EP1830143A2 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

Info

Publication number
EP1830143A2
EP1830143A2 EP07004366A EP07004366A EP1830143A2 EP 1830143 A2 EP1830143 A2 EP 1830143A2 EP 07004366 A EP07004366 A EP 07004366A EP 07004366 A EP07004366 A EP 07004366A EP 1830143 A2 EP1830143 A2 EP 1830143A2
Authority
EP
European Patent Office
Prior art keywords
expansion mechanism
revolutions
refrigeration cycle
pressure
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07004366A
Other languages
English (en)
French (fr)
Other versions
EP1830143A3 (de
Inventor
Noriho c/o Matsushita Electric Industrial Co. Ltd. Okaza
Kazuo Matsushita Electric Industrial Co. Ltd. Nakatani
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Corp
Original Assignee
Panasonic Corp
Matsushita Electric Industrial Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Panasonic Corp, Matsushita Electric Industrial Co Ltd filed Critical Panasonic Corp
Publication of EP1830143A2 publication Critical patent/EP1830143A2/de
Publication of EP1830143A3 publication Critical patent/EP1830143A3/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • F25B2400/141—Power generation using energy from the expansion of the refrigerant the extracted power is not recycled back in the refrigerant circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • 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
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a refrigeration cycle apparatus having an expansion mechanism which collects power.
  • expansion mechanism is provided instead of a decompressor, pressure energy at the time of expansion is collected as power, and COP is enhanced (see patent document 1 for example).
  • Such expansion mechanisms can roughly divided into two types due to a difference in power collecting method.
  • One of the types is a type (mechanical energy collecting type, hereinafter) in which an expansion mechanism and a rotation shaft of a compressing mechanism are connected to one shaft, and power generated by the expansion mechanism is transferred to the compressing mechanism as mechanical energy (rotation energy).
  • the other type is a type (electric energy collecting type, hereinafter) in which a generator is connected to a rotation shaft of an expansion mechanism, and power generated in the expansion mechanism is collected as electric energy.
  • Hzc represents the number of revolutions of the compressing mechanism
  • Hze represents the number of revolutions of the expansion mechanism
  • both the compressing mechanism and expansion mechanism are of positive-displacement type
  • VC represents a cylinder capacity of a compressor
  • VE represents a cylinder capacity of the expansion mechanism
  • DC represents density of refrigerant flowing into the compressing mechanism
  • a structure and a control method in which a bypass flow path bypassing the expansion mechanism is provided, and a decompressor is provided upstream or downstream of the expansion mechanism, a circulation amount flowing into the expansion mechanism is controlled, thereby adjusting the pressure to the optimal high pressure-side pressure.
  • a structure and a control method in which heat is exchanged using an internal heat exchanger, thereby changing the density of refrigerant flowing into the expansion mechanism, and a circulation amount flowing into the expansion mechanism is controlled, thereby adjusting the pressure to the optimal high pressure-side pressure (e.g., see patent document 2).
  • Patent Document 1 Japanese Patent Application Laid-open No.S56-112896
  • Patent Document 2 Japanese Patent Application Laid-open No.2000-329416
  • the refrigeration cycle apparatus of the present invention comprises a compressing mechanism, a heat source-side heat exchanger, an expansion mechanism which collects power and has number of revolutions which can be changed independently from number of revolutions of the compressing mechanism, a utilizing-side heat exchanger, and a pre-decompressor for decompressing a refrigerant flowing into the expansion mechanism.
  • a refrigeration cycle apparatus comprising at least a compressing mechanism, a heat source-side heat exchanger, an expansion mechanism which collects power and has number of revolutions which can be changed independently from number of revolutions of the compressing mechanism, a utilizing-side heat exchanger, and a pre-decompressor for decompressing a refrigerant flowing into the expansion mechanism.
  • the refrigeration cycle apparatus further includes a bypass circuit through which a portion of the refrigerant flowing into the expansion mechanism bypasses directly to a low pressure-side flow path.
  • a third aspect of the invention when any one of a high pressure-side pressure, a discharge temperature of the compressing mechanism, and a sucked superheat of the compressing mechanism does not reach a preset target value even if the number of revolutions of the expansion mechanism reaches a preset lowest number of revolutions, the refrigerant is decompressed by the pre-decompressor.
  • the high pressure-side pressure can be adjusted to a preferable pressure, refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism.
  • a portion of the refrigerant flowing into the expansion mechanism is allowed to bypass.
  • the high pressure-side pressure can be adjusted to a preferable pressure, refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism.
  • the refrigeration cycle apparatus further comprises an internal heat exchanger for cooling the refrigerant flowing into the expansion mechanism.
  • a sixth aspect of the invention when any one of a high pressure-side pressure, a discharge temperature of the compressing mechanism, and a sucked superheat of the compressing mechanism does not reach a preset target value even if the number of revolutions of the expansion mechanism reaches a preset lowest number of revolutions, the internal heat exchanger is not substantially operated.
  • the high pressure-side pressure can be adjusted to a preferable pressure, refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism.
  • a seventh aspect of the invention when any one of a high pressure-side pressure, a discharge temperature of the compressing mechanism, and a sucked superheat of the compressing mechanism exceeds a preset target value even if the number of revolutions of the expansion mechanism reaches a preset highest number of revolutions, the internal heat exchanger is substantially operated.
  • the high pressure-side pressure can be adjusted to a preferable pressure, refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism.
  • a refrigeration cycle apparatus having a compressing mechanism, a heat source-side heat exchanger, an expansion mechanism for collecting power, a utilizing-side heat exchanger, and an internal heat exchanger for cooling a refrigerant flowing into the expansion mechanism, only when any one of a high pressure-side pressure, a discharge temperature of the compressing mechanism, and a sucked superheat of the compressing mechanism does not reach a preset target value even if the internal heat exchanger is not substantially operated, the number of revolutions of the expansion mechanism is reduced. With this, the possibility of reduction in the number of revolutions of the expansion mechanism that may deteriorate the reliability of the expansion mechanism can be lowered. Thus, the refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism.
