
- 2004-05-13 CN CNB2004800132024A patent/CN100340827C/zh not_active Expired - Fee Related
- 2004-05-13 ES ES04732772T patent/ES2297421T3/es not_active Expired - Lifetime
- 2004-05-13 DE DE602004010095T patent/DE602004010095D1/de not_active Expired - Lifetime
- 2004-05-13 US US10/556,818 patent/US7426837B2/en not_active Expired - Fee Related
- 2004-05-13 WO PCT/JP2004/006764 patent/WO2004102086A1/ja active IP Right Grant
- 2004-05-13 AT AT04732772T patent/ATE378559T1/de not_active IP Right Cessation
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Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1637818A1 (en) * | 2003-06-13 | 2006-03-22 | Daikin Industries, Ltd. | Freezer apparatus |
EP1637818A4 (en) * | 2003-06-13 | 2006-08-02 | Daikin Ind Ltd | FREEZING APPARATUS |
US7594409B2 (en) | 2003-06-13 | 2009-09-29 | Daikin Industries, Ltd. | Freezer apparatus |
EP1684034B1 (en) * | 2004-12-30 | 2014-05-21 | Nakayama Engineering Company Limited | Refrigeration apparatus and method for controlling the same |
WO2006100709A1 (en) * | 2005-03-24 | 2006-09-28 | Lambda S.P.A. | Integrated system for the production op hot and cold to be used simultaneously by cooling and heating units |
WO2008079119A1 (en) * | 2006-12-22 | 2008-07-03 | Carrier Corporation | Methods and systems for controlling air conditioning systems having a cooling mode and a free-cooling mode |
US8117859B2 (en) | 2006-12-22 | 2012-02-21 | Carrier Corporation | Methods and systems for controlling air conditioning systems having a cooling mode and a free-cooling mode |
EP2730861A2 (en) | 2012-11-05 | 2014-05-14 | Compañia Industrial De Aplicaciones Termicas, S.A. | Refrigeration circuit for an air-conditioning machine. |
Also Published As
Publication number | Publication date |
---|---|
CN1788185A (zh) | 2006-06-14 |
CN100340827C (zh) | 2007-10-03 |
DE602004010095D1 (de) | 2007-12-27 |
ATE378559T1 (de) | 2007-11-15 |
JP3972860B2 (ja) | 2007-09-05 |
EP1624262B1 (en) | 2007-11-14 |
US20070051119A1 (en) | 2007-03-08 |
ES2297421T3 (es) | 2008-05-01 |
JP2004340470A (ja) | 2004-12-02 |
US7426837B2 (en) | 2008-09-23 |
EP1624262A1 (en) | 2006-02-08 |
EP1624262A4 (en) | 2006-08-02 |
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