WO2011013199A1 - Dispositif de pompe à chaleur, compresseur avec mécanisme d'injection et procédé de fabrication d'un compresseur à spirale avec mécanisme d'injection - Google Patents

Dispositif de pompe à chaleur, compresseur avec mécanisme d'injection et procédé de fabrication d'un compresseur à spirale avec mécanisme d'injection Download PDF

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Publication number
WO2011013199A1
WO2011013199A1 PCT/JP2009/063412 JP2009063412W WO2011013199A1 WO 2011013199 A1 WO2011013199 A1 WO 2011013199A1 JP 2009063412 W JP2009063412 W JP 2009063412W WO 2011013199 A1 WO2011013199 A1 WO 2011013199A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
chamber
injection
valve
compression
Prior art date
Application number
PCT/JP2009/063412
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English (en)
Japanese (ja)
Inventor
茗ヶ原　将史
西木　照彦
広康 高橋
令 三坂
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP09847791.2A priority Critical patent/EP2461122B1/fr
Priority to KR1020117031134A priority patent/KR101312762B1/ko
Priority to CN200980160586.5A priority patent/CN102472528B/zh
Priority to JP2011524561A priority patent/JP5389173B2/ja
Priority to PCT/JP2009/063412 priority patent/WO2011013199A1/fr
Publication of WO2011013199A1 publication Critical patent/WO2011013199A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2600/2509—Economiser valves

Definitions

  • the present invention relates to, for example, a heat pump apparatus having an injection circuit and an injection-compatible compressor having an injection mechanism.
  • the present invention also relates to a method for manufacturing a scroll compressor having an injection mechanism.
  • a scroll compressor having an injection mechanism when the valve of the injection circuit (the third expansion valve 14 shown in FIG. 1 in Patent Document 1) is closed and the injection operation is not performed, the refrigerant in the compression chamber is compressed during the injection circuit. It will flow out to the side. That is, when the injection operation is not performed, the injection circuit becomes a dead volume in the compression process, leading to a decrease in compression efficiency. Also, when the pressure in the compression chamber becomes transiently higher than the pressure of the refrigerant that has left the condenser, the refrigerant being compressed in the compression chamber flows out of the injection circuit to the condenser side.
  • An object of the present invention is to prevent, for example, a refrigerant in the middle of compression in the compression chamber from flowing out to the injection circuit side.
  • the heat pump device is, for example, A main refrigerant circuit in which a compressor, a radiator, a first expansion valve, and an evaporator are sequentially connected; An injection circuit provided between the radiator and the first expansion valve in the main refrigerant circuit and an injection pipe provided in the compressor, and provided with a second expansion valve; When the opening of the second expansion valve decreases, the flow path from the injection pipe to the compression chamber of the compressor is closed, and when the opening of the second expansion valve increases, the compression from the injection pipe of the compressor A mechanism for opening a flow path to the chamber is provided.
  • the mechanism operates by a pressure difference between the refrigerant flowing through the main refrigerant circuit and the refrigerant flowing through the injection circuit.
  • the mechanism is A refrigerant inflow chamber provided in the middle of the flow path and into which refrigerant flows from the injection circuit via the injection pipe;
  • An on-off valve chamber provided between the refrigerant inflow chamber and the compression chamber in the flow path and connected to the refrigerant inflow chamber and the compression chamber, and a connection port with the refrigerant inflow chamber;
  • a connection port with the compression chamber is formed in the same plane in the room, and the connection port with the refrigerant inflow chamber is opened and closed by a pressure difference between the refrigerant on the refrigerant inflow chamber side and the refrigerant on the compression chamber side.
  • an on-off valve chamber provided with the on-off valve.
  • An injection-compatible compressor is, for example, A compression section that forms a compression chamber and compresses the suction refrigerant of the suction pressure sucked into the compression chamber to a discharge pressure;
  • a refrigerant injection unit that injects the injection refrigerant into an intermediate pressure unit in which the intake refrigerant has an intermediate pressure higher than the suction pressure and lower than the discharge pressure, and
  • the refrigerant injection part is A refrigerant inflow chamber into which the injection refrigerant flows from outside;
  • An on-off valve chamber connected to the refrigerant inflow chamber and the intermediate pressure portion of the compression chamber, wherein a connection port with the refrigerant inflow chamber and a connection port with the intermediate pressure portion are in the same plane in the room
  • an on-off valve chamber provided with an on-off valve that opens and closes a connection port with the refrigerant inflow chamber by a pressure difference between the refrigerant on the refrigerant inflow chamber side and the refrig
  • the on-off valve is a plate-like member provided so as to be movable in a predetermined movement direction in the on-off valve chamber, and is connected to the intermediate pressure portion when the connection port with the refrigerant inflow chamber is closed. It is a plate-like member in which a hole is formed at a position overlapping with the mouth.
  • a guide hole is formed in the on-off valve, and a guide rod provided in the on-off valve chamber and extending in the moving direction is provided to penetrate the guide hole.
  • the on-off valve chamber is formed in a cylindrical shape in which a connection port with the refrigerant inflow chamber and a connection port with the intermediate pressure part are formed on the bottom surface,
  • the on-off valve is a circular plate-like member in which the guide hole is formed, and is provided so as not to rotate around the guide rod when the guide rod is engaged with the guide hole. .
  • the on-off valve chamber is formed in a cylindrical shape in which a connection port with the refrigerant inflow chamber and a connection port with the intermediate pressure part are formed on the bottom surface,
  • the on-off valve has a circular shape with a diameter smaller than a circle on the bottom surface of the on-off valve chamber, and has a guide hole having substantially the same size and the same shape as the outer periphery of the guide rod.
  • the on-off valve is a leaf spring.
  • the compression section includes an orbiting scroll having an orbiting spiral tooth formed on an upper surface side of an orbiting base plate, and a fixed spiral tooth that meshes with the orbiting spiral tooth of the orbiting scroll to form the compression chamber.
  • the refrigerant inflow chamber is a room formed inside from the side of the fixed base plate,
  • the on-off valve chamber is a chamber formed on the upper surface side of the fixed base plate.
  • the on-off valve chamber is a chamber in which a depression formed on the upper surface side of the fixed base plate is covered with a back plate.
  • the compression unit forms a compression chamber in which the swinging spiral teeth of the swing scroll and the fixed spiral teeth of the fixed scroll mesh with each other,
  • the on-off valve chamber is provided corresponding to each compression chamber of the paired compression chamber.
  • the injection-compatible compressor further includes: A sealed container that houses the compression section and the refrigerant injection section; And an injection pipe that is provided through the side surface of the sealed container and allows the injection refrigerant to flow into the refrigerant inflow chamber from the outside.
  • the sealed container has a lower container and an upper container that forms a sealed space in combination with the lower container,
  • the injection pipe is provided through the side surface of the lower container.
  • the method for manufacturing an injection-compatible scroll compressor according to the present invention is, for example,
  • the swing spiral teeth are formed on one side of the swing base plate,
  • a fixed spiral tooth is formed on one side of the fixed base plate, Forming a side hole in the side of the fixed base plate, Forming a recess on the other side of the fixed base plate,
  • a first communication hole that communicates the bottom surface of the recess and the side hole, and a second communication hole that communicates the bottom surface of the recess and the one surface side of the fixed base plate are formed in the fixed base plate.