  • a ninth aspect of the invention only when any one of a high pressure-side pressure, a discharge temperature of the compressing mechanism, and a sucked superheat of the compressing mechanism exceeds a preset target value even if the internal heat exchanger is substantially operated, the number of revolutions of the expansion mechanism is increased. With this, the possibility of reduction in the number of revolutions of the expansion mechanism that may deteriorate the reliability of the expansion mechanism can be lowered. Thus, the refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism.
  • FIG. 1 schematically shows a structure thereof.
  • the refrigeration cycle apparatus shown in Fig. 1 includes a compressing mechanism 2 driven by an electric motor 1, a refrigerant flow path of a radiator 3 as a utilizing-side heat exchanger, an expansion mechanism 5 whose power is collected by a generator 4, an evaporator 6 as a heat source-side heat exchanger, a refrigerant circuit A into which CO 2 refrigerant is charged as a refrigerant, and a fluid circuit B comprising a water supply pump 7 as utilizing fluid transfer means, a fluid flow path of the radiator 3, and a boiler 8.
  • the refrigerant circuit A includes the following constituent elements.
  • An air blowing apparatus 9 as heat source fluid transfer means blows heat source fluid (e.g., outside air) to the evaporator 6.
  • a pre-expansion valve 11 as a pre-decompressor previously decompresses refrigerant flowing into the expansion mechanism 5, and reduces the density of the refrigerant flowing into the expansion mechanism 5.
  • a first bypass flow path 12 connects a refrigerant outlet of the radiator 3 and an inlet of the expansion mechanism 5 with each other, and an outlet of the expansion mechanism 5 and an inlet of the compressing mechanism 2 with each other, so that refrigerant flowing through the expansion mechanism 5 bypasses.
  • the first bypass flow path 12 includes a first bypass valve 13 which adjusts a circulation amount of refrigerant to be bypassed.
  • An internal heat exchanger 14 is arranged so that refrigerant from the refrigerant outlet of the radiator 3 flowing through a high pressure-side flow path 14a to an inlet of the expansion mechanism 5 is cooled by refrigerant from the refrigerant outlet of the evaporator 6 flowing through a low pressure-side flow path 14b to an inlet of the compressing mechanism 2.
  • Discharge temperature detecting means 20 is disposed on a refrigerant pipe from discharge of the compressing mechanism 2 to a refrigerant inlet of the radiator 3, and the discharge temperature detecting means 20 detects the discharge temperature of the compressing mechanism 2.
  • Expansion mechanism revolution number control means 21 controls the number of revolutions of the generator 4.
  • Pre-expansion valve opening control means 22 adjusts the opening of the pre-expansion valve 11.
  • First bypass valve opening control means 23 adjusts the opening of the first bypass valve 13.
  • Electronic control means 25 determines a state of the refrigeration cycle from a signal from the discharge temperature detecting means 20 and the like, and sends instructions to the expansion mechanism revolution number control means 21, the pre-expansion valve opening control means 22 and the first bypass valve opening control means 23.
  • a product X (Hze / Hzc) of a density ratio and a ratio of the number of revolutions (DE / DC) X (Hze / Hzc) in the actual operating state is substantially equal to a design capacity ratio (VC / VE) which was assumed at the time of designing.
  • CO 2 refrigerant is compressed by the compressing mechanism 2 to a pressure (high pressure-side pressure) exceeding critical pressure.
  • the compressed refrigerant is brought into a high temperature and high pressure state, and when the refrigerant flows through the refrigerant flow path of the radiator 3, the refrigerant radiates heat to water flowing through the fluid flow path of the radiator 3 and is cooled. Then, the refrigerant flows into the high pressure-side flow path 14a of the internal heat exchanger 14, and is further cooled by low pressure and low temperature refrigerant flowing through the low pressure-side flow path 14b.
  • the first bypass valve 13 is in its fully closed state, the refrigerant does not through the first bypass flow path 12, and all of refrigerants flow into the expansion mechanism 5 through the fully-opened pre-expansion valve 11. Thereafter, the refrigerant is decompressed by the expansion mechanism 5 and is brought into a low temperature and low pressure gas/liquid two-phase state.
  • the refrigeration cycle apparatus of the embodiment can be utilized as a water heater.
  • fluid e.g., water
  • high temperature fluid e.g., hot water
  • the product X (Hze / Hzc) of the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc) in the actual operating state is different from the design capacity ratio (VC / VE) which was assumed at the time of designing will be explained.
  • an operation when the product Xof the density ratio and the ratio of the number of revolutions in the actual operating state (DE / DC) X (Hze / Hzc) is greater than the design capacity ratio (VC / VE) which was assumed at the time of designing will be explained.
  • the refrigeration cycle tries to balance in a state where the high pressure-side pressure is reduced such that the refrigerant density (DE) of the inlet of the expansion mechanism 5 becomes small.
  • the discharge temperature is lowered, the heating ability of the refrigeration cycle apparatus is deteriorated and the efficiency of the refrigeration cycle apparatus is deteriorated. Therefore, first the number of revolutions of the expansion mechanism 5 is operated in the reducing direction, thereby lowering the product Xof the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc). With this, the high pressure-side pressure is not reduced and the optimal state can be maintained.
  • the lowest number of revolutions of the expansion mechanism 5 is preset in terms of reliability of the expansion mechanism 5. That is, if the expansion mechanism 5 is operated for a long term with the number of revolutions lower than the preset lowest number of revolutions, oil is less prone to be supplied to a sliding portion of the expansion mechanism, and there is an adverse possibility of inconvenience that the sliding portion is worn.
  • the refrigerant density (DE) can be made smaller without deteriorating the reliability of the expansion mechanism 5, the high pressure-side pressure is not lowered, and the optimal state can be maintained.
  • the high pressure-side pressure is increased higher than a preferable pressure, the operation efficiency of the refrigeration cycle apparatus is lowered. Therefore, first, the number of revolutions of the expansion mechanism 5 is operated in the increasing direction, and the product Xof the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc) is increased. With this, the high pressure-side pressure is not increased and the optimal state can be maintained.
  • the highest number of revolutions of the expansion mechanism 5 is preset. That is, if the expansion mechanism 5 is operated for a long term with the number of revolutions higher than the preset highest number of revolutions, there is an adverse possibility of inconvenience that the bearing of the expansion mechanism and the sliding portion are worn.
