WO2008072575A1 - Appareil de congélation et détendeur - Google Patents

Appareil de congélation et détendeur Download PDF

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Publication number
WO2008072575A1
WO2008072575A1 PCT/JP2007/073703 JP2007073703W WO2008072575A1 WO 2008072575 A1 WO2008072575 A1 WO 2008072575A1 JP 2007073703 W JP2007073703 W JP 2007073703W WO 2008072575 A1 WO2008072575 A1 WO 2008072575A1
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WO
WIPO (PCT)
Prior art keywords
valve
suction
expansion mechanism
flow rate
refrigerant
Prior art date
Application number
PCT/JP2007/073703
Other languages
English (en)
Japanese (ja)
Inventor
Katsumi Sakitani
Masakazu Okamoto
Eiji Kumakura
Tetsuya Okamoto
Original Assignee
Daikin Industries, 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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to EP07850281.2A priority Critical patent/EP2090746B1/fr
Priority to CN2007800448285A priority patent/CN101548066B/zh
Priority to ES07850281T priority patent/ES2721233T3/es
Publication of WO2008072575A1 publication Critical patent/WO2008072575A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/32—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members
    • F01C1/322—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C13/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01C13/04—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby for driving pumps or compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/02—Control of, monitoring of, or safety arrangements for, machines or engines specially adapted for several machines or engines connected in series or in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/24—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves
    • F01C20/26—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/324—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the inner member and reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/06—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • 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
    • 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 apparatus provided with an expansion mechanism, and more particularly to a positive displacement expansion mechanism that generates power by expansion of a fluid.
  • a refrigerant circuit that performs a refrigeration cycle is provided with an expansion mechanism for recovering refrigerant power in addition to a compression mechanism.
  • the power recovered from the high-pressure refrigerant force by this expansion mechanism is transmitted to the compression mechanism connected via the drive shaft, and is used to drive the compression mechanism.
  • the circulation amount of the refrigerant passing through the compression mechanism per unit time (corresponding to mass flow rate, the same applies hereinafter) and the circulation amount of the refrigerant passing through the expansion mechanism are always constant.
  • a force expansion mechanism is designed at a certain design specification point (for example, a heating rating)
  • the amount of circulation between the compression mechanism and the amount of circulation in the expansion mechanism Excess or deficiency will occur.
  • the optimum suction volume of the expansion mechanism is at the heating rating when the suction pressure of the compression mechanism is high. Since it is larger than that at the time of rating, the refrigerant will run out and cause overexpansion.
  • a refrigerant circuit is provided by inducing high-pressure refrigerant in the expansion process of the expansion mechanism, or providing a passage that bypasses the expansion mechanism and adjusting the bypass amount by a control valve.
  • the refrigerant flow rate on the compression mechanism side and the expansion mechanism side is balanced.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2004-150748
  • Patent Document 2 JP 2001-116371 A
  • the present invention has been made in view of the force and the point, and an object of the present invention is to provide a refrigerant of the expansion mechanism while recovering the energy of the high-pressure refrigerant to the maximum by the expansion mechanism.
  • An object of the present invention is to obtain a refrigeration apparatus having a variable inhalation amount.
  • the main suction hole (55, 103, 201) first communicating with the fluid chamber (72, 82, 230) in the suction process, and the auxiliary suction hole (56, 104) communicating after the main suction hole (55, 103, 201) communicates. , 113, 114, 203, 204
  • the first invention has a first member (71, 81, 102, 112, 210) and a second member (75, 85, 116, 124, 220) that move relatively eccentrically.
  • the refrigeration apparatus includes an expansion mechanism (50, 100, 200) that generates power by expansion of fluid in a fluid chamber (72, 82, 230) formed between the two members.
  • the expansion mechanism (50, 100, 200) has a main suction hole (55, 103, 201) that first communicates with the fluid chamber (72, 82, 230) and the suction path (24) in the suction process.
  • the expansion mechanism (50, 100, 200) includes the fluid chamber (72, 82, 230) so that at least the suction process and the discharge process are performed independently in the fluid chamber (72, 82, 230). Is divided (second invention).
  • the high-pressure fluid introduced into the fluid chamber in the suction process is expanded (50, 100, 200) It can be prevented from flowing out to the outside without being expanded inside. Therefore, with the configuration as described above, the fluid can be sufficiently expanded in the expansion mechanism (50, 100, 200).
  • the auxiliary suction hole (56, 104, 113, 114, 203, 204, 205) is preferably provided so as to open from the lower side to the fluid chamber (72, 230)! 3 inventions).
  • the auxiliary suction holes (56, 104, 113, 114, 203, 204, 205) so as to open from below the fluid chamber (72, 230)
  • the auxiliary suction holes (56, 104, 113) are provided.
  • the suction passage (27) connected to the suction hole (56, 104, 113, 114, 203, 204, 205) is provided in the expansion mechanism (50, 100). Refrigerating machine oil will accumulate. Then, it is possible to prevent the suction path (27) force S and the dead volume in which the fluid in the fluid chamber (72, 230) is accumulated, and to efficiently expand the fluid in the fluid chamber (72, 230). it can.
  • an on-off valve (61) is provided on the suction passage (27) connected to the auxiliary suction hole (56, 104, 113, 114, 203, 204, 205).
  • a check valve (95) that allows only the force to the on-off valve (61) and the flow to the suction holes (56, 104, 113, 114, 203, 204, 205). /! It is preferable to be! / (4th invention).
  • the check valve (95) By providing the check valve (95) in this way, it is possible to more reliably prevent the fluid in the fluid chamber (72, 82, 230) from flowing into the suction passage (27).
  • the ineffective volume in (50, 100) can be more reliably reduced, and the force S is used to expand the fluid more efficiently by the expansion mechanism (50, 100).
  • a bypass circuit (65) for bypassing the expansion mechanism (50, 100, 200) is provided, and the bypass circuit (65) is provided with a bypass flow rate adjusting valve (66). (5th invention).
  • the bypass circuit (65) and the bypass flow rate adjustment valve (66) it is possible to finely adjust the fluid circulation amount of the expansion mechanism (50, 100, 200), as well as immediately after starting.
  • the amount of fluid circulation is significantly increased compared to normal operation, such as during defrost operation. Even in such a case, the force S can be used to suppress the increase in pressure on the suction side of the expansion mechanism (50, 100) by absorbing the increase.
  • bypass flow rate adjustment valve is based on the pressure of the fluid introduced into the expansion mechanism (50, 100, 200).
  • the bypass flow rate control means (94) for controlling (66) is provided! / (6th invention). Accordingly, the bypass amount of the expansion mechanism (50, 100, 200) can be adjusted so that the pressure introduced into the expansion mechanism (50, 100) becomes a target value.
  • a flow rate adjusting valve (60) is provided on the suction passage (24) connected to the main suction hole (55, 103, 201) (seventh invention).
  • the fluid circulation amount introduced into the fluid chamber (72, 82, 230) from the main suction hole (55, 103, 201) can be adjusted by the flow rate adjustment valve (60), so that the compression mechanism (40) An optimal amount of fluid can flow through the expansion mechanism (50, 100) according to the fluid circulation rate.
  • the flow rate adjusting valve (60) is provided downstream of the branch position with the suction passage (27) connected to the auxiliary suction hole (56, 104, 113, 114, 203, 204, 205). I like it! / (8th invention). By doing this, it is possible to adjust only the circulation amount of the fluid introduced from the main suction hole (55, 103, 201) without changing the circulation amount of the fluid introduced from the auxiliary suction hole.
  • a flow rate control means (92) for controlling the flow rate regulating valve (60) based on the pressure of the fluid introduced into the expansion mechanism (50, 100, 200) is provided.
  • the fluid circulation amount of the expansion mechanism (50, 100, 200) can be adjusted so that the pressure introduced into the expansion mechanism (50, 100) becomes a target value.
  • the on-off valve control means (93) for controlling the on-off valve (61) provided above is provided (tenth invention).
  • the open / close valve (61) By controlling the open / close valve (61) by the open / close valve control means (93), the flow rate introduced into the fluid chamber (72, 82, 230) can be controlled.
  • auxiliary suction holes 56, 104, 113, 114, 203, 204, 205
  • each of the auxiliary suction holes (56, 104, 113, 114, 203) is provided.
  • 204, 205) is provided with an on-off valve (61) on the suction passage (27) connected to the suction passage (27), and the on-off valve control means (93) is configured so that the auxiliary suction hole ( 56, 104, 113, 114, 203, 204, 205), the opening / closing valve (61) is sequentially controlled to open so that the fluid chamber (72, 82, 230) and the suction passage (27) communicate with each other in order. (Eleventh invention)
  • the on-off valve control means (93) is configured such that the auxiliary suction hole (56, 104, 113, 114) that communicates last with the fluid chamber (72, 82, 230) when the pressure is smaller than a target value. , 203, 204, 205), the on-off valve (61) is closed in this order (the twelfth invention).