  • An opening / closing valve that opens and closes the first communication hole is disposed in the recess formed in the fixed base plate,
  • a back plate is attached to the fixed base plate so as to close the opening of the recess in which the on-off valve is disposed,
  • the swing base plate on which the swing spiral teeth are formed is disposed in a sealed container,
  • the fixed base plate on which the fixed spiral teeth are formed is disposed in the sealed container so as to form a compression chamber by meshing the fixed spiral teeth and the swing spiral teeth.
  • the heat pump device Since the heat pump device according to the present invention opens and closes the flow path from the injection pipe to the compression chamber according to the opening of the second expansion valve, the refrigerant in the compression chamber in the compression chamber is injected into the injection circuit when the injection operation is not performed. Can be prevented from leaking into.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor 100 according to Embodiment 1.
  • the upper enlarged view (3) of the scroll compressor 100 shown in FIG. The figure which shows the heat pump apparatus which has an injection circuit.
  • coolant of the heat pump apparatus shown in FIG. The figure which showed the relative position of the rocking scroll 2 with respect to the fixed scroll 1 every 90 degree
  • the disassembled perspective view which shows the structure of the injection chamber 1f.
  • FIG. 4 is a longitudinal sectional view of a scroll compressor 100 according to a second embodiment.
  • injection means that the liquid refrigerant (two-phase refrigerant) or gas refrigerant (high-pressure side) after exiting the condenser is returned to the middle of the compressor compression chamber and recompressed.
  • the liquid refrigerant (two-phase refrigerant) or gas refrigerant (on the high pressure side) after exiting the condenser is called an injection refrigerant.
  • the term “after exiting the condenser” may be the refrigerant after passing through a predetermined expansion valve, a predetermined heat exchanger, or the like, not immediately after leaving the condenser.
  • the condenser may be read as a radiator, a heat exchanger that gives heat to the load side, or a gas cooler.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor 100 according to the first embodiment.
  • the scroll compressor 100 is an injection-compatible compressor having an injection mechanism.
  • FIGS. 2 to 4 are enlarged top views of the scroll compressor 100 shown in FIG. 1, and all show the same portion.
  • FIG. 2 is a diagram for explaining the fixed scroll 1 in particular.
  • FIG. 3 is a diagram specifically illustrating the orbiting scroll 2.
  • FIG. 4 is a diagram for explaining the compliant frame 3 and the guide frame 4 in particular.
  • components that are not originally visible are indicated by broken lines.
  • the scroll compressor 100 includes a fixed scroll 1, an orbiting scroll 2, a compliant frame 3, a guide frame 4, an electric motor 5, a subframe 6, a main shaft 7, and an Oldham mechanism 8 in an airtight container 10. It is stored and formed.
  • the fixed scroll 1 and the orbiting scroll 2 are collectively referred to as a compression unit.
  • the fixed scroll 1 will be described with reference to FIGS.
  • the outer peripheral portion of the fixed scroll 1 is fastened and fixed to the guide frame 4 with bolts.
  • a plate-like spiral tooth 1 b (fixed spiral tooth) is formed on one surface side (lower side in FIG. 2) of the base plate portion 1 a of the fixed scroll 1.
  • a compression chamber 20 is formed by meshing a spiral tooth 1b of the fixed scroll 1 and a spiral tooth 2b (oscillating spiral tooth) of the swing scroll 2 described later.
  • Two Oldham guide grooves 1c are formed in a substantially straight line on the outer peripheral portion on the one surface side (the lower side in FIG. 2) of the base plate portion 1a.
  • a claw 8b of the Oldham mechanism 8 is engaged with the Oldham guide groove 1c so as to be slidable back and forth.
  • a discharge port 1d is provided at substantially the center of the base plate portion 1a so as to penetrate the base plate portion 1a. Further, from the side part of the base plate part 1a, the outside of the closed container 10 is provided via an injection pipe 41 (refrigerant inlet) provided through the closed container 10 in the side part of the base plate part 1a. A refrigerant inflow chamber 1e into which the injection refrigerant flows from the injection circuit is formed. Further, on the opposite surface side (upper side in FIG. 2) of the base plate portion 1a, there are two on-off valve chambers 1f (check valve chambers) in which the openings of the two depressions are covered with the back plate 31 and sealed. Is formed.
  • each on-off valve chamber 1f On the lower surface of each on-off valve chamber 1f, a connection port with an inflow chamber communication passage 1g (inflow chamber communication hole, first communication hole) communicating with the refrigerant inflow chamber 1e, and a compression chamber communication passage 1h ( A compression chamber communication hole and a second communication hole) are formed. Further, an on-off valve 30 (check valve) is accommodated in each on-off valve chamber 1f. The on-off valve 30 and the back plate 31 will be described in detail later.
  • a mechanism for injecting the injection refrigerant into the compression chamber such as the refrigerant inflow chamber 1e, the inflow chamber communication passage 1g, the on-off valve chamber 1f, the compression chamber communication passage 1h, the on-off valve 30, the back plate 31, and the like is referred to as a refrigerant injection portion.
  • a plate-like spiral tooth 2 b having substantially the same shape as the spiral tooth 1 b of the fixed scroll 1 is formed on one surface side (the upper side in FIG. 3) of the base plate portion 2 a of the orbiting scroll 2.
  • the compression chamber 20 is formed when the spiral tooth 1 b of the fixed scroll 1 and the spiral tooth 2 b of the orbiting scroll 2 are engaged with each other.
  • An Oldham guide groove 2e having a phase difference of about 90 degrees from the Oldham guide groove 1c of the fixed scroll 1 is almost straight on the outer peripheral portion of the base plate portion 2a opposite to the spiral tooth 2b (the lower side in FIG. 3). Two are formed on the line.
  • a claw 8a of the Oldham mechanism 8 is engaged with the Oldham guide groove 2e so as to be slidable back and forth.
  • a hollow cylindrical boss 2f is formed at the center of the base plate 2a opposite to the spiral teeth 2b (lower side in FIG. 3), and the inside of the boss 2f swings. It becomes the bearing 2c.
  • a rocking shaft portion 7b at the upper end of the main shaft 7 is engaged with the rocking bearing 2c.
  • a space between the rocking bearing 2c and the rocking shaft portion 7b is referred to as a boss space 15a.
  • a thrust surface 2d is formed on the outer diameter side of the boss portion 2f. The thrust surface 2d is slidable against the thrust bearing 3a of the compliant frame 3.
  • a space formed between the thrust surface 2d of the orbiting scroll 2 and the compliant frame 3 on the outer diameter side of the boss portion 2f is referred to as a boss portion outer diameter space 15b.
  • a space formed between the base plate portion 2a of the orbiting scroll 2 and the compliant frame 3 on the outer diameter side of the thrust bearing 3a is referred to as a base plate outer diameter portion space 15c.
  • the base plate outer diameter space 15c is a low pressure space of the suction gas atmospheric pressure (suction pressure).
  • the base plate portion 2a is provided with a bleed hole 2j penetrating from the surface on the fixed scroll 1 side (upper surface in FIG. 3) to the surface on the compliant frame 3 side (lower surface in FIG. 3). .
  • the base plate 2a is provided with a bleed hole 2j that allows the compression chamber 20 and the space on the thrust surface 2d side to communicate with each other.
  • the extraction hole 2j is arranged so that the circular locus drawn by the opening (lower opening 2k) on the compliant frame 3 side of the extraction hole 2j during normal operation is always within the thrust bearing 3a of the compliant frame 3. Has been. Therefore, the refrigerant does not leak from the bleed hole 2j to the boss portion outer diameter space 15b or the base plate outer diameter space 15c.