  • the first bypass valve 13 is operated in the opening direction so that a portion of the refrigerant is allowed to flow to the first bypass flow path 12.
  • the number of revolutions of the expansion mechanism 5 becomes higher than the highest number of revolutions, the circulation amount of refrigerant flowing into the expansion mechanism 5 can be reduced without deteriorating the reliability of the expansion mechanism 5, the high pressure-side pressure does not rise and the optimal state can be maintained.
  • the first bypass valve 13 is operated in the opening direction instead of increasing the number of revolutions of the expansion mechanism 5. With this, the high pressure-side pressure can be adjusted to the preferable pressure. Therefore, the refrigeration cycle apparatus can be operated efficiently without deteriorating the reliability of the expansion mechanism 5.
  • the compressing mechanism 2, i.e., the electric motor 1 which is substantially a driving source is controlled by the compressing mechanism revolution number control means (not shown) such that the number of revolutions thereof becomes equal to the number of revolutions calculated by the electronic control apparatus 25 from the outside air temperature or the entering-water temperature detected by the outside air temperature detecting means (not shown) or the entering-water temperature detecting means (not shown), or a target billowing temperature which was set by a user (temperature of hot water stored in the boiler, or a target value of fluid outlet side temperature of the radiator 3).
  • the control performed by the electronic control apparatus 25, the expansion mechanism revolution number control means 21, the pre-expansion valve opening control means 22 and the first bypass valve opening control means 23 will be explained based on the flowchart shown in Fig. 2.
  • An expensive sensor is required to measure the high pressure-side pressure. According to the control of this embodiment, the high pressure-side pressure is not measured, and the expansion mechanism 5, the pre-expansion valve 11 and the first bypass valve 13 are controlled using the discharge temperature which can be measured relatively inexpensively using a correlation between the high pressure-side pressure and the discharge temperature.
  • a detection value (discharge temperature: Td) (100) from the discharge temperature detecting means 20 is taken in.
  • a target discharge temperature (target Td) which is previously stored in a ROM or the like and the taken discharge temperature (Td) are compared with each other (110). If the discharge temperature (Td) is lower than the target discharge temperature (target Td), there is a tendency that the high pressure-side pressure is lower than the optimal pressure and thus, it is determined whether the first bypass valve 13 is fully closed (120). When the first bypass valve 13 is fully closed, it is determined whether the number of revolutions (Hze) of the expansion mechanism 5 reaches the preset lowest number of revolutions (lowest Hze) (130).
  • the pre-expansion valve 11 is operated in the closing direction (140), refrigerant flowing into the expansion mechanism 5 is decompressed, the refrigerant density is lowered, and the high pressure-side pressure and the discharge temperature are increased.
  • the number of revolutions (Hze) of the expansion mechanism 5 does not reach the preset lowest number of revolutions (lowest Hze)
  • the number of revolutions (Hze) of the expansion mechanism 5 is operated in the lowering direction (150)
  • the circulation amount of refrigerant flowing through the expansion mechanism 5 is reduced, and the high pressure-side pressure and the discharge temperature are increased.
  • the first bypass valve 13 is not fully closed in step 120, the first bypass valve 13 is operated in the closing direction (160), the circulation amount of refrigerant which bypasses the expansion mechanism 5 and flows into the first bypass flow path 12 is reduced, and the high pressure-side pressure and the discharge temperature are increased.
  • the pre-expansion valve 11 is fully opened (170). If the pre-expansion valve 11 is fully opened, it is determined whether the number of revolutions (Hze) of the expansion mechanism 5 reaches the preset highest number of revolutions (highest Hze) (180).
  • the first bypass valve 13 When the number of revolutions (Hze) of the expansion mechanism 5 reaches the present highest number of revolutions (highest Hze), the first bypass valve 13 is operated in the opening direction (190), the circulation amount of refrigerant which bypasses the expansion mechanism 5 and flows into the first bypass flow path 12 is increased, and the high pressure-side pressure and the discharge temperature are lowered.
  • the number of revolutions (Hze) of the expansion mechanism 5 does not reach the preset highest number of revolutions (highest Hze)
  • the number of revolutions (Hze) of the expansion mechanism 5 is operated in the increasing direction (200)
  • the circulation amount of refrigerant flowing through the expansion mechanism 5 is increased, and the high pressure-side pressure and the discharge temperature are lowered.
  • the pre-expansion valve 11 is not fully opened in step 170, the pre-expansion valve 11 is operated in the opening direction (210) so that the refrigerant flowing into the expansion mechanism 5 is not decompressed, and the refrigerant density is not lowered. With this, the high pressure-side pressure and the discharge temperature are lowered.
  • step 100 the procedure is returned to step 100, and steps 100 to 210 are repeated, and the number of revolutions of the expansion mechanism 5, the pre-expansion valve 11 and the opening of the first bypass valve 13 are controlled in liaison with each other as shown in Fig. 3.
  • the refrigeration cycle apparatus of the embodiment including the electric energy collecting type expansion mechanism even if the number of revolutions of the expansion mechanism 5 is reduced within the using range, if the discharge temperature (Td) does not reach the target discharge temperature (target Td), the pre-expansion valve 11 is operated in the closing direction based on the discharge temperature and the refrigerant is decompressed. With this, the pressure can be adjusted to a desired high pressure-side pressure without exceeding the using range of the expansion mechanism 5, and the refrigeration cycle apparatus can be operated without deteriorating its operating efficiency and ability.
  • the first bypass valve 13 is operated in the opening direction based on the discharge temperature to flow a portion of the refrigerant into the first bypass flow path 12.
  • FIG. 4 is a schematic diagram showing a structure of the refrigeration cycle apparatus.
  • the refrigeration cycle apparatus shown in Fig. 4 includes a second bypass flow path 31 bypassing the high pressure-side flow path 14a of the internal heat exchanger 14, and a second bypass valve 32 which adjusts a circulation amount of refrigerant flowing through the second bypass flow path 31.
  • a second bypass valve opening control means 33 adjusts the opening of the second bypass valve 32.
  • CO 2 refrigerant is compressed by the compressing mechanism 2 to a pressure (high pressure-side pressure) exceeding critical pressure.