  • the amount of circulation introduced into the fluid chamber (72, 82, 230) can be reduced stepwise by closing the on-off valve (61) in order. Accordingly, even if the amount of circulation required in the fluid chamber (72, 82, 230) changes greatly, the amount of inflow into the liquid chamber (72, 82, 230) can be quickly achieved by controlling the opening / closing valve (61). Can be reduced.
  • the bypass flow control means (94) for controlling the bypass flow adjustment valve (66) provided in the bypass circuit (65) bypassing the expansion mechanism (50, 100) is provided.
  • the bypass flow rate control means (94) controls the bypass flow rate adjustment valve (66) so that the pressure becomes a target value
  • the on-off valve control means (93) controls the bypass flow rate adjustment valve.
  • the circulation amount of the fluid introduced into the fluid chamber (72, 82, 230) of the expansion mechanism (50, 100, 200) is finely adjusted by the bypass flow rate adjustment valve (66) on the bypass circuit (65).
  • the bypass flow rate adjusting valve (66) cannot be adjusted, the circulation amount of the fluid chamber (72, 82, 230) is increased or decreased quickly and reliably by the opening / closing control of the opening / closing valve (61). That power S.
  • the flow rate can be adjusted quickly and reliably so as to achieve an optimum circulation amount for the expansion mechanism (50, 100, 200).
  • the configuration includes a flow rate control means (92) for controlling a flow rate adjustment valve (60) provided on the suction path (24) connected to the main suction hole (55, 103, 201).
  • the flow rate control means (92) adjusts the flow rate when the pressure is smaller than the target value even when the bypass flow rate adjustment valve (66) and the on-off valve (61) are all closed.
  • the flow rate of the expansion mechanism (50, 100, 200) is adjusted by the valve (60) (14th invention).
  • the auxiliary suction hole (56, 104) is closed by closing the bypass flow rate adjustment valve (66) and the on-off valve (61). , 11 3, 114, 203, 204, 205), reducing the circulation rate of the fluid introduced from the main suction hole (55, 103, 201) only into the fluid chamber (72, 82, 230), but the fluid circulation rate is still If there is too much, the flow rate is adjusted by the flow rate adjustment valve (60). As a result, the amount introduced into the fluid chamber (72, 82, 230) can be reliably and rapidly reduced.
  • the expansion mechanism (50, 100) has a plurality of rotary mechanism parts (70, 80, 101, 111, 121) connected in series in order from the smallest displacement volume, and the main suction mechanism
  • the holes (55, 103) and the auxiliary suction holes (56, 104, 113, 114) are located on the front rotary mechanism (70, 101, 111) on the front stage side of the rotary mechanism (80, 121) on the last stage. It is preferably provided (15th invention). In this way, by using a multi-stage rotary expansion mechanism (50, 100), high-pressure fluid can be prevented from blowing from the suction side to the discharge side, and the expansion mechanism (50, 100) efficiently expands the fluid. It can be made.
  • the expansion mechanism (50) has two rotary mechanism parts (70, 80) connected in series, and the main suction hole is connected to the front rotary mechanism part (70) having a small displacement volume. (55) and supplement An auxiliary suction hole (56) is provided! /, Preferably ! (16th invention).
  • the auxiliary suction holes (56, 104, 113, 114) It is assumed that it is provided at an angular position obtained by adding a predetermined correction value to the angular position obtained geometrically based on the desired displacement (17th invention).
  • the desired displacement volume is preferably a displacement volume required during cooling operation (18th invention).
  • the pressure on the low pressure side is higher than that during heating operation, and even in the cooling operation where more refrigerant flow is required by the expansion mechanism (50, 100), the inside of the fluid chamber (72, 230)
  • the necessary refrigerant flow rate can flow in the fluid chamber (72, 230). Therefore, during the cooling operation, the expansion mechanism (50, 100) is prevented by the force S to prevent the refrigerant from running out and causing overexpansion.
  • the expansion mechanism (200) includes a pair of scroll members (210, 220) in which spiral wraps are formed on the end plate, and the wraps (211, 221) of the scroll members (210, 220) are mutually connected. It has a scroll mechanism that forms at least a pair of fluid chambers (231, 232) by being combined, and the main suction hole (201) is located at a position communicating with the fluid chamber (231, 232) in the suction process of the scroll mechanism. And auxiliary suction holes (203, 204, 205) are provided! / (19th invention).
  • a supercritical cooling is performed using a refrigerant composed of C02 as the fluid. It is preferably configured to perform a freezing cycle (20th invention). Thereby, a refrigerant circuit suitable for the environment can be configured.
  • the twenty-first invention has a first member (71, 81, 102, 112, 210) and a second member (75, 85, 116, 124, 220) that move relatively eccentrically, and the two members.
  • the target is an expander equipped with an expansion mechanism (50, 100, 200) that generates power by expansion of the fluid in the fluid chamber (72, 82, 230) formed between them.
  • the expansion mechanism (50, 100, 200) includes a main suction hole (55, 103, 201) that first communicates with the fluid chamber (72, 82, 230) and the suction path (24) in the suction process. And an auxiliary suction hole (56, 104, 113, 114, 203, 204, 205) ⁇ , which communicates the fluid chamber (72, 82, 230) and the suction passage (27) after the main suction hole (55, 103, 201) communicates. It shall be. As a result, an expander capable of obtaining the same operation as that of the first invention can be configured.
  • the main suction hole (55, 103, 201) that first communicates with the expansion chamber (50, 100, 200) and the fluid chamber (72, 82, 230) in the suction step, and then the communication. Since the auxiliary suction holes (56, 104, 113, 114, 203, 204, 205) are provided, the flow rate of fluid to the fluid chamber (72, 82, 230) can be controlled, and the operating conditions change greatly. Even so, the fluid circulation rate of the expansion mechanism (50, 100, 200) can be optimized. Therefore, the fluid can be efficiently expanded by the expansion mechanism (50, 100, 200), and power can be recovered efficiently.
  • the expansion mechanism (50, 100, 200) since the expansion mechanism (50, 100, 200) is independent of at least the suction process and the discharge process, the expansion mechanism (50, 100, 200) does not blow through even when a high-pressure fluid is introduced.
  • the expansion mechanism (50, 100, 200) can reliably expand the fluid.
  • the auxiliary suction hole (56, 104, 113, 114, 203, 204, 205) is formed so as to open from the lower side to the fluid chamber (72, 82, 230). If fluid is introduced from the suction hole (56, 104, 113, 114, 203, 204, 205)! /, V, in the case of the auxiliary suction hole (56, 104, 113, 114, 203, 204, 205) It is possible to reliably prevent the refrigerating machine oil from accumulating and the suction hole (56, 104, 113, 114, 203, 204, 205) from becoming a dead volume of the fluid in the fluid chamber (72, 82, 230).
  • the fluid can be efficiently expanded by the expansion mechanism (50, 100, 200).
  • the auxiliary suction hole (56, 104, 113, 114, 203, 204, 205) If the check valve (95) is provided on the downstream side of the on-off valve (61) provided on the suction passage (27) connected to the suction passage (27), the suction hole (56, 104, 113, 114, 203, 204, 205) is formed in the fluid chamber.
  • the dead volume of the fluid in (72, 82, 230) can be prevented more reliably, and the fluid can be expanded more efficiently by the expansion mechanism (50, 100, 200).
  • the bypass flow rate adjusting valve (66) is provided in the bypass circuit (65) that bypasses the expansion mechanism (50, 100, 200), the expansion mechanism (50, 100, 200) This makes it possible to finely adjust the circulation rate of the fluid and to adjust the flow rate when the fluid flow rate is extremely high compared to normal operation.
  • the expansion mechanism (50, 100, 200) by controlling the bypass flow rate adjustment valve (66) based on the pressure of the fluid introduced into the expansion mechanism (50, 100, 200), the expansion mechanism (50, The circulation amount can be adjusted so that the pressure of 100,200) becomes the target value.
  • the flow rate adjustment valve (60) is provided on the suction passage (24) connected to the main suction hole (55, 103, 201), the expansion mechanism (50, 100, 200)
  • the flow rate of the fluid introduced into the fluid chamber (72, 82, 230) can be adjusted to an optimum flow rate, and power recovery can be efficiently performed by the expansion mechanism (50, 100, 200).
  • the flow rate adjusting valve (60) is arranged downstream of a branch position with the suction passage (27) connected to the auxiliary suction holes (56, 104, 113, 114, 203, 204, 205). Since the main suction hole (55, 103, 201) force is also provided on the side, the flow rate of the introduced fluid can be adjusted independently, so that the fluid circulation rate of the expansion mechanism (50, 100, 200) can be controlled more finely. become.
  • the flow regulating valve (60) is set based on the pressure of the fluid introduced into the expansion mechanism (50, 100, 200). By controlling, the flow rate of the fluid introduced from the main suction hole (55, 103, 201) can be directly adjusted so that the pressure of the expansion mechanism (50, 100, 200) becomes a target value.