  • the compliant frame 3 and the guide frame 4 will be described with reference to FIGS.
  • upper and lower cylindrical surfaces 3 d and 3 e provided on the outer peripheral portion are supported in a radial direction by cylindrical surfaces 4 a and 4 b provided on the inner peripheral portion of the guide frame 4.
  • a main bearing 3c and an auxiliary main bearing 3h for supporting the main shaft 7 driven to rotate by the electric motor 5 in the radial direction are formed.
  • a space formed between the guide frame 4 and the compliant frame 3 and partitioned vertically by ring-shaped sealing materials 16a and 16b is referred to as a frame space 15d.
  • ring-shaped seal grooves for accommodating the sealing materials 16a and 16b are formed at two locations on the inner peripheral surface of the guide frame 4.
  • the seal groove may be formed on the outer peripheral surface of the compliant frame 3.
  • the compliant frame 3 passes through from the thrust bearing 3a side to the frame space 15d side at a position facing the lower opening 2k of the bleed hole 2j so that the bleed hole 2j and the frame space 15d are constantly or intermittently provided.
  • a communication hole 3s that communicates is formed.
  • the compliant frame 3 is provided with an adjustment valve space 3p in which a valve 3t for adjusting the pressure in the boss outer diameter space 15b, a valve presser 3y, and an intermediate pressure adjustment spring 3m are housed.
  • the intermediate pressure adjusting spring 3m is accommodated in the adjusting valve space 3p in a state of being contracted from the natural length.
  • a space between the compliant frame 3 and the guide frame 4 on the outer diameter side of the valve 3t is referred to as a valve outer diameter space 15e.
  • the compliant frame 3 is formed with a reciprocating sliding portion 3x on the outer diameter side of the thrust bearing 3a, in which the Oldham mechanism annular portion 8c reciprocates.
  • the reciprocating sliding portion 3x is formed with a communication hole 3n that communicates the valve outer diameter space 15e and the base plate outer diameter space 15c.
  • the outer peripheral surface of the guide frame 4 is fixed to the sealed container 10 by shrink fitting or welding. However, a notch is provided in the outer peripheral portion of the guide frame 4, and a flow path through which the refrigerant discharged from the discharge port 1 d flows to the discharge pipe 43 is secured.
  • the upper fitting cylindrical surface 4 a is engaged with an upper fitting cylindrical surface 3 d formed on the outer peripheral surface of the compliant frame 3.
  • a lower fitting cylindrical surface 4b is formed on the inner surface of the guide frame 4 on the motor 5 side (lower side in FIG. 4).
  • the lower fitting cylindrical surface 4 b is engaged with a lower fitting cylindrical surface 3 e formed on the outer peripheral surface of the compliant frame 3.
  • a rocking shaft portion 7b that is rotatably engaged with the rocking bearing 2c of the rocking scroll 2 is formed on the main shaft 7 on the rocking scroll 2 side (the upper side in FIG. 1).
  • a main shaft portion 7c that is rotatably engaged with the main bearing 3c and the auxiliary main bearing 3h of the compliant frame 3 is formed below the swing shaft portion 7b.
  • a sub-shaft portion 7d that is rotatably engaged with the sub-bearing 6a of the sub-frame 6 is formed on the opposite side of the main shaft 7 (lower side in FIG. 1).
  • the rotor 5a of the electric motor 5 is shrink-fitted between the auxiliary shaft portion 7d and the main shaft portion 7c described above, and the stator 5b is provided around the rotor 5a.
  • a high-pressure oil supply hole 7g is provided in the main shaft 7 so as to penetrate in the axial direction.
  • an oil pipe 7 f communicating with the high-pressure oil supply hole 7 g is press-fitted into the lower end surface of the main shaft 7.
  • Low-pressure suction refrigerant enters the compression chamber 20 formed by the spiral teeth 1 b of the fixed scroll 1 and the spiral teeth 2 b of the swing scroll 2 from the suction pipe 42.
  • the injection refrigerant that has flowed in from the outside through the injection pipe 41 is injected into the compression chamber 20 from the compression chamber communication passage 1h via the refrigerant inflow chamber 1e, the inflow chamber communication passage 1g, and the on-off valve chamber 1f. Note that the injection refrigerant is not injected into the compression chamber 20 when the injection operation is not performed.
  • the main shaft 7 is driven by the electric motor 5 and the swing scroll 2 is driven.
  • the orbiting scroll 2 does not rotate by the Oldham mechanism 8 but performs a revolving motion (eccentric turning motion) to perform a compression operation for gradually reducing the volume of the compression chamber 20.
  • a revolving motion eccentric turning motion
  • the suction refrigerant becomes high pressure and is discharged into the sealed container 10 from the discharge port 1 d of the fixed scroll 1.
  • the discharged refrigerant is discharged out of the sealed container 10 from the discharge pipe 43. That is, the inside of the sealed container 10 is at a high pressure.
  • the inside of the sealed container 10 becomes a high pressure during steady operation. Due to this pressure, the refrigerating machine oil 11 accumulated at the bottom of the sealed container 10 flows through the oil pipe 7f and the high-pressure oil supply hole 7g toward the rocking scroll 2 (upper side in FIG. 1).
  • the high-pressure refrigerating machine oil is guided to the boss portion space 15a, is reduced to an intermediate pressure Pm1 higher than the suction pressure and lower than the discharge pressure, and flows into the boss portion outer diameter space 15b.
  • the high-pressure oil flowing through the high-pressure oil supply hole 7g is guided between the main bearing 3c and the main shaft portion 7c from a lateral hole provided in the main shaft 7.
  • the refrigerating machine oil introduced between the main bearing 3c and the main shaft portion 7c is reduced between the main bearing 3c and the main shaft portion 7c to an intermediate pressure Pm1 higher than the suction pressure and lower than the discharge pressure, and the boss portion outer diameter space 15b.
  • the refrigerating machine oil that has reached the intermediate pressure Pm1 in the outer diameter space 15b of the boss part is the firing of the refrigerant that has been dissolved in the refrigerating machine oil, and generally has two phases of gas refrigerant and refrigerating machine oil.
  • the refrigerating machine oil that has become the intermediate pressure Pm1 in the boss portion outer diameter space 15b flows through the adjustment valve space 3p into the valve outer diameter space 15e.
  • the refrigerating machine oil that has flowed into the valve outer diameter space 15e is discharged to the inside of the Oldham mechanism annular portion 8c through the communication hole 3n.
  • the refrigeration oil overcomes the force applied by the intermediate pressure regulating spring 3m, pushes up the intermediate pressure regulating valve 3t, and flows into the valve outer diameter space 15e.
  • the refrigerating machine oil having an intermediate pressure Pm1 in the boss portion outer diameter space 15b is supplied to the thrust surface 2d of the orbiting scroll 2 and the sliding portion of the thrust bearing 3a of the compliant frame 3, and the Oldham mechanism annular portion 8c. It is discharged inside.
  • the refrigerating machine oil discharged inside the Oldham mechanism annular portion 8c is supplied to the sliding surface of the Oldham mechanism annular portion 8c and the sliding surfaces of the claws 8a and 8b of the Oldham mechanism 8, and then the outer diameter portion of the base plate Open to the space 15c.
  • Ps is a suction atmosphere pressure, that is, a low pressure.
  • the lower opening 2k of the bleed hole 2j communicates with an opening (upper opening 3u shown in FIG. 4) on the thrust bearing 3a side of the communication hole 3s provided in the compliant frame 3 constantly or intermittently. .