  • the compressed refrigerant is brought into a high temperature and high pressure state, and when the refrigerant flows through the refrigerant flow path of the radiator 3, the refrigerant radiates heat to water flowing through the fluid flow path of the radiator 3 and is cooled.
  • the refrigerant does not through the second bypass flow path 31 due to the fully closed second bypass valve 32, but flows into the high pressure-side flow path 14a of the internal heat exchanger 14, and the refrigerant is further cooled by a low pressure and low temperature refrigerant which flows through the low pressure-side flow path 14b.
  • the first bypass valve 13 is also fully closed, the refrigerant does not through the first bypass flow path 12, and all of refrigerants flow into the expansion mechanism 5.
  • the refrigerant is decompressed by the expansion mechanism 5 and is brought into a low temperature and low pressure gas/liquid two-phase state.
  • pressure energy of the refrigerant is converted into power, and the power is converted into electricity by the generator 4.
  • the pressure energy at the time of expansion can be collected as electricity and the COP can be enhanced.
  • Refrigerant decompressed by the expansion mechanism 5 is supplied to the evaporator 6.
  • the refrigerant is heated by the outside air sent by the air blowing apparatus 9, and the refrigerant is brought into a gas/liquid two-phase state or a gaseous state.
  • Refrigerant which flows out from the evaporator 6 is heated by the low pressure-side flow path 14b of the internal heat exchanger 14 and then, the refrigerant is again sucked into the compressing mechanism 2.
  • the product Xof the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc) in the actual operating state is different from the design capacity ratio (VC / VE) which was assumed at the time of designing will be explained.
  • an operation when the product X (Hze / Hzc) of the density ratio and the ratio of the number of revolutions in the actual operating state (DE / DC) X (Hze / Hzc) is greater than the design capacity ratio (VC / VE) which was assumed at the time of designing will be explained.
  • the refrigeration cycle tries to balance in a state where the high pressure-side pressure is reduced such that the refrigerant density (DE) of the inlet of the expansion mechanism 5 becomes small.
  • the discharge temperature is lowered, the heating ability of the refrigeration cycle apparatus is deteriorated and the efficiency of the refrigeration cycle apparatus is deteriorated. Therefore, first the number of revolutions of the expansion mechanism 5 is operated in the reducing direction, thereby lowering the product (DE / DC) X (Hze / Hzc) of the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc). With this, the high pressure-side pressure is not reduced and the optimal state can be maintained.
  • the lowest number of revolutions of the expansion mechanism 5 is preset in terms of reliability of the expansion mechanism 5. That is, if the expansion mechanism 5 is operated for a long term with the number of revolutions lower than the preset lowest number of revolutions, oil is less prone to be supplied to a sliding portion of the expansion mechanism, and there is an adverse possibility of inconvenience that the sliding portion is worn.
  • the second bypass valve 32 is operated in the opening direction to flow the refrigerant into the second bypass flow path 31, and the circulation amount of refrigerant flowing into the high pressure-side flow path 14a of the internal heat exchanger 14 is reduced.
  • the heat exchanging amount at the internal heat exchanger 14 is reduced, and the density (DE) of refrigerant flowing into the expansion mechanism 5 is reduced. Therefore, the number of revolutions of the expansion mechanism 5 becomes lower than the lowest number of revolutions, the refrigerant density (DE) can be reduced without deteriorating the reliability of the expansion mechanism 5, the high pressure-side pressure is not lowered, and the optimal state can be maintained.
  • the opening of the second bypass valve 32 is operated in the opening direction instead of reducing the number of revolutions of the expansion mechanism 5, and the internal heat exchanging amount is reduced.
  • the high pressure-side pressure can be adjusted to a desired value and thus, the refrigeration cycle apparatus can be operated efficiently without deteriorating the reliability of the expansion mechanism 5.
  • a detection value (discharge temperature: Td) (300) from the discharge temperature detecting means 20 is taken in.
  • a target discharge temperature (target Td) which is previously stored in a ROM or the like and the taken discharge temperature (Td) are compared with each other (310). If the discharge temperature (Td) is lower than the target discharge temperature (target Td), there is a tendency that the high pressure-side pressure is lower than the optimal pressure and thus, it is determined whether the first bypass valve 13 is fully closed (320). When the first bypass valve 13 is fully closed, it is determined whether the number of revolutions (Hze) of the expansion mechanism 5 reaches the preset lowest number of revolutions (lowest Hze) (330).
  • the second bypass valve 32 is operated in the opening direction (340), and the circulation amount of refrigerant flowing into the high pressure-side flow path 14a of the internal heat exchanger 14 is reduced.
  • the density of refrigerant flowing into the expansion mechanism 5 is lowered, and the high pressure-side pressure and the discharge temperature are increased.
  • the number of revolutions (Hze) of the expansion mechanism 5 does not reach the preset lowest number of revolutions (lowest Hze)
  • the number of revolutions (Hze) of the expansion mechanism 5 is operated in the lowering direction (350)
  • the circulation amount of refrigerant flowing through the expansion mechanism 5 is reduced, and the high pressure-side pressure and the discharge temperature are increased.
  • the first bypass valve 13 is not fully closed in step 320, the first bypass valve 13 is operated in the closing direction (360), the circulation amount of refrigerant which bypasses the expansion mechanism 5 and flows into the first bypass flow path 12 is reduced, and the high pressure-side pressure and the discharge temperature are increased.
  • the second bypass valve 32 is fully closed (370). If the second bypass valve 32 is fully closed, it is determined whether the number of revolutions (Hze) of the expansion mechanism 5 reaches the preset highest number of revolutions (highest Hze) (380).
  • the first bypass valve 13 When the number of revolutions (Hze) of the expansion mechanism 5 reaches the present highest number of revolutions (highest Hze), the first bypass valve 13 is operated in the opening direction (390), the circulation amount of refrigerant which bypasses the expansion mechanism 5 and flows into the first bypass flow path 12 is increased, and the high pressure-side pressure and the discharge temperature are lowered. If the number of revolutions (Hze) of the expansion mechanism 5 does not reach the preset highest number of revolutions (highest Hze), the number of revolutions (Hze) of the expansion mechanism 5 is operated in the increasing direction (400), the circulation amount of refrigerant flowing through the expansion mechanism 5 is increased, and the high pressure-side pressure and the discharge temperature are lowered.