  • the on-off valve control means (93) controls the on-off valve (61) based on the pressure of the fluid introduced into the expansion mechanism (50, 100, 200). ), The amount of circulation can be increased or decreased so that the fluid circulation amount of the expansion mechanism (50, 100, 200) becomes an optimal flow rate by the opening / closing control of the on-off valve (61).
  • the mechanism (50, 100, 200) can efficiently recover power.
  • the on-off valve control means (93) is configured so that the pressure is less than a target value. Is larger than the above-mentioned on-off valve (56, 104, 113, 114, 203, 204, 205) so that the fluid chamber (72, 82, 230) and the suction passage (27) communicate with each other in order. Since 61) is configured to sequentially open, the flow rate of the fluid can be quickly and reliably increased to the flow rate required by the expansion mechanism (50, 100, 200).
  • the on-off valve control means (93) is configured such that, when the pressure is smaller than a target value, the auxiliary suction hole (finally communicating with the fluid chamber (72, 82, 230)) ( 56, 104, 113, 114, 203, 204, 205), the on-off valve (61) is closed and controlled in order !, so that the flow rate of the fluid is reduced to the flow rate required by the expansion mechanism (50, 100, 200). Decrease quickly and reliably.
  • the bypass flow rate adjustment valve (66) is controlled so that the pressure becomes a target value, and the bypass flow rate adjustment valve (66) is set to a predetermined opening degree.
  • the on-off valve (61) is controlled to open and close, so that the circulation rate of the fluid in the expansion mechanism (50, 100, 200) can be adjusted quickly and smoothly, and power can be recovered efficiently. it can.
  • the on-off valve (61) and the bypass flow rate adjustment valve (66) are closed when the fluid circulation rate of the expansion mechanism (50, 100, 200) is reduced.
  • the flow rate adjustment valve (60) is used to adjust the flow rate further, so that the flow rate of the fluid of the expansion mechanism (50, 100, 200) can be quickly and smoothly widened. The power can be recovered more efficiently.
  • the expansion mechanism (50, 100) is a multi-stage rotary type, so that the introduced high-pressure fluid can be prevented from being blown through, and the expansion mechanism (50, 100) can be prevented. 100) can efficiently expand the fluid.
  • the structure can be simplified and the manufacturing cost can be reduced while reliably preventing high-pressure fluid from being blown through.
  • the auxiliary suction hole (56, 104, 113, 114) is a correction value for an angular position geometrically determined based on a desired displacement volume.
  • the auxiliary suction hole (56, 104, 113, 114) force in the fluid chamber (72, 230) is taken into account to reduce the refrigerant inflow due to the pressure loss when the refrigerant is introduced.
  • the fluid It is possible to reliably flow the necessary refrigerant flow into the chamber (72,230), and to prevent overexpansion in the expansion mechanism (50,100).
  • the desired displacement volume is a displacement volume required during the cooling operation, it is possible to reliably prevent overexpansion in the expansion mechanism (50, 100) during the cooling operation. be able to.
  • the expansion mechanism (200) is of a scroll type, it is possible to reliably prevent high-pressure fluid from being blown through without being multi-staged, and an efficient expansion mechanism. (200) is obtained.
  • the fluid is a C02 refrigerant and the refrigeration apparatus is configured to perform a supercritical refrigeration cycle, a refrigeration apparatus suitable for the environment can be obtained.
  • the main suction hole (55, 103, 201) and the auxiliary suction hole (56, 104, 1 13, 114, 203, 204, 205) are provided in the expander, whereby the first invention An expander having the same effect as the above can be obtained.
  • FIG. 1 is a schematic configuration diagram of a refrigerant circuit of an air-conditioning apparatus according to Embodiment 1.
  • FIG. 2 is a longitudinal sectional view of a compression / expansion unit.
  • FIG. 3 is an enlarged sectional view showing a longitudinal section of the expansion mechanism.
  • FIG. 4 is an enlarged cross-sectional view showing a cross-section of the main part in the expansion mechanism.
  • FIG. 5 is a cross-sectional view of the main part showing the state of each rotary mechanism part for every 90 ° rotation angle of the crankshaft in the expansion mechanism of the first embodiment.
  • FIG. 6 is a graph showing the relationship between the refrigerant suction capacity and pressure of the expansion mechanism.
  • FIG. 7 is a view corresponding to FIG. 6 for comparing the case of injection with the present invention.
  • FIG. 8 is a diagram showing a schematic configuration of a control device that controls each valve.
  • FIG. 9 is a flowchart showing a control flow of each valve.
  • FIG. 10 is a diagram showing an example of control of each valve.
  • FIG. 11 is an actual diagram schematically showing the relationship between the total valve opening of each valve and the refrigerant circulation rate of the expansion mechanism.
  • FIG. 12 One example of the relationship between the refrigerant suction capacity and pressure when multiple suction ports are opened. It is a graph which shows an example.
  • FIG. 3 is a diagram corresponding to FIG. 3 according to Modification 1 of Embodiment 1.
  • FIG. 4 is a diagram corresponding to FIG. 4 according to Modification 2 of Embodiment 1.
  • FIG. 16 A graph showing an example of the relationship between the angular position of the second suction port and the refrigerant flow rate.
  • FIG. 17 is a diagram showing the calculation result of the angular position of the second suction port when the performance of the heat exchanger is changed.
  • Air conditioner (refrigeration equipment)
  • FIG. 1 shows a refrigerant circuit (10) of an air conditioner (1) as a refrigeration apparatus according to Embodiment 1 of the present invention.
  • the air conditioner (1) includes an outdoor unit (2) and an indoor unit (3).
  • the outdoor unit (2) includes a compression / expansion unit (20), an outdoor heat exchanger (14), a four-way selector valve (12), and a check valve (11, 11, 11, 11).
  • the circuit part (13) is accommodated.
  • the indoor heat exchanger (15) is accommodated in the indoor unit (3).
  • each of the heat exchangers (14, 15) is provided with a fan so that outside air or inside air is blown to the heat exchangers (14, 15). It is composed.
  • the outdoor unit (2) and the indoor unit (3) are connected by a pair of connecting pipes (16, 17), whereby the compressor / expansion unit (20) and the heat exchanger (
  • the refrigerant circuit (10) is configured as a closed circuit to which 14, 15) and the like are connected.
  • the refrigerant circuit (10) is charged with carbon dioxide (C02) as a refrigerant.
  • the compression / expansion unit (20) includes a casing (21) formed in a vertically long cylindrical sealed container shape.
  • the casing (21) houses a compression mechanism (40), an expansion mechanism (50), and an electric motor (26). That is, in the casing (21), the compression mechanism (40), the electric motor (26), and the expansion mechanism (50) are arranged in order from the bottom to the top.
  • the details of the compression / expansion unit (20) will be described later.
  • the expansion mechanism (50) is provided with a plurality of suction ports (55, 56) as suction holes. Refrigerant The inhalation amount is variable. Note that FIG. 1 shows an example in which two suction ports of the expansion mechanism (50) are provided.
  • an accumulator (18) is provided on the suction side of the compression mechanism (40) of the compression / expansion unit (20). Further, on the suction side of the expansion mechanism (50), a front throttle valve (60) and an on-off valve (61) are provided corresponding to the plurality of suction ports (55, 56). Specifically, in the suction process of the expansion mechanism (50), the front throttle valve (60) force communicates second on the suction path connected to the first suction port (55) that first communicates with the fluid chamber (72). On-off valve (61) force is provided on the suction path connected to the second suction port (56).
  • the front throttle valve (60) is the flow regulating valve of the present invention, the first suction port (55) is the main suction hole of the present invention, and the second suction port (56) is the auxiliary suction valve of the present invention. It corresponds to each hole.
  • the refrigerant circuit (10) is provided with a bypass pipe (65) constituting a bypass circuit so as to bypass the suction side and the discharge side of the expansion mechanism (50).
  • the bypass pipe (65) is provided with a bypass valve (66) as a bypass flow rate adjusting valve of the present invention.
  • Each of the heat exchangers (14, 15) is a cross-fin type fin-and-tube heat exchanger.
  • the refrigerant circulating in the refrigerant circuit (10) exchanges heat with outdoor air
  • the indoor heat exchanger (15) the refrigerant circulating in the refrigerant circuit (10) Exchanges heat with room air.
  • the four-way selector valve (12) includes four ports.
  • the first port of the four-way selector valve (12) is at the discharge side of the compression mechanism (40)
  • the second port is at one end of the indoor heat exchanger (15)
  • the third port is at the outdoor heat exchanger (14).
  • the fourth port is connected to the suction side of the compression mechanism (40).
  • the first port and the second port communicate with each other, and the third port and the fourth port communicate with each other (shown by a solid line in FIG. 1). State), and the first port and the third port communicate with each other and the second port and the fourth port communicate with each other (the state indicated by the broken line in FIG. 1). ! / [0070]
  • the bridge circuit section (13) is a combination of four check valves (11, 11, 11, 11) in a bridge shape, and the refrigerant is controlled by the operation of the four-way switching valve (12). Even when the refrigerant flow in the circuit (10) is in the reverse direction, the refrigerant is always supplied to the expansion mechanism (50) in a fixed direction.