  • the refrigerant gas being compressed from the compression chamber 20 is guided to the frame space 15 d through the extraction holes 2 j of the orbiting scroll 2 and the communication holes 3 s of the compliant frame 3. Since this refrigerant gas is being compressed, it is an intermediate pressure Pm2 that is higher than the suction pressure and lower than or equal to the discharge pressure.
  • the frame space 15d is a closed space sealed by the upper seal material 16a and the lower seal material 16b, and therefore compressed in response to pressure fluctuations in the compression chamber 20 during normal operation.
  • the chamber 20 and the frame space 15d have a slight flow in both directions. That is, the compression chamber 20 and the frame space 15d are in a state of breathing.
  • Ps is a suction atmosphere pressure, that is, a low pressure.
  • the compliant frame 3 has a total of (A) the force resulting from the intermediate pressure Pm1 in the boss portion outer diameter space 15b and (B) the pressing force from the orbiting scroll 2 via the thrust bearing 3a ( A + B) acts as a downward force.
  • C + D acts as an upward force.
  • the upward force (C + D) is set to be greater than the downward force (A + B).
  • the compliant frame 3 is lifted to the fixed scroll 1 side (upper side in FIG. 1). That is, in the compliant frame 3, the upper fitting cylindrical surface 3d is guided by the upper fitting cylindrical surface 4a of the guide frame 4, and the lower fitting cylindrical surface 3e is guided by the lower fitting cylindrical surface 4b of the guide frame 4. As a result, it is lifted to the fixed scroll 1 side (upper side in FIG. 1). That is, the compliant frame 3 floats to the fixed scroll 1 side (upper side in FIG. 1) and is pressed against the orbiting scroll 2 via the thrust bearing 3a.
  • the orbiting scroll 2 Since the compliant frame 3 is pressed against the orbiting scroll 2, the orbiting scroll 2 is also lifted to the fixed scroll 1 side (upper side in FIG. 1) like the compliant frame 3. As a result, the tooth tip of the spiral tooth 2b of the swing scroll 2 and the tooth bottom (base plate portion 1a) of the fixed scroll 1 come into contact with each other, the tooth tip of the spiral tooth 1b of the fixed scroll 1 and the swing scroll 2 To the tooth bottom (base plate portion 2a).
  • FIG. 5 is a diagram illustrating an example of a circuit configuration of a heat pump apparatus having an injection circuit.
  • FIG. 6 is a Mollier diagram of the state of the refrigerant in the heat pump apparatus shown in FIG.
  • the horizontal axis represents specific enthalpy and the vertical axis represents refrigerant pressure.
  • the heating operation includes not only heating used for air conditioning, but also hot water supply that heats water to make hot water.
  • the gas-phase refrigerant (point 1 in FIG. 6) that has become high temperature and high pressure in the compressor 51 (the scroll compressor 100) is discharged from the discharge pipe 43 of the compressor 51, and is a heat exchanger 52 that is a condenser and serves as a radiator. It is liquefied by heat exchange (point 2 in FIG. 6). At this time, air or water is warmed by heat radiated from the refrigerant, and heating or hot water is supplied.
  • the liquid-phase refrigerant liquefied by the heat exchanger 52 is decompressed to an intermediate pressure by the first expansion valve 53 (decompression mechanism) and becomes a gas-liquid two-phase state (point 3 in FIG. 6).
  • the refrigerant in the gas-liquid two-phase state at the first expansion valve 53 is heat-exchanged with the refrigerant sucked into the compressor 51 by the receiver 59, cooled and liquefied (point 4 in FIG. 6).
  • the liquid phase refrigerant liquefied by the receiver 59 branches and flows to the internal heat exchanger 54, the third expansion valve 55 side (main flow), and the second expansion valve 56 side (branch flow, injection circuit).
  • the liquid-phase refrigerant flowing through the main flow is heat-exchanged by the internal heat exchanger 54 with the refrigerant flowing through the tributary that has been decompressed by the second expansion valve 56 and is in a gas-liquid two-phase state, and further cooled (point 5 in FIG. ).
  • the liquid-phase refrigerant cooled by the internal heat exchanger 54 is decompressed by the third expansion valve 55 (decompression mechanism) and becomes a gas-liquid two-phase state (point 6 in FIG. 6).
  • the refrigerant in the gas-liquid two-phase state by the third expansion valve 55 is heat-exchanged and heated by the heat exchanger 57 serving as an evaporator (point 7 in FIG. 6).
  • the refrigerant heated by the heat exchanger 57 is further heated by the receiver 59 (point 8 in FIG. 6), and is sucked into the compressor 51 from the suction pipe.
  • the refrigerant flowing through the tributary is depressurized by the second expansion valve 56 (decompression mechanism) (point 9 in FIG. 6) and heat exchanged by the internal heat exchanger 54 (point 10 in FIG. 6). ).
  • the gas-liquid two-phase refrigerant (injection refrigerant) heat-exchanged by the internal heat exchanger 54 flows into the refrigerant inflow chamber 1e of the fixed scroll 1 from the injection pipe 41 of the compressor 51 in the gas-liquid two-phase state.
  • the refrigerant (point 8 in FIG. 6) flowing through the main flow and sucked from the suction pipe 42 is compressed and heated to an intermediate pressure ( Point 11 in FIG.
  • the opening of the second expansion valve 56 is closed. That is, when the injection operation is performed, the opening of the second expansion valve 56 is larger than the predetermined opening, but when the injection operation is not performed, the opening of the second expansion valve 56 is set to a predetermined value. The opening is smaller than.
  • coolant inflow chamber 1e of the compressor 51 is interrupted
  • the opening degree of the second expansion valve 56 is controlled by electronic control, for example.
  • the four-way valve 58 is set in the direction of the broken line.
  • the gas-phase refrigerant (point 1 in FIG. 6) that has become high-temperature and high-pressure in the compressor 51 (the scroll compressor 100) is discharged from the discharge pipe 43 of the compressor 51, and is heat-exchanged by the heat exchanger 57 serving as a condenser.
  • To liquefy (point 2 in FIG. 6).
  • the liquid-phase refrigerant liquefied by the heat exchanger 57 is reduced to an intermediate pressure by the third expansion valve 55, and becomes a gas-liquid two-phase state (point 3 in FIG. 6).
  • the refrigerant that has become a gas-liquid two-phase state by the third expansion valve 55 is heat-exchanged by the internal heat exchanger 54, cooled and liquefied (point 4 in FIG. 6).
  • the refrigerant that has become a gas-liquid two-phase state by the third expansion valve 55 and the liquid-phase refrigerant that has been liquefied by the internal heat exchanger 54 are decompressed by the second expansion valve 56, and the gas-liquid two-phase Heat is exchanged with the refrigerant in the state (point 9 in FIG. 6).
  • heat-exchanged by the internal heat exchanger 54 flows in a branched manner to the receiver 59 side (main flow) and the internal heat exchanger 54 side (branch flow, injection circuit).
  • the liquid-phase refrigerant flowing through the main stream is heat-exchanged with the refrigerant sucked into the compressor 51 by the receiver 59 and further cooled (point 5 in FIG. 6).
  • the liquid-phase refrigerant cooled by the receiver 59 is decompressed by the first expansion valve 53 and becomes a gas-liquid two-phase state (point 6 in FIG. 6).
  • the refrigerant in the gas-liquid two-phase state by the first expansion valve 53 is heat-exchanged and heated by the heat exchanger 52 serving as an evaporator (point 7 in FIG. 6).