  • the second bypass valve 32 is operated in the closing direction (410), and the circulation amount of refrigerant flowing into the high pressure-side flow path 14a of the internal heat exchanger 14 is increased.
  • the density of refrigerant flowing into the expansion mechanism 5 is increased by increasing the heat exchanging amount in the internal heat exchanger 14, and the high pressure-side pressure and the discharge temperature are lowered.
  • the second bypass valve 32 is operated in the opening direction based on the discharge temperature to flow a portion of refrigerant into the second bypass flow path 31, thereby reducing the heat exchanging amount in the internal heat exchanger 14 so that the refrigerant is not cooled.
  • the first bypass valve 13 is operated in the opening direction based on the discharge temperature to flow a portion of the refrigerant into the first bypass flow path 12.
  • FIG. 7 is a schematic diagram showing a structure of the refrigeration cycle apparatus.
  • the same constituent elements as those shown in Figs. 1 and 4 are designated with the same symbols, and explanation thereof will be omitted.
  • the action of the refrigeration cycle apparatus when it is operated will be explained based on a case where the product Xof the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc) in the actual operating state is substantially the same as the design capacity ratio (VC / VE) which was assumed at the time of designing.
  • CO2 refrigerant is compressed by the compressing mechanism 2 to a pressure (high pressure-side pressure) exceeding critical pressure.
  • the compressed refrigerant is brought into a high temperature and high pressure state, and when the refrigerant flows through the refrigerant flow path of the radiator 3, the refrigerant radiates heat to water flowing through the fluid flow path of the radiator 3 and is cooled. Then, the refrigerant does not flow through the high pressure-side flow path 14a of the internal heat exchanger 14 due to the fully opened second bypass valve 32 but flows into the second bypass flow path 31, and flows into the expansion mechanism 5 through the fully opened pre-expansion valve 11.
  • the refrigerant is decompressed by the expansion mechanism 5 and brought.into the low temperature and low pressure gas/liquid two-phase state. At that time, in the expansion mechanism 5. the pressure energy of the refrigerant is converted into power and the power is converted into electricity by the generator 4.
  • the pressure energy at the time of expansion can be collected as electricity and the COP can be enhanced.
  • Refrigerant decompressed by the expansion mechanism 5 is supplied to the evaporator 6.
  • the refrigerant is heated by the outside air sent by the air blowing apparatus 9, and the refrigerant is brought into a gas/liquid two-phase state or a gaseous state.
  • the refrigerant which flows out from the evaporator 6 flows into the low pressure-side flow path 14b of the internal heat exchanger 14, but since almost no refrigerant flows into the high pressure-side flow path 14a, heat is not exchanged substantially, and the refrigerant is sucked into the compressing mechanism 2 again.
  • the product Xof the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc) in the actual operating state is different from the design capacity ratio (VC / VE) which was assumed during designing will be explained.
  • the operation when the product (DE / DC) X (Hze / Hzc) of the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc) in the actual operating state is greater than the design capacity ratio (VC / VE) which was assumed at the time of designing is the same as that explained in the (first embodiment), explanation thereof will be omitted.
  • the number of revolutions of the expansion mechanism 5 is operated in the increasing direction, and the product (DE / DC) (X (Hze / Hzc) of the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc) is increased.
  • the high pressure-side pressure is not increased, and the optimal state can be maintained.
  • the highest number of revolutions of the expansion mechanism 5 is preset in terms of reliability of the expansion mechanism 5. That is, if the expansion mechanism 5 is operated form a long term with the number of revolutions higher than the preset lowest number of revolutions, there is a possibility of inconvenience that the bearing of the expansion mechanism and the sliding portion are worn.
  • the second bypass valve 32 is operated in the closing direction, and the circulation amount of refrigerant flowing into the high pressure-side flow path 14a of the internal heat exchanger 14 is increased.
  • the heat exchanging amount in the internal heat exchanger 14 is increased, and the density (DE) of refrigerant flowing into the expansion mechanism 5 is increased. Therefore, the number of revolutions exceeds the highest number of revolutions of the expansion mechanism 5, the refrigerant density (DE) can be increased without deteriorating the reliability of the expansion mechanism 5, the high pressure-side pressure is not increased and the optimal state can be maintained.
  • the opening of the second bypass valve 32 is operated in the closing direction instead of increasing the number of revolutions of the expansion mechanism 5, and the internal heat exchanging amount is increased.
  • the high pressure-side pressure can be adjusted to a desired value and thus, the refrigeration cycle apparatus can be operated efficiently without deteriorating the reliability of the expansion mechanism 5.
  • the second bypass valve 32 is fully opened (520).
  • the second bypass valve 32 it is determined whether the number of revolutions (Hze) of the expansion mechanism 5 reaches the preset lowest number of revolutions (lowest Hze) (530). If the number of revolutions (Hze) of the expansion mechanism 5 reaches the preset lowest number of revolutions (lowest Hze), the pre-expansion valve 11 is operated in the closing direction (540), refrigerant flowing into the expansion mechanism 5 is decompressed, the refrigerant density is lowered, and the high pressure-side pressure and the discharge temperature are increased.
  • the number of revolutions (Hze) of the expansion mechanism 5 When the number of revolutions (Hze) of the expansion mechanism 5 does not reach the preset lowest number of revolutions (lowest Hze), the number of revolutions (Hze) of the expansion mechanism 5 is operated in the reducing direction (550), the circulation amount of refrigerant flowing through the expansion mechanism 5 is reduced, and the high pressure-side pressure and the discharge temperature are increased.
  • the second bypass valve 32 When the second bypass valve 32 is not fully opened in step 520, the second bypass valve 32 is operated in the opening direction (560), and the circulation amount of refrigerant flowing into the high pressure-side flow path 14a of the internal heat exchanger 14 is reduced.
  • the density of refrigerant flowing into the expansion mechanism 5 is reduced by reducing the heat exchanging amount in the internal heat exchanger 14, and the high pressure-side pressure and the discharge temperature are increased.