  • the force for providing the bridge circuit section (13) constituted by the check valves (11, 11, 11, 11) is to provide another four-way switching valve. May be.
  • the compression / expansion unit (20) includes a casing (21) which is a vertically long and cylindrical sealed container. Inside the casing (21), a compression mechanism (40), an electric motor (26), and an expansion mechanism (50) are arranged in order from the bottom to the top. Further, the casing (21) includes a suction pipe (22), a discharge pipe (23) and an introduction pipe (24, 27) forming a part of the suction path of the present invention so as to penetrate the trunk portion. A lead-out pipe (25) is provided! The suction pipe (22) is connected to the compression mechanism (40), and the introduction pipe (24, 27) and the outlet pipe (25) are connected to the expansion mechanism (50).
  • the discharge pipe (23) is provided in the space between the electric motor (26) and the expansion mechanism (50) in the casing (21) so that one end side is opened.
  • the first introduction pipe (24) is connected to the first suction port (55), and the second introduction pipe (25) is connected to the second suction port (56).
  • the front throttle valve (60) is provided outside the casing (21) of the first introduction pipe (24) and downstream of the branch position with the second introduction pipe (27).
  • the on-off valve (61) is provided outside the casing (21) of the second introduction pipe (27) and downstream of the branch position with the first introduction pipe (24).
  • the front throttle valve (60) is provided downstream of the branch position with the second introduction pipe (27), so that the expansion from the first introduction pipe (24), that is, the first suction port (55). Only the flow rate of the refrigerant introduced into the mechanism (50) can be adjusted, and the flow rate can be finely adjusted.
  • the compression mechanism (40) constitutes an oscillating piston type rotary compressor.
  • the compression mechanism (40) includes two cylinders (41, 42) and two pistons (47, 47).
  • the rear head (44), the first cylinder (41), The intermediate plate (46), the second cylinder (42), and the front head (45) are stacked.
  • the compression mechanism (40) is provided with a first crankshaft (31) for drivingly connecting to the electric motor (26).
  • the first crankshaft (31) passes through the lower force rear head (44), the first cylinder (41), the intermediate plate (46), the second cylinder (42), and the front head (45). It is arranged!
  • two compression-side eccentric portions (32, 33) are formed in the axial direction below the first crankshaft (31). These compression-side eccentric parts (32, 33) have their axes eccentric with respect to the axis of the first crankshaft (31)! The eccentric direction of the lower first compression side eccentric part (32) and the upper second compression side eccentric part (33) is shifted by 180 °.
  • the first compression side eccentric portion (32) is positioned in the first cylinder (41), and the second compression side eccentric portion (33) is positioned in the second cylinder (42).
  • Cylindrical pistons (47, 47) are fitted on the first and second compression side eccentric portions (32, 33), respectively. These pistons (47, 47) are positioned one by one inside the first and second cylinders (41, 42), so that the outer peripheral surface of the piston (47, 47) and the cylinder ( Compression chambers (43, 43) are respectively formed between the inner peripheral surfaces of 41, 42). Although not particularly shown, a flat blade is projected on the side surface of the piston (47) so as to extend outward in the radial direction, and this blade is connected to the blade via the swing bush. Supported by cylinders (41, 42).
  • first crankshaft (31) is provided with an engagement hole (34) on the upper end surface thereof.
  • the engagement hole (34) is a hexagonal cross-section hole extending downward along the axis of the first crankshaft (31), and is formed at the lower end of the second crankshaft (35) described later. It is adapted to engage with the engaging protrusion (38).
  • Each of the first and second cylinders (41, 42) is provided with one suction port (48).
  • Each suction port (48) passes through the cylinder (41, 42) in the radial direction, and is open to the inner peripheral surface of the cylinder (41, 42) so that one end side communicates with the compression chamber (43). The other end communicates with the suction pipe (22)!
  • the front head (44) and the rear head (45) each have one discharge port. It is A discharge port provided in the front head (44) allows the compression chamber (43) in the second cylinder (42) to communicate with the internal space of the casing (21). On the other hand, the discharge port provided in the rear head (45) allows the compression chamber (43) in the first cylinder (41) to communicate with the internal space of the casing (21).
  • Each discharge port is provided with a discharge valve consisting of a reed valve at its end, and is opened and closed by this discharge valve. As a result, the gas refrigerant discharged from the compression mechanism (40) into the internal space of the casing (21) also sends out the compression / expansion unit (20) force through the discharge pipe (23). In FIG. 2, the illustration of the discharge port and the discharge valve is omitted.
  • the compression mechanism (40) is fixed to the casing (21) by a ring-shaped mounting plate (49). Specifically, the outer peripheral side of the mounting plate (49) is fixed on the inner surface of the casing (21) by welding, and the front head (44) of the compression mechanism (40) is illustrated on the mounting plate (49). It is fastened with bolts! / ⁇
  • the electric motor (26) is disposed at the longitudinal center portion of the casing (21).
  • the electric motor (26) includes a stator (27) and a rotor (28).
  • the stator (27) is fixed on the inner peripheral surface of the casing (21) on the outer peripheral side.
  • the rotor (28) is disposed inside the stator (27) and is penetrated by the upper part of the first crankshaft (31).
  • the expansion mechanism (50) is a so-called oscillating piston type rotary expander, and is paired with the expansion mechanism (50). Two sets of cylinders (71, 81) as first members and pistons (75, 85) as second members are provided.
  • the expansion mechanism (50) also includes a front head (51), an intermediate plate (53), and a rear head (52).
  • each cylinder (71, 81), front head (51), intermediate plate (53), and rear head (52) constitute a fixed member
  • each piston (75, 85) is movable. It constitutes a member.
  • the front head (51), the first cylinder (71), the intermediate plate (53), the second cylinder (81), the rear head (52) are arranged in order from the bottom to the top. Are stacked.
  • the lower end surface of the first cylinder (71) is the front head (5
  • the upper end surface is closed by the intermediate plate (53).
  • the lower end of the second cylinder (81) is closed by the intermediate plate (53)
  • the upper end of the second cylinder (81) is closed by the rear head (52).
  • Each cylinder (71, 81) is formed in a generally ring-shaped thick plate shape.
  • the inner diameter of the second cylinder (81) is larger than the inner diameter of the first cylinder (71).
  • the thickness (height) of the second cylinder (81) should be thicker than the thickness (height) of the first cylinder (71)!
  • the expansion mechanism (50) passes through the front head (51), the first cylinder (71), the intermediate plate (53), the second cylinder (81), and the rear head (52).
  • a second crankshaft (35) is provided.
  • the second crankshaft (35) has an engaging projection (38) projecting from its lower end surface.
  • the engaging protrusion (38) is a hexagonal columnar protrusion extending downward from the lower end surface of the second crankshaft (35).
  • the cross-sectional shape of the engagement protrusion (38) is the engagement hole of the first crankshaft (31).
  • Two expansion side eccentric portions (36, 37) are formed on the upper portion of the second crankshaft (35) corresponding to the cylinders (71, 81). These two expansion-side eccentric parts (36, 37) have their axes eccentric with respect to the axis of the second crankshaft (35).
  • the lower first expansion side eccentric portion (36) and the upper second expansion side eccentric portion (37) have the same eccentric direction with respect to the axis of the second crankshaft (35).
  • the amount of eccentricity of the second expansion side eccentric portion (37) is larger than the amount of eccentricity of the first expansion side eccentric portion (36).
  • the first expansion side eccentric part (36) is arranged in the first cylinder (71), and the second expansion side eccentric part (37) is arranged in the second cylinder (81).
  • Cylindrical pistons (75, 85) are fitted on the first and second expansion side eccentric portions (36, 37), respectively.
  • a first piston (75) fitted around the first expansion side eccentric part (36) is fitted inside the first cylinder (71) and fitted around the second expansion side eccentric part (37).
  • Two pistons (85) are positioned in the second cylinder (81), respectively.
  • the first piston (75) has an outer peripheral surface on the inner peripheral surface of the first cylinder (71), a lower end surface on the front head (51), and an upper end surface on the middle. Each slide on the plate (53) Touching. As a result, a first fluid chamber (72) is formed in the first cylinder (71) between the inner peripheral surface thereof and the outer peripheral surface of the first piston (75).
  • the second piston (85) has an outer peripheral surface that slides on the inner peripheral surface of the second cylinder (81), a lower end surface that slides on the intermediate plate (53), and an upper end surface that slides on the rear head (52). Touching.
  • a second fluid chamber (82) is formed in the second cylinder (81) between the inner peripheral surface thereof and the outer peripheral surface of the second piston (85).
  • Each of the first and second pistons (75, 85) is integrally provided with one blade (76, 86).
  • the blades (76, 86) are formed in a plate shape extending radially outward from the outer peripheral surface of the piston (75, 85).
  • Each of the cylinders (71, 81) is provided with a pair of bushes (77, 87).