  • the refrigerant absorbs heat, thereby cooling the air, water, etc., cooling, making cold water or ice, or freezing. Then, the refrigerant heated by the heat exchanger 57 is further heated by the receiver 59 (point 8 in FIG. 6), and is sucked into the compressor 51 from the suction pipe. On the other hand, as described above, the refrigerant flowing through the tributary is decompressed by the second expansion valve 56 (point 9 in FIG. 6) and is heat-exchanged by the internal heat exchanger 54 (point 10 in FIG. 6).
  • the gas-liquid two-phase refrigerant (injection refrigerant) heat-exchanged by the internal heat exchanger 54 flows into the refrigerant inflow chamber 1e of the fixed scroll 1 from the injection pipe 41 of the compressor 51 in the gas-liquid two-phase state.
  • the compression operation in the compressor 51 is the same as in the heating operation.
  • the opening of the second expansion valve 56 is closed and the injection refrigerant flowing into the refrigerant inflow chamber 1e of the compressor 51 is shut off as in the heating operation.
  • the injection operation is usually performed in the heating operation. Therefore, normally, the injection operation is not performed during the cooling operation. In addition, even during the heating operation, the injection operation is not always performed. For example, when the outside air temperature is equal to or lower than a predetermined temperature (for example, 2 ° C.), or the rotation speed of the compressor is a predetermined frequency (for example, 60 Hz). ) In the above case, the heating capacity can be increased by performing the injection operation, and a heat pump device with good heating and hot water supply performance can be obtained. When there is no need for the injection operation, the opening of the second expansion valve 56 is closed and the injection operation is not performed even during the heating operation.
  • the criterion for determining whether or not to perform the injection operation may not be the above-described criterion.
  • the injection operation may be performed during the cooling operation.
  • the heat exchanger 52 may be a heat exchanger that performs heat exchange between a gas-phase refrigerant that has become high temperature and pressure or a liquid-phase refrigerant that has become low temperature and low pressure and a liquid such as water, It may be a heat exchanger that performs heat exchange between a gas-phase refrigerant having a high temperature and a high pressure or a liquid-phase refrigerant having a low temperature and a low pressure and a gas such as air. That is, the heat pump apparatus described in FIGS. 5 and 6 may be an air conditioner, a hot water supply apparatus, a refrigeration apparatus, or a refrigeration apparatus.
  • FIG. 7 is a view showing the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 every 90 degrees, with the suction completion state being 0 degrees.
  • a pair of compression chambers 20a, 20b is formed by the engagement of the spiral teeth 1b of the fixed scroll 1 and the spiral teeth 2b of the swing scroll 2.
  • the compression chambers 20a and 20b are collectively referred to as the compression chamber 20.
  • the compression chamber 20 moves to the center while gradually decreasing in volume as the orbiting scroll 2 rotates as the main shaft 7 rotates. That is, the refrigerant sucked into the compression chamber 20 is gradually compressed by the revolving motion of the swing scroll 2 as the main shaft 7 rotates, and moves to the center while increasing the pressure.
  • the compression chamber 20 communicates with the discharge port 1d provided in the central portion, the compressed refrigerant is discharged into the sealed container 10 from the discharge port 1d.
  • the time point of 0 degree is a state where the suction of the refrigerant is completed as described above.
  • the refrigerant is sucked into the compression chamber 20 from the suction pipe 42, and the compression chamber 20 is sealed.
  • the main shaft 7 rotates 90 degrees from the time of 0 degrees (the time when the refrigerant suction is completed)
  • the volume of the compression chamber 20 is slightly reduced and the compression chamber 20 is moved slightly closer to the center.
  • the compression chamber 20 communicates with the compression chamber communication path 1h. Therefore, if the injection operation is performed, the injection refrigerant flows from the compression chamber communication path 1h.
  • the injection refrigerant is injected into the intermediate pressure portion.
  • the main shaft 7 rotates 180 degrees, 270 degrees, and 360 degrees from the point of time when the refrigerant suction is completed.
  • the compression chamber 20 communicates with the compression chamber communication path 1h. Therefore, during this time, while the injection refrigerant flows into the compression chamber 20 from the compression chamber communication path 1h, the refrigerant in the compression chamber 20 is compressed and gradually moves toward the center.
  • the compression chamber 20 ends the communication with the compression chamber communication path 1h. Thereafter, until the compression chamber 20 communicates with the discharge port 1d, the refrigerant in the compression chamber 20 is compressed without any refrigerant flowing into the compression chamber 20 from the outside.
  • the rotation of the main shaft 7 exceeds 450 degrees from the time when the refrigerant suction is completed, the compression chamber 20 communicates with the discharge port 1d, and the compressed refrigerant is discharged into the sealed container 10 from the discharge port 1d.
  • the compression chambers 20a and 20b are configured to communicate with one compression chamber communication path 1h that communicates with different on-off valve chambers 1f. That is, as described above, the two on-off valve chambers 1 f are formed in the base plate portion 1 a of the fixed scroll 1. The one on-off valve chamber 1f of the two on-off valve chambers 1f and the compression chamber 20a communicate with each other, and the other on-off valve chamber 1f and the compression chamber 20b communicate with each other.
  • FIG. 8 is an exploded perspective view showing the configuration of the on-off valve chamber 1f.
  • the two on-off valve chambers 1f are sealed by fastening a back plate 31 with bolts 34 in two cylindrical recesses provided on the opposite side to the spiral teeth 1b of the base plate portion 1a of the fixed scroll 1. It is formed.
  • one back plate 31 that covers both openings of the two depressions is covered. Of course, you may make it cover the separate backplate 31 for every hollow.
  • the connection port with the inflow chamber communication path 1g and the connection port with the compression chamber communication path 1h are formed on the lower plane of each recess.
  • the inflow chamber communication passage 1g communicates with the refrigerant inflow chamber 1e formed from the side portion of the base plate portion 1a toward the inside. Further, the compression chamber communication passage 1h communicates with the surface on the spiral tooth 1b side. That is, the compression chamber communication path 1 h communicates with the compression chamber 20. That is, a connection port to the refrigerant inflow chamber 1e and a connection port to the compression chamber 20 are formed on the lower plane of each recess.
  • Each on-off valve chamber 1f is provided with an on-off valve 30 formed in a circular plate shape having a diameter substantially the same as or slightly smaller than the inner diameter of the recess.
  • the on-off valve 30 is formed with a passage hole 30a and a guide hole 30b.
  • the on-off valve 30 is disposed at a position where the passage hole 30a overlaps the connection port with the compression chamber communication path 1h.
  • the on-off valve 30 is arranged in the on-off valve chamber 1f by inserting a guide projection 31a (guide rod) formed on the back plate 31 into the guide hole 30b.
  • the guide protrusion 31a is a protrusion that extends in a bar shape in a direction perpendicular to the surface on which the inflow chamber communication passage 1g and the compression chamber communication passage 1h are formed (vertical direction and vertical direction in FIG. 1).
  • the guide hole 30b is formed in a keyhole shape, and the guide protrusion 31a is also formed in a key shape. Therefore, the on-off valve 30 can be moved in the on-off valve chamber 1f in the direction perpendicular to the surface direction of the fixed base plate (up and down direction in FIG. 1), but the guide hole 30b and the guide protrusion 31a mesh with each other, The guide projection 31a is not rotated about the axis.
  • the position of the passage hole 30a disposed at a position communicating with the compression chamber communication path 1h does not shift.