  • step 510 If the discharge temperature (Td) is higher than the target discharge temperature (target Td) in step 510, there is a tendency that the high pressure-side pressure is higher than the optimal pressure and thus, it is determined whether the pre-expansion valve 11 is fully opened (570). If the pre-expansion valve 11 is fully opened, it is determined whether the number of revolutions (Hze) of the expansion mechanism 5 reaches the preset highest number of revolutions (highest Hze) (580).
  • the second bypass valve 32 is operated in the closing direction (590), refrigerant flowing into the expansion mechanism 5 is cooled by the internal heat exchanger 14, and the refrigerant density is increased, thereby lowering the high pressure-side pressure and the discharge temperature. If the number of revolutions (Hze) of the expansion mechanism 5 does not reach the preset highest number of revolutions (highest Hze), the number of revolutions (Hze) of the expansion mechanism 5 is operated in the increasing direction (600), the circulation amount of refrigerant flowing through the expansion mechanism 5 is increased, and the high pressure-side pressure and the discharge temperature are lowered.
  • step 570 If the pre-expansion valve 11 is not fully opened in step 570, the pre-expansion valve 11 is operated in the opening direction (610) so that the refrigerant flowing into the expansion mechanism 5 is not decompressed, and the refrigerant density is not lowered. With this, the high pressure-side pressure and the discharge temperature are lowered. After these steps, the procedure is returned to step 500, and steps 500 to 610 are repeated, and the number of revolutions of the expansion mechanism 5, the pre-expansion valve 11 and the opening of the second bypass valve 32 are controlled in liaison with each other as shown in Fig. 9.
  • the refrigeration cycle apparatus of the embodiment including the electric energy collecting type expansion mechanism even if the number of revolutions of the expansion mechanism 5 is reduced within the using range, if the discharge temperature (Td) does not reach the target discharge temperature (target Td), the pre-expansion valve 11 is operated in the closing direction based on the discharge temperature, the refrigerant is decompressed. With this, it is possible to adjust the pressure to the desired high pressure-side pressure without exceeding the using range of the expansion mechanism 5, and to operate the refrigeration cycle apparatus without deteriorating the operation efficiency and ability.
  • FIG. 10 is a schematic diagram showing a structure of the refrigeration cycle apparatus.
  • the same constituent elements as those shown in Fig. 4 are designated with the same symbols, and explanation thereof will be omitted.
  • the action of the refrigeration cycle apparatus when it is operated will be explained based on a case where the product Xof the density ratio and the ratio of the number of revolutions in the actual operating state (DE / DC) x (Hze / Hzc) is substantially the same as the design capacity ratio (VC / VE) which was assumed at the time of designing.
  • CO 2 refrigerant is compressed by the compressing mechanism 2 to a pressure (high pressure-side pressure) exceeding critical pressure.
  • the compressed refrigerant is brought into a high temperature and high pressure state, and when the refrigerant flows through the refrigerant flow path of the radiator 3, the refrigerant radiates heat to water flowing through the fluid flow path of the radiator 3 and is cooled. Thereafter, a portion of the refrigerant flows through the second bypass flow path 31 by a half-opened second bypass valve 32, and other refrigerant flows into the high pressure-side flow path 14a of the internal heat exchanger 14, and the refrigerant is further cooled by a low pressure and low temperature refrigerant flowing through the low pressure-side flow path 14b.
  • the refrigerant flows into the expansion mechanism 5, and is decompressed by the expansion mechanism 5 and brought into the low temperature and low pressure gas/liquid two-phase state. At that time, in the expansion mechanism 5, the pressure energy of the refrigerant is converted into power and the power is converted into electricity by the generator 4.
  • the pressure energy at the time of expansion can be collected as electricity and the COP can be enhanced.
  • Refrigerant decompressed by the expansion mechanism 5 is supplied to the evaporator 6.
  • the refrigerant is heated by the outside air sent by the air blowing apparatus 9, and the refrigerant is brought into a gas/liquid two-phase state or a gaseous state.
  • the refrigerant which flows out from the evaporator 6 is heated by the low pressure-side flow path 14b of the internal heat exchanger 14 and then, the refrigerant is again sucked into the compressing mechanism 2.
  • the product Xof the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc) in the actual operating state is different from the design capacity ratio (VC / VE) which was assumed during designing will be explained.
  • the operation when the product (DE / DC) Xof the density ratio and the ratio of the number of revolutions (DE / DC) X (Hze / Hzc) in the actual operating state is greater than the design capacity ratio (VC / VE) which was assumed at the time of designing will be explained.
  • the refrigeration cycle tries to balance in a state where the high pressure-side pressure is reduced such that the refrigerant density (DE) of the inlet of the expansion mechanism 5 becomes small.
  • the high pressure-side pressure is reduced lower than the preferable pressure, the discharge temperature may be lowered, the heating ability of the refrigeration cycle apparatus may be deteriorated and the efficiency of the refrigeration cycle apparatus may be deteriorated.
  • the second bypass valve 32 is operated in the opening direction so that the circulation amount of refrigerant flowing into the second bypass flow path 31 is increased, and the circulation amount of refrigerant flowing into the high pressure-side flow path 14a of the internal heat exchanger 14 is reduced.
  • the heat exchanging amount in the internal heat exchanger 14 is reduced, the density (DE) of refrigerant flowing into the expansion mechanism 5 can be reduced, the high pressure-side pressure is not lowered, and the optimal state can be maintained.
  • the internal heat exchanging amount in the internal heat exchanger 14 is reduced by operating the second bypass valve 32 in the opening direction, and only when the pressure can not be adjusted to the optimal high pressure-side pressure even if the second bypass valve 32 is fully opened, the number of revolutions of the expansion mechanism 5 is operated in the lowering direction. With this, the possibility of reduction in the number of revolutions of the expansion mechanism 5 that may deteriorate the reliability of the expansion mechanism 5 can be lowered. Thus, the refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism 5.
  • the second bypass valve 32 is operated in the closing direction, thereby reducing the circulation amount of refrigerant flowing into the second bypass flow path 31, and the circulation amount of refrigerant flowing into the high pressure-side flow path 14a of the internal heat exchanger 14 is increased.
  • the heat exchanging amount in the internal heat exchanger 14 is increased, the density (DE) of refrigerant flowing into the expansion mechanism 5 can be increased, the high pressure-side pressure is not increased and the optimal state can be maintained.