  • Each bush (77, 87) is a small piece formed such that the inner surface is a flat surface and the outer surface is a circular arc surface.
  • Each of the pair of bushes (77, 87) has a blade (76, 76) so that its inner surface slides with the blade (76, 86) and its outer surface slides with the cylinder (71, 81). , 8 6).
  • the blade (76, 86) integrally formed with the piston (75, 85) is supported by the cylinder (71, 81) via the bush (77, 87), and is supported by the cylinder (71, 81).
  • it is rotatable and can be advanced and retracted.
  • the first fluid chamber (72) in the first cylinder (71) is partitioned by the first blade (76), and the left side of the first blade (76) in FIG. 1 High pressure chamber (73), and the right side is the first low pressure chamber (74) on the low pressure side.
  • the second fluid chamber (82) in the second cylinder (81) is also partitioned by the second blade (86), and the left side of the second blade (86) in FIG. 2 High pressure chamber (83), and the right side is the second low pressure chamber (84) on the low pressure side.
  • the first cylinder (71) and the second cylinder (81) are arranged so that the positions of the bushes (77, 87) in the respective circumferential directions coincide.
  • the arrangement angle of the second cylinder (81) with respect to the first cylinder (71) is 0 °.
  • the first expansion side eccentric part (36) and the second expansion side eccentric part (37) are eccentric in the same direction with respect to the axis of the second crankshaft (35). Accordingly, at the same time as the first blade (76) is most retracted to the outside of the first cylinder (71), the second blade (86) is also most retracted to the outside of the second cylinder (81). It becomes a state.
  • the intermediate plate (53) is provided with a communication path (54) so as to penetrate the plate (53) in the thickness direction.
  • a communication path (54) On the surface of the intermediate plate (53) on the first cylinder (71) side, one end of the communication path (54) opens at a position on the right side of the first blade (76) in FIG.
  • the other end of the communication path (54) is opened at the left side of the second blade (86). That is, the communication path (54) is provided so as to communicate the first low pressure chamber (74) and the second high pressure chamber (83). In this way, the first low pressure chamber (74) and the second high pressure chamber (83) communicating with each other via the communication path (54) form one expansion chamber (59).
  • An outflow port (57) is formed in the second cylinder (81).
  • the outflow port (57) opens at a position slightly on the right side of the bush (87) in FIG. 4 on the inner peripheral surface of the second cylinder (81), and can communicate with the second low pressure chamber (84). ing. As shown in FIGS. 1 and 2, the outflow port (57) communicates with the outlet pipe (25)! /.
  • the front head (51) is provided with a first for introducing a refrigerant into the first fluid chamber (72) of the first cylinder (71).
  • a second suction port (55, 56) is formed.
  • these suction ports (55, 56) extend radially inward from the outer peripheral surface of the front head (51), and the end portions thereof are bent upward so that the front head ( 51) so as to open on the upper surface. That is, in FIG. 4, when the first fluid chamber (72) is viewed from above, the first suction port (55) extends in the radial direction and opens at a position slightly to the left of the bush (77).
  • the second suction port (56) extends in the radial direction and is provided so as to open at a position forming a predetermined angle (for example, 160 degrees) so as to be located on the substantially opposite side to the first suction port (55). It is done. Details of the angular position of the second suction port (56) will be described later.
  • first suction port (55) is connected to the first introduction pipe (24) provided with the front throttle valve (60), and the second suction port (56) is connected to the on-off valve (61). Communicating with the second introduction pipe (27) provided with the first suction port (55) provided with the front throttle valve (60), and the second suction port (56) is connected to the on-off valve (61). Communicating with the second introduction pipe (27) provided with the first suction port (55) provided with the front throttle valve (60), and the second suction port (56) is connected to the on-off valve (61). Communicating with the second introduction pipe (27) provided with
  • the amount of refrigerant introduced into the fluid chamber (72) can be reduced.
  • Easy adjustment That is, when the circulation amount of the refrigerant (mass flow rate, the same applies hereinafter) is insufficient only with the first suction port (55), the refrigerant is introduced also from the second suction port (56). (50) can secure the necessary amount of refrigerant circulation.
  • the on-off valve (61) is closed and the second suction port is closed.
  • the refrigerating machine oil in the fluid chamber (72) accumulates in the second suction port (56) and fills the space.
  • the refrigerant can be prevented from entering the suction port (56).
  • the expansion mechanism (50) can efficiently stretch the refrigerant II. I'll do it.
  • (51), the intermediate plate (53), the first piston (75), and the first blade (76) constitute a first rotary mechanism (70).
  • the second blade (86) constitutes the second rotary mechanism (80).
  • the expansion mechanism (50) is a two-stage rotary expander including a first rotary mechanism (70) and a second rotary mechanism (80). Therefore, as in a single-stage rotary expander, the suction port and the outflow port do not communicate with each other through the fluid chamber, and the high-pressure refrigerant introduced from the intake port is prevented from blowing through to the outflow port. Can do.
  • the suction port and the outflow port communicate with each other in a single stage. Therefore, it is possible to reliably prevent the high-pressure refrigerant from being blown through, and the high-pressure refrigerant is sufficiently stretched in the expansion chamber (59).
  • the expansion mechanism (50) is fixed to the casing (21) via a ring-shaped mounting plate (58) in the same manner as the compression mechanism (40). Specifically, the outer peripheral side of the mounting plate (58) is fixed to the inner surface of the casing (21) by welding, and the front head (51) of the expansion mechanism (50) is not shown on the mounting plate (58). Fixed by the default!
  • the second suction port (56) in addition to the first suction port (55), a larger amount of refrigerant can flow into the first fluid chamber (72). Can do.
  • the volume of the fluid chamber (72, 82) with which the second suction port (56) communicates varies depending on the angular position where the second suction port (56) is provided.
  • the displacement volume of can be obtained geometrically. Specifically, for example, as shown by a thick solid line in FIG. 16, it is possible to geometrically calculate the refrigerant inflow amount of the expansion mechanism (50) with respect to the angular position of the second suction port (56). .
  • the actual refrigerant inflow is the geometrically determined refrigerant inflow. Less than. That is, as shown in FIG. 16 above, the actually measured value (blacked triangle) of the refrigerant inflow amount is due to pressure loss when the refrigerant flows into the first fluid chamber (72) from the second suction port (56). Therefore, it becomes smaller than the ideal refrigerant flow rate geometrically required.
  • the second suction port (72, 82) is at an angular position where the volume change of the fluid chamber (72, 82) communicating with the second suction port (56) is relatively large, as shown in FIG. 56), the effect of the suction pressure loss at the second suction port (56) increases, so the actual refrigerant inflow (solid triangle) is the geometrically determined refrigerant inflow ( It is greatly reduced compared to the thick solid line).
  • the correction value for the angular position corresponding to the geometrically calculated refrigerant inflow amount in consideration of the decrease in the refrigerant inflow amount due to the pressure loss at the time of refrigerant intake as described above.
  • the second suction port (56) is provided at an angular position corresponding to the actual refrigerant inflow amount.
  • the expansion ratio of the expansion mechanism (50) is set so as to be optimal during the rated operation of heating. Therefore, as described later in detail, the rated operation of cooling is performed. Sometimes, the pressure on the low-pressure side is higher than the rated operation of heating, so it is necessary to increase the inflow of high-pressure refrigerant. Therefore, from the second suction port (56) during rated operation of cooling It is necessary to set the position of the second suction port (56) so that the necessary refrigerant inflow amount can be supplied.
  • FIG. 17 shows a calculation example of the angular position of the second suction port (56).
  • the performance of the outdoor heat exchanger (14) (outdoor heat exchange) and the indoor heat exchanger (15) (indoor heat exchange) of the air conditioner (1) is changed (up or
  • the angular position of the second suction port (56) is determined so that the refrigerant flow rate required for the heating rated operation and the cooling rated operation in each case can be secured.
  • the high pressure indicates the discharge pressure from the compression mechanism (40)
  • the low pressure indicates the suction pressure of the compression mechanism (40).
  • the gas cooler outlet temperature is substantially equal to the inlet temperature of the expansion mechanism (50).
  • the relationship between the angular position of the second suction port (56) and the refrigerant flow rate (thick broken line) obtained geometrically even under different conditions (when the refrigerant flow rates are different).
  • the geometrically determined angular position of the second suction port (56) is corrected (thin broken line). This is almost the same as the measured value (open triangle). Therefore, the correction method as described above is sufficient.
  • the angular position of the second suction port (56) can be obtained with high accuracy. In the present embodiment, as is apparent from FIG.
  • the position of the second suction port (56) is preferably provided at an angular position larger than 120 ° at which the refrigerant flow rate changes by 10% or more. As shown in FIG. 17 above, it is more preferable to provide within a range of 150 200 °.
  • the operation of the air conditioner (1) will be described. Here, the operation of the air conditioner (1) during the cooling operation and the heating operation will be described, and then the operation of the expansion mechanism (50) will be described.
  • the four-way selector valve (12) is switched to the state indicated by the broken line in FIG.