  • the on-off valve 30 is shifted in the horizontal direction by making the on-off valve 30 a circular shape having substantially the same diameter as the inner diameter of the recess, or by making the guide hole 30b substantially the same size and shape as the outer periphery of the guide projection 31a. There is nothing.
  • the on-off valve 30 has a circular shape having substantially the same diameter as the inner diameter of the recess, the outer periphery of the on-off valve 30 and the inner wall of the recess may be rubbed to cause burrs.
  • the opening / closing valve 30 has a circular shape with a diameter slightly smaller than the inner diameter of the recess, and that the guide hole 30b has the same shape and the same shape as the outer periphery of the guide protrusion 31a.
  • the recess is a columnar shape and the on-off valve 30 is a circular plate shape, which is easy to process and manufacture, the on-off valve 30 can be rotated by devising the shape of the guide hole 30b and the guide protrusion 31a. There was a need to prevent.
  • the depressions may be prismatic and the on / off valve 30 may be polygonal to prevent the on / off valve 30 from rotating.
  • FIG. 9 is a view showing the vicinity of one on-off valve chamber 1f when performing the injection operation.
  • the gas-liquid two-phase injection refrigerant flows from the injection pipe 41 into the refrigerant inflow chamber 1e formed in the base plate portion 1a of the fixed scroll 1.
  • the injection refrigerant that has flowed into the refrigerant inflow chamber 1e flows into the two inflow chamber communication passages 1g, respectively.
  • the pressure of the injection refrigerant flowing into the refrigerant inflow chamber 1e is higher than the pressure of the refrigerant in the compression chamber 20 (in particular, the position where the compression chamber communication passage 1h communicates in the compression chamber 20, that is, the intermediate pressure portion). high. Therefore, the injection refrigerant that has flowed into the inflow chamber communication passage 1g pushes up the on-off valve 30 provided in the on-off valve chamber 1f to the back plate 31 side (upper side in FIG. 9). As a result, the injection refrigerant that has flowed into the inflow chamber communication passage 1g flows into the on-off valve chamber 1f.
  • the compression chamber 20 communicates with the compression chamber communication passage 1h
  • the injection refrigerant in the on-off valve chamber 1f flows into the compression chamber 20 through the compression chamber communication passage 1h.
  • FIG. 10 is a view showing the vicinity of one on-off valve chamber 1f when the injection operation is not performed. As described with reference to FIGS. 5 and 4, when the injection operation is not performed, the second expansion valve 56 in the heat pump device is closed. Therefore, the injection refrigerant does not flow into the refrigerant inflow chamber 1e.
  • the pressure in the compression chamber 20 (in particular, the position where the compression chamber communication passage 1h communicates in the compression chamber 20, that is, the intermediate pressure portion) is higher than the refrigerant pressure from the refrigerant inflow chamber 1e to the on-off valve chamber 1f,
  • the refrigerant in the compression chamber 20 flows backward to the on-off valve chamber 1f via the compression chamber communication passage 1h.
  • the refrigerant that has flowed into the on-off valve chamber 1 f flows into the on-off valve chamber 1 f through the passage hole 30 a of the on-off valve 30.
  • the refrigerant that has flowed from the compression chamber 20 into the on-off valve chamber 1f passes the on-off valve 30 to the inflow chamber communication passage 1g side (lower side of FIG. 10). To the side).
  • the inflow chamber communication passage 1g is closed by the on-off valve 30. Therefore, the refrigerant that has flowed into the on-off valve chamber 1f does not flow out from the inflow chamber communication passage 1g to the refrigerant inflow chamber 1e.
  • the on-off valve 30 is pushed up to the back plate 31 side, The on-off valve 30 is in an open state. Then, the injection refrigerant flows into the on-off valve chamber 1f from the inflow chamber communication passage 1g, and flows into the compression chamber 20 through the compression chamber communication passage 1h.
  • the on-off valve 30 opens and closes due to a pressure difference between the refrigerant pressure on the refrigerant inflow chamber 1e side (inflow chamber communication path 1g) and the refrigerant pressure in the compression chamber 20 (compression chamber communication path 1h).
  • the refrigerant in the compression chamber 20 can be prevented from flowing back to the injection circuit. If the on-off valve 30 is not provided, the refrigerant in the compression chamber 20 flows back to the injection circuit, and the volume from the compression chamber communication path 1h to the second expansion valve 56 becomes a dead volume in compression. The efficiency is greatly reduced. That is, the dead volume can be significantly reduced by using the on-off valve 30, and the compression efficiency can be increased.
  • the on / off valve 30 prevents the refrigerant from flowing out to the injection circuit.
  • the pressure in the refrigerant inflow chamber 1e gradually decreases.
  • the on-off valve 30 pushed up to the back plate 31 side (the upper side of FIGS. 9 and 10) It goes down to the communication passage 1g side (the lower side of FIGS. 9 and 10).
  • the on / off valve 30 When the pressure in the compression chamber 20 becomes higher than the pressure in the refrigerant inflow chamber 1e, the on / off valve 30 is connected to the inflow chamber communication path by the refrigerant that has passed from the compression chamber 20 through the passage hole 30a and flowed into the on-off valve chamber 1f. It is pressed to the 1g side (the lower side of FIGS. 9 and 10). That is, the on-off valve 30 operates only by the pressure difference and gravity, and operates without using any spring force such as a coil spring. Therefore, it is very reliable and can be manufactured at low cost.
  • connection port with the inflow chamber communication passage 1g and a connection port with the compression chamber communication passage 1h are formed on the lower surface of the on-off valve chamber 1f. Therefore, as described above, when shifting from the state where the injection operation is performed to the state where the injection operation is not performed, in addition to the pressure difference, the on-off valve 30 is moved by the gravity to the inflow chamber communication passage 1g side (lower side of FIGS. Side).
  • a connection port with the inflow chamber communication passage 1g and a connection port with the compression chamber communication passage 1h may be provided on the side surface or the upper surface of the on-off valve chamber 1f.
  • the on-off valve 30 moves only by the pressure difference, but the movement of the on-off valve 30 may be supported by a coil spring or the like. That is, when the pressure in the compression chamber 20 and the pressure in the refrigerant inflow chamber 1e are approximately the same pressure by a coil spring or the like, the on-off valve 30 is pressed against the inflow chamber communication passage 1g, thereby allowing the injection operation. When switching from the state of performing the operation to the state of not performing the injection operation, the on-off valve 30 may be easily moved to the inflow chamber communication path 1g side.
  • connection port to the inflow chamber communication passage 1g and the connection port to the compression chamber communication passage 1h are formed on the lower surface of the on-off valve chamber 1f, a coil spring is provided between the on-off valve 30 and the back plate 31. Etc. may be provided to support the operation in which the on-off valve 30 is lowered toward the inflow chamber communication passage 1g (the lower side in FIGS. 9 and 10).
  • the inflow chamber communication passage 1g communicating with the refrigerant inflow chamber 1e and the compression chamber communication passage 1h communicating with the compression chamber 20 are provided on the same surface in the on-off valve chamber 1f. Therefore, the on-off valve 30 can have a simple configuration.
  • the fixed scroll 1, the orbiting scroll 2 and the like are formed in the shape described above.
  • the spiral tooth 1b, the base plate portion 1a of the fixed scroll 1 a hole serving as the refrigerant inflow chamber 1e, two depressions, a hole serving as the inflow chamber communication passage 1g, and the compression chamber communication. Machining to form a hole to become the passage 1h is performed, the opening / closing valve 30 is disposed in the formed depression, and the back plate 31 is attached.