  • the internal heat exchanging amount in the internal heat exchanger 14 is increased by operating the second bypass valve 32 in the closing direction, and only when the pressure can not be adjusted to the optimal high pressure-side pressure even if the second bypass valve 32 is fully closed, the number of revolutions of the expansion mechanism 5 is operated in the increasing direction. With this, the possibility of increase in the number of revolutions of the expansion mechanism 5 that may deteriorate the reliability of the expansion mechanism 5 can be lowered. Thus, the refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism 5.
  • a detection value (discharge temperature: Td) (700) from the discharge temperature detecting means 20 is taken in.
  • a target discharge temperature (target Td) which is previously stored in a ROM or the like and the taken discharge temperature (Td) are compared with each other (710) . If the discharge temperature (Td) is lower than the target discharge temperature (target Td), there is a tendency that the high pressure-side pressure is lower than the optimal pressure and thus, it is determined whether the second bypass valve 32 is fully opened (720).
  • the second bypass valve 32 When the second bypass valve 32 is fully opened, the number of revolutions (Hze) of the expansion mechanism 5 is operated in the lowering direction (730) to reduce the circulation amount of refrigerant flowing through the expansion mechanism 5, and the high pressure-side pressure and the discharge temperature are increased.
  • the second bypass valve 32 When the second bypass valve 32 is not fully opened, the second bypass valve 32 is operated in the opening direction (740), and the circulation amount of refrigerant flowing into the high pressure-side flow path 14a of the internal heat exchanger 14 is reduced. By reducing the heat exchanging amount in the internal heat exchanger 14, the density of refrigerant flowing into the expansion mechanism 5 is reduced, and the high pressure-side pressure and the discharge temperature are increased.
  • the second bypass valve 32 is fully closed (750).
  • the number of revolutions (Hze) of the expansion mechanism 5 is operated in the increasing direction (760) to increase the circulation amount of refrigerant flowing through the expansion mechanism 5, and the high pressure-side pressure and the discharge temperature are lowered.
  • the second bypass valve 32 When the second bypass valve 32 is not fully opened in step 750, the second bypass valve 32 is operated in the closing direction (770) to increase the circulation amount of refrigerant flowing into the high pressure-side flow path 14a of the internal heat exchanger 14.
  • the density of refrigerant flowing into the expansion mechanism 5 is increased by increasing the heat exchanging amount in the internal heat exchanger 14, and the high pressure-side pressure and the discharge temperature are lowered.
  • the procedure is returned to step 700, and steps 700 to 770 are repeated, and the number of revolutions of the expansion mechanism 5 and the opening of the second bypass valve 32 are controlled in liaison with each other as shown in Fig. 12.
  • the second bypass valve 32 is operated in the opening direction to increase the heat exchanging amount in the internal heat exchanger 14.
  • the discharge temperature (Td) does not reach the target discharge temperature (target Td) even when the second bypass valve 32 is fully opened
  • the number of revolutions of the expansion mechanism 5 is operated in the lowering direction based on the discharge temperature.
  • the possibility of reduction in the number of revolutions of the expansion mechanism 5 that may deteriorate the reliability of the expansion mechanism 5 can be lowered.
  • the refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism 5.
  • the second bypass valve 32 is operated in the closing direction to reduce the heat exchanging amount in the internal heat exchanger 14.
  • the number of revolutions of the expansion mechanism 5 is operated in the increasing direction based on the discharge temperature. With this, the possibility of increase in the number of revolutions of the expansion mechanism 5 that may deteriorate the reliability of the expansion mechanism 5 can be lowered.
  • the refrigeration cycle apparatus can be operated efficiently without lowering the reliability of the expansion mechanism 5.
  • the first bypass valve 13 and the second bypass valve 32 in the determination of the fully opened states or fully closed states of the pre-expansion valve 11, the first bypass valve 13 and the second bypass valve 32, they need not physically fully opened or fully closed, and preset maximum opened state or minimum opened state close to the fully opened or closed state may be employed while taking the reliability of the valves into account .
  • the number of revolutions of the expansion mechanism 5 may be determined based on the actual number of revolutions, or based on a set value of the expansion mechanism revolution number control means 21.
  • a very small value may be added to or subtracted from the target discharge temperature (target Td) so that the discharge temperature falls within a constant temperature range.
  • the number of revolutions of the expansion mechanism 5, the pre-expansion valve 11, the first bypass valve 13 and the opening of the second bypass valve 32 are controlled.
  • the high pressure-side pressure may be directed directly, and the control may be performed using this value, or the control may be performed using a detection value obtained by detecting the temperature of the refrigeration cycle apparatus which has a correlation with the high pressure-side pressure or using a calculation value using the detection value.
  • the control may be performed using a degree of sucked superheat of the compressing mechanism 2 or a degree of superheat of an outlet of the evaporator 3.
  • the refrigerant flowing from a refrigerant outlet of the radiator 3 flowing through the high pressure-side flow path 14a of the internal heat exchanger 14 to the inlet of the expansion mechanism 5 is cooled by a refrigerant flowing from the refrigerant outlet of the evaporator 6 flowing through the low pressure-side flow path 14b to the inlet of the compressing mechanism 2.
  • a refrigerant flowing from the refrigerant outlet of the radiator 3 flowing through the high pressure-side flow path 14a to the inlet of the expansion mechanism 5 may partially branch off from another low pressure refrigerant flowing through the low pressure-side flow path 14b, e.g., from a refrigerant of an inlet of the expansion mechanism 5, and may be cooled by a decompressed low temperature and low pressure refrigerant.
  • the second bypass flow path 31 bypasses the high pressure-side flow path 14a of the internal heat exchanger 14. but even when the second bypass flow path 31 bypasses the low pressure-side flow path 14b, the same effect can be obtained.
  • CO 2 carbon dioxide
  • R410A refrigerant
  • the circulation amount of refrigerant flowing into the expansion mechanism can be adjusted in a wider range without deteriorating the reliability of the expansion mechanism, and the refrigeration cycle apparatus can be operated efficiently and thus, the refrigeration cycle apparatus can be applied to a water heater and an air conditioner having the expansion mechanism.