  • the motor (26) of the compression / expansion unit (20) is energized in this state, the refrigerant circulates in the direction of the broken line arrow in the refrigerant circuit (10), and a vapor compression refrigeration cycle is performed.
  • the refrigerant compressed by the compression mechanism (40) is discharged from the compression / expansion unit (20) through the discharge pipe (23). In this state, the pressure of the refrigerant is higher than the critical pressure. This discharged refrigerant is sent to the outdoor heat exchanger (14) to radiate heat to the outdoor air.
  • the high-pressure refrigerant radiated by the outdoor heat exchanger (14) passes through the introduction pipe (24, 27) and is expanded.
  • the refrigerant that has flowed in absorbs heat from the indoor air and evaporates, thereby cooling the indoor air.
  • the low-pressure gas refrigerant generated by the indoor heat exchanger (15) is drawn into the compression mechanism (40) through the suction pipe (22).
  • the compression mechanism (40) compresses and discharges the sucked refrigerant again.
  • the four-way selector valve (12) is switched to the state shown by the solid line in FIG.
  • the motor (26) of the compression / expansion unit (20) is energized in this state, the refrigerant circulates in the direction of the solid arrow in the refrigerant circuit (10) to perform a vapor compression refrigeration cycle.
  • the refrigerant compressed by the compression mechanism (40) passes through the discharge pipe (23) and is compressed and expanded ( 20) In this state, the pressure of the refrigerant is higher than the critical pressure.
  • This discharged refrigerant is sent to the indoor heat exchanger (15). In the indoor heat exchanger (15), the inflowing refrigerant dissipates the indoor air and heats the indoor air.
  • the refrigerant that has radiated heat in the indoor heat exchanger (15) flows into the expansion mechanism (50) through the introduction pipes (24, 27).
  • the expansion mechanism (50) the high-pressure refrigerant expands, and power is recovered from the high-pressure refrigerant.
  • the expanded low-pressure refrigerant is sent to the outdoor heat exchanger (14) through the outlet pipe (25) and absorbs heat from the outdoor air to evaporate.
  • the low-pressure gas refrigerant generated by the outdoor heat exchanger (14) is sucked into the compression mechanism (40) through the suction pipe (22).
  • the compression mechanism (40) compresses the sucked refrigerant again and discharges it.
  • the intake stroke can be extended compared to the conventional configuration in which only the first intake port (55) is provided, and more high-pressure refrigerant can be introduced.
  • the first high-pressure chamber (73) and the second high-pressure chamber (83 ) Hardly expands the refrigerant, but after the second inlet port (56) is closed (after the rotation angle reaches about 520 °), the rotation angle of the second crankshaft (35) is 540 °.
  • the volume gradually increases to 630 ° the volume of the first high pressure chamber (73), that is, the first low pressure chamber (74) gradually decreases and the volume of the second high pressure chamber (83) gradually increases, resulting in expansion.
  • the volume of the chamber (59) gradually increases. This increase in the volume of the expansion chamber (59) continues until just before the rotation angle of the second crankshaft (35) reaches 720 °.
  • the refrigerant in the expansion chamber (59) expands in the process of increasing the volume of the expansion chamber (59), and the second crankshaft (35) is rotationally driven by the expansion of the refrigerant.
  • the refrigerant in the first low-pressure chamber (74) flows into the second high-pressure chamber (83) while expanding through the communication passage (54).
  • the rotation angle of the second crankshaft (35) gradually increased to 810 °, 900 °, 990 °, and until the rotation angle reached 1080 °, the second low pressure chamber (84)
  • the low-pressure refrigerant after expansion flows out of the tank.
  • FIG. 6 shows the relationship between the change in suction volume and the change in pressure in the expansion chamber (59) in the expansion mechanism (50).
  • the broken line is a graph when high-pressure refrigerant is introduced only from the first suction port (55) and no overexpansion occurs, and the thin solid line is the pressure only at the first suction port (55).
  • overexpansion has occurred in the expansion mechanism (50)! /, N! /, (In the case of! / In FIG.
  • the supercritical high-pressure refrigerant is It flows into the first high pressure chamber (73) from a to point b. Thereafter, the first high pressure chamber (73) communicates with the communication passage (54) and switches to the first low pressure chamber (74).
  • the expansion chamber (59) composed of the first low pressure chamber (74) and the second high pressure chamber (83) the internal high pressure refrigerant suddenly drops in pressure between points b and c and becomes saturated.
  • the refrigerant that has become saturated expands while evaporating a part of the refrigerant, and gradually decreases in pressure to point d.
  • the second high pressure chamber (83) communicates with the outflow port (57) and switches to the second low pressure chamber (84).
  • the refrigerant in the second low pressure chamber (84) is sent to the outflow port (35) until point e. At this time, the density ratio of the intake refrigerant and the exhaust refrigerant matches the design expansion ratio, and the power recovery efficiency and operation are performed.
  • the high pressure or the low pressure may deviate from the design value due to switching between cooling operation and heating operation or a change in the outside air temperature. That is, in FIG. 6, when the expansion mechanism (50) is designed so that the pressure and the suction volume change as indicated by the broken line when the air conditioner (1) is rated for heating, when switching to cooling operation, When the pressure on the side increases to the level of the thin solid line, the region of overexpansion (D) occurs.
  • the above-described configuration can recover power more efficiently than in the case of the injection method in the conventional expansion process (Fig. 7). That is, as shown in FIG. 7, in the configuration in which injection is performed, in addition to region B in which power is recovered by the high-pressure refrigerant introduced from the first suction port (55), only the portion in region C is driven as an effect of injection. Recovery is not possible. On the other hand, as shown by the alternate long and short dash line in FIG. 7, more power can be recovered with the above configuration.
  • the refrigerant circuit (10) is a closed circuit, and the flow rate of the refrigerant in the expansion mechanism (50) needs to coincide with the flow rate of the refrigerant in the compression mechanism (40).
  • the refrigerant circulation amount of the expansion mechanism (50) can be adjusted to an appropriate refrigerant circulation amount by simply increasing the refrigerant circulation amount.
  • the refrigerant flow rate of the expansion mechanism (50) is divided into a front throttle valve (60) provided in the first introduction pipe (24), an on-off valve (61) provided in the second introduction pipe (27), and a bypass pipe (65).
  • the opening / closing control or flow rate control of the bypass valve (66) provided in the! Will be described with reference to FIGS.
  • pressure detecting means (90) for detecting the pressure of the high-pressure refrigerant introduced into the expansion mechanism (50).
  • This pressure detecting means (90) is constituted by, for example, a pressure sensor (not shown) for detecting the pressure on the discharge side of the compression mechanism (40).
  • the pressure value of the high-pressure refrigerant detected by the pressure detection means (90) is sent to the controller (91).
  • the controller (91) has a front throttle valve flow rate control unit (92) for controlling the flow rate of the front throttle valve (60) and an open / close control for the on / off valve (61).
  • each control unit (92, 93, 94) is configured to control each valve (60, 61, 62).
  • the front throttle valve flow control unit (92) is the flow control means of the present invention
  • the open / close control unit (93) is the open / close valve control means of the present invention
  • the bypass valve flow control unit (93) Corresponds to the bypass flow rate control means (94) of the present invention.
  • each valve 60, 61, 62
  • the on-off valve (61) is closed.
  • the pressure of the high-pressure refrigerant introduced into the expansion mechanism (50) is detected by the pressure detection means (91) in step S1.
  • the pressure value is compared with a preset target value (step S2) . If the pressure value is larger than the target value (in the case of YES), first, the bypass valve (66) is set so that the pressure value becomes the target value. To finely adjust the amount of circulating refrigerant to the expansion mechanism (50).
  • the opening degree of the bypass valve (66) reaches a predetermined value (in the case of YES in step S4), the on-off valve (61) is opened to circulate the refrigerant in the expansion mechanism (50).
  • step S5 By increasing the amount, adjustment is made so that the refrigerant circulation amount is the same as that of the compression mechanism (40) (step S5). Even when the on-off valve (61) is opened as described above, the circulation amount is finely adjusted by the bypass valve (66). If the opening of the bypass valve (66) is smaller than a predetermined value in step S4, the process returns to step S2 until the pressure value reaches the target value or the opening of the bypass valve (66) The opening of the bypass valve (66) is increased until a predetermined value is reached.
  • the target value is set to a pressure value at which COP is maximized
  • the predetermined value of the opening degree of the bypass valve (66) corresponds to the predetermined opening degree of the present invention. 66) means that the opening cannot be opened any more, or that the flow rate cannot be adjusted even if it is opened further.
  • step S2 when the pressure value is equal to or less than the target value (NO in step S2), the process proceeds to step S6 to determine whether the pressure value is smaller than the target value. If it is determined that the pressure value is not smaller than the target value (NO in step 6), the pressure value is equal to the target value, so return to the start (return) and start this flow again. .
  • step S6 If it is determined in step S6 that the pressure value is smaller than the target value (YES), then in step S7, the bypass valve (66) is closed and the pressure value reaches the target value.