  • a hole serving as the refrigerant inflow chamber 1e, two depressions, a hole serving as the inflow chamber communication passage 1g, and a hole serving as the compression chamber communication passage 1h are all straight on the base plate portion 1a of the fixed scroll 1. It can be formed by performing a general cutting process. What is the order of machining to form the spiral tooth 1b, the hole serving as the refrigerant inflow chamber 1e, the two depressions, the hole serving as the inflow chamber communication passage 1g, and the hole serving as the compression chamber communication passage 1h. May be in any order. Next, as shown in FIG.
  • the sub-frame 6, the electric motor 5, the main shaft 7, the guide frame 4, the compliant frame 3, and the Oldham mechanism 8 are disposed in the lower container 10 a of the sealed container 10, and the swing scroll 2 is arranged to engage with the main shaft 7. Further, the fixed scroll 1 is arranged so that the compression chamber 20 is formed between the swing scroll 2.
  • the injection pipe 41 is attached to the lower container 10a so as to be connected to the refrigerant inflow chamber 1e
  • the suction pipe 42 is attached to the lower container 10a so as to be connected to the suction port of the compression chamber 20, and the discharge pipe 43 is attached.
  • the upper container 10b is attached to the lower container 10a and sealed. Thereby, the scroll compressor 100 is manufactured.
  • the scroll compressor 100 it is possible to prevent backflow of refrigerant in the middle of compression to the injection circuit and increase in dead volume in the compression process.
  • the connection port of the inflow chamber communication path 1g and the compression chamber communication path 1h to the on-off valve chamber 1f is provided on the same surface of the on-off valve chamber 1f, and the on-off valve 30 is connected to the inflow chamber communication path. It opens and closes by the pressure difference between the pressure on the 1g side and the pressure on the compression chamber communication path 1h side. Therefore, the on-off valve 30 can move smoothly to open and close, and the reliability can be improved.
  • the on-off valve chamber 1f can be formed compactly.
  • the opening / closing can be controlled by the pressure difference between the pressure in the compression chamber 20 and the pressure in the refrigerant inflow chamber 1e without using a coil spring.
  • the number of parts can be reduced.
  • a refrigerant inflow chamber 1e, two depressions, an inflow chamber communication passage 1g, and a compression chamber communication passage 1h are formed in a straight line with respect to the base plate portion 1a of the fixed scroll 1, and are opened and closed.
  • the valve 30 is installed and the back plate 31 is covered with a back plate 31 to form an on-off valve chamber 1f. That is, in the scroll compressor 100, a straight hole is simply opened and the on-off valve 30 and the back plate 31 are installed. Therefore, for example, complicated processing such as providing a groove for the refrigerant flow path in the valve seat portion of the on-off valve is unnecessary. Therefore, the number of processing steps can be reduced.
  • a refrigerant inflow chamber 1 e is provided from the side of the base plate portion 1 a of the fixed scroll 1 toward the inside. Therefore, since the injection pipe 41 may be attached to the side portion of the base plate portion 1a of the fixed scroll 1, the injection pipe 41 can be attached to the lower container 10a. That is, it is not necessary to attach the injection pipe 41 to the upper container 10b. Therefore, the work of attaching the upper container 10b to the lower container 10a is very easy. Further, since the injection pipe 41 may be attached to the side portion of the base plate portion 1 a of the fixed scroll 1, the injection pipe 41 is provided on the side portion of the sealed container 10.
  • the pipe connected to the injection pipe 41 may be disposed on the side portion of the sealed container 10 and does not need to be disposed on the upper side of the sealed container 10.
  • the scroll compressor 100 can save the space above the sealed container 10 compared to the compressor that requires the piping connected to the injection pipe 41 to be disposed above the sealed container 10, and the heat pump device can be made compact. Can be realized.
  • FIG. 1 a scroll compressor 100 using an on-off valve 32 constituted by a leaf spring will be described.
  • FIG. 11 is a longitudinal sectional view of the scroll compressor 100 according to the second embodiment.
  • the scroll compressor 100 according to Embodiment 2 shown in FIG. 11 is different from the scroll compressor 100 according to Embodiment 1 shown in FIG.
  • the on-off valve 32 configured by a leaf spring is used.
  • the on-off valve 32 is provided so as to cover the inflow chamber communication passage 1g.
  • the injection refrigerant flows into the on-off valve chamber 1f from the inflow chamber communication passage 1g, and flows into the compression chamber 20 through the compression chamber communication passage 1h.
  • the on-off valve 32 is pressed toward the inflow chamber communication passage 1g. Therefore, the refrigerant that flows backward from the compression chamber 20 and flows into the on-off valve chamber 1f does not flow out from the inflow chamber communication passage 1g to the refrigerant inflow chamber 1e.
  • the back plate 33 can have a simple configuration.
  • the scroll compressor 100 according to the second embodiment using the on-off valve 32 configured by a leaf spring can obtain the same effects as those of the scroll compressor 100 according to the first embodiment. it can.
  • the scroll compressor according to the above embodiment is The fixed scroll and the orbiting scroll are meshed with each other in the sealed container, and the orbiting scroll is revolved without rotating with respect to the fixed scroll, thereby being compressed in the compression chamber formed by the plate-like spiral teeth of both scrolls.
  • Refrigerant is discharged from the discharge port provided at the center of the fixed scroll to the discharge space on the back surface of the fixed scroll, and the refrigerant has an intermediate pressure between the pressure of the refrigerant flowing into the compression chamber and the pressure of the refrigerant discharged from the compression chamber.
  • an on-off valve chamber that houses two on-off valves and two on-off valves in the middle of the refrigerant inflow chamber that passes through the inside from the side of the fixed scroll and flows into the compression chamber through the compression chamber communication passage. And having one back plate.
  • the scroll compressor 100 has been described as an example of an injection-compatible compressor.
  • the injection-compatible compressor is not limited to this, and may be another compressor as long as it is a compressor having an injection mechanism such as a rotary compressor.
  • the example in which the refrigerant inflow chamber 1e, the on-off valve chamber 1f, and the like are provided in the base plate portion 1a of the fixed scroll 1 in the scroll compressor 100 has been described.
  • the present invention is not limited to this, and a refrigerant inflow chamber 1e, an on-off valve chamber 1f, and the like may be provided separately from the base plate portion 1a of the fixed scroll 1.

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Abstract

Un fluide frigorigène comprimé ne peut pas circuler vers un circuit d'injection. Compresseur comprenant des sections de compression (1, 2) destinées à former une chambre de compression (20) et à comprimer un fluide frigorigène aspiré à une pression de décharge, le fluide frigorigène aspiré présentant une pression d'aspiration aspirée dans la chambre de compression (20) et le compresseur comprend également une section de versement du fluide frigorigène destinée à verser, dans la chambre de compression (20), un fluide frigorigène d'injection dans une section à pression intermédiaire dans laquelle le fluide frigorigène aspiré présente une pression intermédiaire supérieure à la pression d'aspiration et inférieure à la pression de décharge. La section de versement de fluide frigorigène comprend une chambre d'entrée de fluide frigorigène (1e) dans laquelle le fluide frigorigène d'injection circule depuis le circuit d'injection à travers un conduit d'injection (41), et comprend également une chambre à clapet d'ouverture/fermeture (1f) reliée à la chambre d'entrée de fluide frigorigène (1e) et à la section de pression intermédiaire de la chambre de compression (20), la chambre à clapet d'ouverture/fermeture (1f) présentant à la fois un orifice relié à la chambre d'entrée de fluide frigorigène (1e) et un orifice relié à la section de pression intermédiaire, les orifices étant formés dans le même plan dans la chambre à clapet d'ouverture/fermeture (1f), la chambre à clapet d'ouverture/fermeture (1f) présentant également un clapet d'ouverture/fermeture (30) qui, au moyen d'une différence de pression entre le fluide frigorigène sur le côté de la chambre d'entrée de fluide frigorigène (1e) et le fluide frigorigène sur le côté de la section de pression intermédiaire, ouvre et ferme l'orifice relié à la chambre d'entrée de fluide frigorigène (1e).