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)
EP07004366A 2006-03-03 2007-03-02 Kältekreislaufvorrichtung Withdrawn EP1830143A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006057417A JP4765675B2 (ja) 2006-03-03 2006-03-03 冷凍サイクル装置

Publications (2)

Publication Number Publication Date
EP1830143A2 true EP1830143A2 (de) 2007-09-05
EP1830143A3 EP1830143A3 (de) 2010-04-14

Family

ID=38066678

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07004366A Withdrawn EP1830143A3 (de) 2006-03-03 2007-03-02 Kältekreislaufvorrichtung

Country Status (2)

Country Link
EP (1) EP1830143A3 (de)
JP (1) JP4765675B2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202200003557A1 (it) * 2022-02-25 2023-08-25 Onda S P A Impianto di scambio termico.

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4827859B2 (ja) * 2008-01-08 2011-11-30 三菱電機株式会社 空気調和装置およびその運転方法
JP5593623B2 (ja) * 2009-03-13 2014-09-24 ダイキン工業株式会社 冷凍装置
JP5825041B2 (ja) * 2011-10-25 2015-12-02 ダイキン工業株式会社 冷凍装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4140778A1 (de) * 1991-12-06 1992-12-24 Nitschke R Peter Vorrichtung und verfahren zur umwandlung von erdoberflaechenwaerme in elektrische- und waermeenergie
US6272871B1 (en) * 2000-03-30 2001-08-14 Nissan Technical Center North America Air conditioner with energy recovery device
JP2003194432A (ja) * 2001-10-19 2003-07-09 Matsushita Electric Ind Co Ltd 冷凍サイクル装置

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4096544B2 (ja) * 2001-10-30 2008-06-04 ダイキン工業株式会社 冷凍装置
JP4233843B2 (ja) * 2002-10-31 2009-03-04 パナソニック株式会社 冷凍サイクル装置
JP3998249B2 (ja) * 2003-04-28 2007-10-24 株式会社日立製作所 冷凍サイクル

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4140778A1 (de) * 1991-12-06 1992-12-24 Nitschke R Peter Vorrichtung und verfahren zur umwandlung von erdoberflaechenwaerme in elektrische- und waermeenergie
US6272871B1 (en) * 2000-03-30 2001-08-14 Nissan Technical Center North America Air conditioner with energy recovery device
JP2003194432A (ja) * 2001-10-19 2003-07-09 Matsushita Electric Ind Co Ltd 冷凍サイクル装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202200003557A1 (it) * 2022-02-25 2023-08-25 Onda S P A Impianto di scambio termico.
WO2023161157A1 (en) * 2022-02-25 2023-08-31 Onda S.P.A. Heat exchange apparatus

Also Published As

Publication number Publication date
EP1830143A3 (de) 2010-04-14
JP2007232322A (ja) 2007-09-13
JP4765675B2 (ja) 2011-09-07

Similar Documents

Publication Publication Date Title
CN100513930C (zh) 冷冻循环装置及其控制方法
EP2565555B1 (de) Kältekreislaufvorrichtung
EP1416231B1 (de) Kühlgerät
US6505476B1 (en) Refrigerant cycle system with super-critical refrigerant pressure
US7350366B2 (en) Heat pump
JP4053082B2 (ja) 冷凍サイクル装置
EP1416232B1 (de) Kälteanlage
JP4375171B2 (ja) 冷凍装置
US20100287964A1 (en) Refrigerating apparatus
US6945066B2 (en) Refrigeration cycle apparatus
EP2302310A1 (de) Kühlzyklusvorrichtung
WO2011117924A1 (ja) 冷凍サイクル装置及びその運転方法
JP4273493B2 (ja) 冷凍空調装置
US8769983B2 (en) Refrigeration cycle apparatus
WO2009098899A1 (ja) 冷凍装置
EP1830143A2 (de) Kältekreislaufvorrichtung
JP2007212024A (ja) 冷凍サイクル装置および冷凍サイクル装置の制御方法
JP3870951B2 (ja) 冷凍サイクル装置およびその制御方法
CN112368523B (zh) 冷冻循环装置以及其控制方法
JP4760166B2 (ja) 冷凍サイクル装置の制御方法およびそれを用いた冷凍サイクル装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: PANASONIC CORPORATION

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

17P Request for examination filed

Effective date: 20100610

17Q First examination report despatched

Effective date: 20100803

AKX Designation fees paid

Designated state(s): DE DK FR GB SE

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20130228