  • the refrigerant circulation amount to the expansion mechanism (50) is finely adjusted so that If the pressure value is still smaller than the target value (YES in step S8), in step S9, the open / close valve (61) is closed and the expansion mechanism (50) is turned on. Reduce the amount of refrigerant circulation. At this time, since the refrigerant circulation amount of the compression mechanism (40) is small, it is necessary to reduce the expansion mechanism (50) accordingly. At this time, fine adjustment of the refrigerant circulation amount to the expansion mechanism (50) is performed by the bypass valve (66).
  • step S10 If the pressure value is smaller than the target value even when the on / off valve (61) is closed in step 9 above (if YES in step S10), the bypass valve (66) Is fully closed or almost fully closed (predetermined opening) (step S11), and if it is still smaller than the target value (YES in step S12), the front throttle valve (60) is throttled to reduce the refrigerant. The circulation amount is adjusted (step S13). After that, it returns to the start (return) and starts this flow again.
  • steps S8, S10, and S12 it is determined that the pressure value is not smaller than the target value. If this is the case (NO), the pressure value is equal to the target value, so return to the start (return) and start this flow again.
  • FIG. 10 An example of the valve control according to the flowchart shown in FIG. 9 is shown in FIG. 10, where the relationship between the refrigerant circulation amount of the expansion mechanism (50) and the opening degree of each valve (60, 61, 66) is schematically shown.
  • the representation is shown in Fig. 11, and the relationship between the refrigerant suction volume and pressure when the on-off valve is opened is shown in Fig. 12, respectively.
  • FIGS. 10 to 12 are examples in which a plurality of suction ports of the expansion mechanism (50) are provided. In this case, only the number of on-off valves is increased accordingly.
  • a step for opening or closing the other on-off valves may be added.
  • the front throttle valve (60) is fully opened and the step (STP) proceeds (the value of STP is large). Accordingly, if the difference between the pressure value and the target value is small, the flow rate of the high-pressure refrigerant introduced into the expansion mechanism (50) by the bypass valve (66) so that the pressure value becomes the target value.
  • the on-off valve (61) is opened. In the example of FIG. 10, there are three suction ports of the expansion mechanism (50), the second suction port on-off valve is the second suction valve, and the third suction port on-off valve is the third suction port. It is a suction valve.
  • step (STP) proceeds in a decreasing direction, and the flow rate is controlled by the bypass valve (66) while the on-off valve is controlled.
  • the bypass valve (66) is fully closed and the refrigerant circulation rate is adjusted by the front throttle valve (60).
  • the refrigerant circulation amount of the expansion mechanism (50) when the refrigerant circulation amount of the expansion mechanism (50) is increased, the refrigerant circulation amount is increased stepwise by sequentially opening and closing the plurality of on-off valves.
  • the refrigerant circulation amount can be increased smoothly by adjusting the refrigerant circulation amount with the bypass valve (66) until the on-off valve is opened.
  • the refrigerant suction volume can be increased as shown in FIG.
  • the on-off valve closing control is performed.
  • the refrigerant circulation amount can be reduced stepwise, and the refrigerant circulation amount can be reduced smoothly by adjusting the refrigerant circulation amount with the bypass valve (66) until the on-off valve is closed. it can. Further, even if the on-off valve is closed and the bypass valve (66) is fully closed, the refrigerant circulation amount can be adjusted by the front throttle valve (60).
  • the refrigerant circulation amount to the expansion mechanism (50) can be increased and decreased quickly and smoothly in a wide range, and the compression mechanism (40) It is possible to maintain a balance with the refrigerant circulation amount.
  • the first and second suction ports (55, 56) are provided in the expansion mechanism (50), and the first introduction pipe (24) communicating with the first suction port (55) is provided.
  • the high-pressure refrigerant introduced into the expansion mechanism (50) can be quickly and reliably increased or decreased according to the increase or decrease in the amount, and the refrigerant circulation amount of the high-pressure refrigerant introduced into the expansion mechanism (50) can be reduced by the compression mechanism ( Power recovery can be efficiently performed from the energy of the high-pressure refrigerant while maintaining a balance with the refrigerant circulation amount of 40).
  • the suction port (55, 56) By opening the suction port (55, 56) below the first fluid chamber (72), the refrigerating machine oil in the fluid chamber (72) is placed in the suction port (55, 56). As a result, it is possible to prevent the refrigerant from accumulating. That is, by providing the suction port (55, 56) in the fluid chamber (72) from below, it is possible to prevent the suction port (55, 56) from becoming dead volume.
  • the refrigerant can be efficiently expanded by the expansion mechanism (50).
  • the expansion mechanism (50) is a two-stage rotary expander including the first rotary mechanism section (70) and the second rotary mechanism section (80). In this way, the suction port and the outflow port do not communicate with each other through the fluid chamber, and the high-pressure refrigerant introduced from the suction port can be prevented from blowing through to the outflow port. Therefore, above The expansion mechanism (50) can sufficiently expand the high-pressure refrigerant in the fluid chamber (72, 82).
  • the second suction port (56) was obtained by performing a predetermined correction with respect to the angular position obtained geometrically so as to ensure the displacement required during rated operation of the cooling.
  • the first modification differs from the first embodiment in that a check valve (95) is provided in the second suction port (56) of the expansion mechanism (50).
  • a check valve is provided to allow only the refrigerant to flow into the first fluid chamber (72) into the second suction port (56) and not to flow in the opposite direction. (95) is provided. This prevents the refrigerant from flowing back from the fluid chamber (72) even when the on-off valve (61) is closed and the high-pressure refrigerant is not introduced from the second suction port (56). It can be surely prevented. That is, the dead volume of the second suction port (56) can be reliably reduced, and the refrigerant can be efficiently expanded by the expansion mechanism (50).
  • Modification 2 is different from the above embodiment in that the expansion mechanism is a three-stage rotary expander including three rotary mechanism portions.
  • the expansion mechanism (100) includes a first rotary mechanism portion (101) and a second rotary mechanism portion (111) having substantially the same configuration as that of the first embodiment, and an upper side thereof.
  • a third rotary mechanism (121) with a larger diameter is provided!
  • the communication path (115) is directed outwardly from the outer peripheral surface of the cylindrical second piston (116) disposed in the second cylinder (112).
  • the third blade (125) extending radially outward from the third piston (124) disposed in the third cylinder (122) is supported from the right side of the bush (118) of the second blade (117) extending. It extends so as to extend to the left side of the bush (12 6).
  • the fluid chamber of the second cylinder (112) communicates with the fluid chamber of the third cylinder (122).
  • the refrigerant expands as it moves from the second cylinder (112) to the third cylinder (122) as it moves to the second cylinder (112).
  • the expansion mechanism (100) having the above-described configuration with the plurality of suction ports (103, 104, 113, 114) as described above, the above-described embodiment can be achieved even with a three-stage rotary expander. Similar to 1, the refrigerant circulation amount of the expansion mechanism (100) can be adjusted while efficiently recovering the power of the high-pressure refrigerant.
  • the second embodiment is different from the first embodiment in which the expansion mechanism (50) includes two rotary mechanism portions (70, 80), and the expansion mechanism is a scroll mechanism (200). It is composed. Since the configuration other than the expansion mechanism is the same as that of the first embodiment, description and illustration are omitted.
  • the scroll mechanism (200) includes a fixed scroll (220) fixed to a casing (not shown) and a movable scroll (210) held on the casing via an Oldham ring (not shown). ).
  • the fixed scroll (220) constitutes a scroll member, and includes a flat fixed end plate (not shown) and a spiral fixed wrap (221) standing on the fixed end plate.
  • the movable scroll (210) constitutes a scroll member and includes a flat plate-like movable mirror plate (not shown) and a spiral movable wrap (211) standing on the movable mirror plate.
  • the fixed wrap (221) of the fixed scroll (220) and the movable wrap (211) of the movable scroll (210) Are mixed together, and a plurality of fluid chambers (230) are formed between the two!
  • the fixed scroll (220) is formed with a suction port (201) and an outflow port (202), as well as a second suction port (203, 203), a third suction port (204, 204), and a fourth suction port.
  • Two sheets (205, 205) are formed.
  • the suction port (201) opens in the vicinity of the winding start side end of the fixed wrap (221).
  • the outflow port (202) opens in the vicinity of the winding end side end of the fixed wrap (221).
  • the second to fourth suction ports (203, 204, 205) are provided at positions that sequentially communicate with the space on the wrap (221) start side in the suction process.
  • the space force sandwiched between the inner surface of the fixed wrap (221) and the outer surface of the movable wrap (211) A chamber as the first fluid chamber (230) ( 231).
  • the space sandwiched between the outer surface of the fixed wrap (221) and the inner surface of the movable wrap (211) constitutes the B chamber (232) as the second fluid chamber (230)! .