PCT/JP2009/063412 2009-07-28 2009-07-28 Dispositif de pompe à chaleur, compresseur avec mécanisme d'injection et procédé de fabrication d'un compresseur à spirale avec mécanisme d'injection WO2011013199A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP09847791.2A EP2461122B1 (fr) 2009-07-28 2009-07-28 Dispositif de pompe à chaleur, compresseur avec mécanisme d'injection et procédé de fabrication d'un compresseur à spirale avec mécanisme d'injection
KR1020117031134A KR101312762B1 (ko) 2009-07-28 2009-07-28 히트 펌프 장치, 인젝션 대응 압축기 및 인젝션 대응 스크롤 압축기의 제조 방법
CN200980160586.5A CN102472528B (zh) 2009-07-28 2009-07-28 热泵装置、喷射对应压缩机及喷射对应涡旋压缩机的制造方法
JP2011524561A JP5389173B2 (ja) 2009-07-28 2009-07-28 ヒートポンプ装置、インジェクション対応圧縮機及びインジェクション対応スクロール圧縮機の製造方法
PCT/JP2009/063412 WO2011013199A1 (fr) 2009-07-28 2009-07-28 Dispositif de pompe à chaleur, compresseur avec mécanisme d'injection et procédé de fabrication d'un compresseur à spirale avec mécanisme d'injection

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JP2012172581A (ja) * 2011-02-21 2012-09-10 Mitsubishi Electric Corp スクロール圧縮機及びヒートポンプ装置
JP2012184873A (ja) * 2011-03-04 2012-09-27 Mitsubishi Electric Corp 冷凍装置
JP2016011620A (ja) * 2014-06-27 2016-01-21 三菱電機株式会社 スクロール圧縮機
CZ305898B6 (cs) * 2012-06-11 2016-04-27 Mitsubishi Electric Corporation Šnekový kompresor
WO2017130401A1 (fr) * 2016-01-29 2017-08-03 三菱電機株式会社 Compresseur à volutes et dispositif du type pompe à chaleur
WO2017141342A1 (fr) * 2016-02-16 2017-08-24 三菱電機株式会社 Compresseur à volute
WO2019069441A1 (fr) * 2017-10-06 2019-04-11 三菱電機株式会社 Dispositif à cycle frigorifique
WO2021157121A1 (fr) * 2020-02-03 2021-08-12 パナソニックＩｐマネジメント株式会社 Compresseur doté d'un mécanisme d'injection
WO2022038730A1 (fr) * 2020-08-20 2022-02-24 三菱電機株式会社 Compresseur à spirale
JP2022536398A (ja) * 2019-07-24 2022-08-15 ハンオン システムズ スクロール圧縮機

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CN102953992A (zh) * 2012-11-27 2013-03-06 大连三洋压缩机有限公司 具有喷射通道的涡旋式压缩机
CN105952638A (zh) * 2016-06-21 2016-09-21 广东美的暖通设备有限公司 涡旋压缩机和空调器
CN106122010A (zh) * 2016-08-22 2016-11-16 广东美的暖通设备有限公司 涡旋压缩机和制冷设备
EP3546756B1 (fr) * 2016-11-24 2022-01-19 Panasonic Intellectual Property Management Co., Ltd. Compresseur à spirales ayant une fonction d'injection
DE102016125400A1 (de) * 2016-12-22 2018-06-28 OET GmbH Verfahren zur Herstellung eines Scrollkompressors
CN111656017B (zh) * 2018-01-30 2021-12-28 三菱电机株式会社 涡旋式压缩机
CN111852852A (zh) * 2019-04-26 2020-10-30 艾默生环境优化技术(苏州)有限公司 一种涡旋压缩机
CN114072580B (zh) * 2019-07-16 2023-06-23 三菱电机株式会社 涡旋压缩机
KR20210012292A (ko) 2019-07-24 2021-02-03 한온시스템 주식회사 스크롤 압축기
EP3812589B1 (fr) * 2019-10-21 2023-07-19 Emerson Climate Technologies GmbH Refroidissement de compresseur avec fluide d'aspiration
US11982277B2 (en) * 2020-03-23 2024-05-14 Hanon Systems Scroll compressor

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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012172581A (ja) * 2011-02-21 2012-09-10 Mitsubishi Electric Corp スクロール圧縮機及びヒートポンプ装置
JP2012184873A (ja) * 2011-03-04 2012-09-27 Mitsubishi Electric Corp 冷凍装置
CZ305898B6 (cs) * 2012-06-11 2016-04-27 Mitsubishi Electric Corporation Šnekový kompresor
JP2016011620A (ja) * 2014-06-27 2016-01-21 三菱電機株式会社 スクロール圧縮機
WO2017130401A1 (fr) * 2016-01-29 2017-08-03 三菱電機株式会社 Compresseur à volutes et dispositif du type pompe à chaleur
JPWO2017130401A1 (ja) * 2016-01-29 2018-08-23 三菱電機株式会社 スクロール圧縮機およびヒートポンプ装置
WO2017141342A1 (fr) * 2016-02-16 2017-08-24 三菱電機株式会社 Compresseur à volute
JPWO2017141342A1 (ja) * 2016-02-16 2018-09-13 三菱電機株式会社 スクロール圧縮機
WO2019069441A1 (fr) * 2017-10-06 2019-04-11 三菱電機株式会社 Dispositif à cycle frigorifique
JPWO2019069441A1 (ja) * 2017-10-06 2020-04-02 三菱電機株式会社 冷凍サイクル装置
JP2022536398A (ja) * 2019-07-24 2022-08-15 ハンオン システムズ スクロール圧縮機
JP7425811B2 (ja) 2019-07-24 2024-01-31 ハンオン システムズ スクロール圧縮機
US11971030B2 (en) 2019-07-24 2024-04-30 Hanon Systems Scroll compressor
WO2021157121A1 (fr) * 2020-02-03 2021-08-12 パナソニックＩｐマネジメント株式会社 Compresseur doté d'un mécanisme d'injection
JP7398642B2 (ja) 2020-02-03 2023-12-15 パナソニックＩｐマネジメント株式会社 インジェクション機構付き圧縮機
WO2022038730A1 (fr) * 2020-08-20 2022-02-24 三菱電機株式会社 Compresseur à spirale
JPWO2022038730A1 (fr) * 2020-08-20 2022-02-24
JP7305055B2 (ja) 2020-08-20 2023-07-07 三菱電機株式会社 スクロール圧縮機

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EP2461122A4 (fr) 2016-04-13
CN102472528B (zh) 2014-07-02
JP5389173B2 (ja) 2014-01-15
EP2461122A1 (fr) 2012-06-06
CN102472528A (zh) 2012-05-23
JPWO2011013199A1 (ja) 2013-01-07
EP2461122B1 (fr) 2018-12-19
KR20120024858A (ko) 2012-03-14
KR101312762B1 (ko) 2013-09-27

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