  • the second to fourth suction ports (203, 204, 205) are provided with the second suction port (203, 203), the third suction port (204, 204), The fourth suction port (205, 205) starts to communicate with the fluid chamber (230) in this order until the next formed fluid chamber (230) begins to be divided into two chambers (the movable scroll (210) becomes the fixed scroll (220)). (Until it revolves 540 °), it communicates with the fluid chamber (230)!
  • the inlet pipes connected to the second to fourth suction ports (203, 204, 205) are each provided with an on-off valve (not shown).
  • a high pressure discharge pressure of the compressor
  • opening / closing control is performed.
  • a front throttle valve is provided in the introduction pipe connected to the suction port (201), and a bypass valve is provided in the bypass pipe that bypasses the expansion mechanism.
  • the control of each valve is the same as in the first embodiment.
  • the high-pressure refrigerant introduced from the suction port (101) begins to wind the fixed-side wrap (221). It flows into one fluid chamber (230) sandwiched between the vicinity and the vicinity of the start of winding of the movable wrap (211). That is, the high-pressure refrigerant is introduced from the suction port (101) into the fluid chamber (130).
  • the winding start side end of the fixed wrap (221) is in contact with the inner surface of the movable wrap (211) and at the same time the winding start side end of the movable wrap (211) is fixed wrap (
  • the state in contact with the inner surface of 221) is defined as the standard 0 °.
  • the fluid chamber (230) expands and the fluid chamber (230) is The second suction port (203, 203), the third suction port (204, 204), and the fourth suction port (205, 205) communicate with each other in this order.
  • the fluid chamber (230) is gradually partitioned into two spaces, and when the revolving angle reaches 360 °, the fluid chamber (130) is divided into the A chamber (231) and the B chamber (232).
  • the expansion step in the A chamber (231) continues until the revolution angle of the movable scroll (210) reaches 1020 °, and when the movable scroll (210) further rotates, the A chamber (231) In communication with the outflow port (202), the refrigerant in the A chamber (231) flows out from the outflow port (202) to the outside, and the discharge process is started.
  • the expansion process in the B chamber (232) continues until the revolution angle of the movable scroll (210) reaches 840 °, and when the movable scroll (210) further rotates, the B chamber ( 232) communicates with the outflow port (202), the refrigerant in the B chamber (232) flows out from the outflow port (202) to the outside, and the discharge process is started.
  • the force provided by the four suction ports is not limited to the above. As in the first embodiment, only two may be provided, or three or five or more may be provided.
  • the refrigerant circulation amount of the expansion mechanism can be increased. That is, for example, even when it is necessary to increase the refrigerant circulation amount of the expansion mechanism where the pressure value on the high pressure side is larger than the target value, the necessary refrigerant circulation amount can be reduced by introducing the high-pressure refrigerant from the inflow ports (203, 204, 205).
  • the refrigerant circulation amount of the expansion mechanism and the refrigerant circulation amount of the compression mechanism can be balanced.
  • the present invention may be configured as follows with respect to the above embodiment.
  • each rotary mechanism portion (70, 80) of the expansion mechanism (50) is constituted by a oscillating piston type rotary fluid machine.
  • Each rotary mechanism (70, 80) may be constituted by a fluid machine.
  • the blade (76, 86) is formed separately from the piston (75, 85). Further, the bushes (77, 87) are omitted from the rotary mechanism portions (70, 80). The blades (76,86) follow the movement of the piston (75,85) with the tip thereof pressed against the outer peripheral surface of the piston (75,85). Reciprocate to.
  • the two suction ports (55, 56) are provided in the expansion mechanism (50).
  • three or more suction ports may be provided.
  • the scroll mechanism (200) is provided with four suction ports (201, 203, 204, 205). However, as long as this is limited, two or three, or five or more may be provided.
  • the front throttle valve (60) is provided, but in this case, it may be provided upstream of the branch position. In this case, the entire flow rate of the first and second suction ports (55, 56) is adjusted by the front throttle valve.
  • the present invention is useful for a refrigeration apparatus including an expansion mechanism that generates power by expansion of a fluid.

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Abstract

L'invention concerne un appareil de congélation, qui est constitué pour rendre variable la quantité d'entrée d'un liquide de refroidissement d'un mécanisme de détente, tout en récupérant l'énergie d'un liquide de refroidissement haute pression sous forme de puissance au maximum par le mécanisme de détente. Le mécanisme de détente (50) est équipé de deux unités de mécanisme rotatives (70 et 80) ayant des cylindrées différentes. Ces unités de mécanisme rotatives sont reliées en série, et l'unité de mécanisme rotative ayant la plus petite cylindrée possède deux orifices d'entrée (55 et 56) formés dans son cylindre (71). Des tuyaux d'entrée (24 et 27), reliés aux orifices d'entrée (55 et 58), sont équipés d'un robinet d'étranglement avant (60) et d'une soupape de commutation (61). Un tuyau de dérivation (65) destiné à éviter le mécanisme de détente (50) est équipé d'une soupape de dérivation (66). Ces soupapes (60, 61 et 66) sont commandées pour atteindre un équilibre entre la vitesse de circulation du liquide de refroidissement du mécanisme de détente (50) et la vitesse du circulation de liquide de refroidissement d'un mécanisme de compression (40).
PCT/JP2007/073703 2006-12-08 2007-12-07 Appareil de congélation et détendeur WO2008072575A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP07850281.2A EP2090746B1 (fr) 2006-12-08 2007-12-07 Appareil de congélation et détendeur
CN2007800448285A CN101548066B (zh) 2006-12-08 2007-12-07 冷冻装置及膨胀机
ES07850281T ES2721233T3 (es) 2006-12-08 2007-12-07 Aparato de congelación y expansor

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JP2006-331664 2006-12-08
JP2006331664 2006-12-08
JP2007316259A JP4946840B2 (ja) 2006-12-08 2007-12-06 冷凍装置
JP2007-316259 2007-12-06

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WO2008072575A1 true WO2008072575A1 (fr) 2008-06-19

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JP (1) JP4946840B2 (fr)
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JP2012122343A (ja) * 2010-12-06 2012-06-28 Mitsubishi Electric Corp 排熱回生装置
WO2013084618A1 (fr) * 2011-12-05 2013-06-13 株式会社豊田自動織機 Mécanisme de détente à volute
WO2013161888A1 (fr) * 2012-04-26 2013-10-31 サンデン株式会社 Détendeur à spirale
JP2020148177A (ja) * 2019-03-15 2020-09-17 富士電機株式会社 スクロール膨張機
US11971038B2 (en) * 2020-03-31 2024-04-30 Gree Electric Appliances, Inc. Of Zhuhai Single-stage enthalpy enhancing rotary compressor and air conditioner having same

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JP5535511B2 (ja) 2009-03-31 2014-07-02 三菱重工業株式会社 密閉型流体機械の製造方法および密閉型流体機械
DE102010034230A1 (de) * 2010-08-07 2012-02-09 Daimler Ag Expansionsvorrichtung zur Verwendung in einem Arbeitsmittelkreislauf und Verfahren zum Betrieb einer Expansionsvorrichtung
JP5597589B2 (ja) * 2011-04-19 2014-10-01 株式会社神戸製鋼所 スクリュ膨張機
US20140075941A1 (en) * 2012-09-14 2014-03-20 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Power generating apparatus and operation method thereof
CN105041383B (zh) * 2014-07-24 2018-04-10 摩尔动力(北京)技术股份有限公司 受控阀容积型变界流体机构
JP6403282B2 (ja) * 2015-09-11 2018-10-10 株式会社神戸製鋼所 熱エネルギー回収装置
JP6779361B2 (ja) * 2017-03-09 2020-11-04 三菱電機株式会社 空気調和装置
JP6975066B2 (ja) * 2018-02-20 2021-12-01 住友重機械工業株式会社 極低温冷凍機

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JP2012122343A (ja) * 2010-12-06 2012-06-28 Mitsubishi Electric Corp 排熱回生装置
WO2013084618A1 (fr) * 2011-12-05 2013-06-13 株式会社豊田自動織機 Mécanisme de détente à volute
JP2013117207A (ja) * 2011-12-05 2013-06-13 Toyota Industries Corp スクロール膨張機
WO2013161888A1 (fr) * 2012-04-26 2013-10-31 サンデン株式会社 Détendeur à spirale
JP2020148177A (ja) * 2019-03-15 2020-09-17 富士電機株式会社 スクロール膨張機
JP7287022B2 (ja) 2019-03-15 2023-06-06 富士電機株式会社 スクロール膨張機
US11971038B2 (en) * 2020-03-31 2024-04-30 Gree Electric Appliances, Inc. Of Zhuhai Single-stage enthalpy enhancing rotary compressor and air conditioner having same

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EP2090746A1 (fr) 2009-08-19
JP4946840B2 (ja) 2012-06-06
EP2090746B1 (fr) 2019-01-23
EP2090746A4 (fr) 2016-06-01
JP2008163938A (ja) 2008-07-17
ES2721233T3 (es) 2019-07-29
CN101548066B (zh) 2011-05-04
CN101548066A (zh) 2009-09-30

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