US20170089341A1 - Scroll compressor and method of manufacturing the same - Google Patents

Scroll compressor and method of manufacturing the same Download PDF

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Publication number
US20170089341A1
US20170089341A1 US15/311,868 US201415311868A US2017089341A1 US 20170089341 A1 US20170089341 A1 US 20170089341A1 US 201415311868 A US201415311868 A US 201415311868A US 2017089341 A1 US2017089341 A1 US 2017089341A1
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Prior art keywords
balancer
density part
density
low
scroll compressor
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Abandoned
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US15/311,868
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English (en)
Inventor
Yuji Takamura
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TAKAMURA, YUJI
Publication of US20170089341A1 publication Critical patent/US20170089341A1/en
Abandoned legal-status Critical Current

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    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085—Prime movers
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/603—Centering; Aligning
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump

Definitions

  • the present invention relates to a scroll compressor and a method of manufacturing the same, and particularly relates to the structure of a balancer.
  • balancers or more have been attached to a main shaft of a scroll compressor to compensate centrifugal force of an eccentrically orbiting spiral of oscillatory movement.
  • Each balancer has, for example, a semi-circular shape or a fan shape in plan view to achieve eccentricity of a barycenter.
  • rotation of the balancer agitates surrounding fluid, causing the following problems.
  • balancer When the balancer is arranged below a main bearing, oil dropped from the main bearing is scattered in the form of mist by rotation of the balancer and is moved to the compressor together with refrigerant, resulting in an increase of oil loss.
  • the balancer When the balancer is arranged in a frame above the main bearing, the balancer rotates in a space filled with oil, which leads to power loss due to agitation of the oil.
  • a scroll compressor in which the agitation of fluid by the balancer is prevented (for example, refer to Patent Literature 1).
  • the balancer has an outline in a cylinder shape that is circular in plan view, and a hollow space is provided in the balancer to secure centrifugal force necessary for balancing with the centrifugal force of the orbiting spiral, and prevent agitation of surrounding fluid.
  • Patent Literature 1 Japanese Patent Laid-open No. 2002-031070 (for example, refer to [0016] and FIG. 2)
  • Patent Literature 1 the hollow space is provided inside each balancer to achieve the eccentricity of its barycenter, and thus, when the balancer is disposed in a space filled with oil, the oil flows into the hollow space. This leads to a difference in the centrifugal force generated to the balancer from a designed value, causing a problem of increasing vibration.
  • the present invention is intended to solve the above-described problems, and it is an object of the present invention to provide a scroll compressor capable of preventing agitation of fluid and an increase in vibration, and a method of manufacturing the same.
  • a scroll compressor includes a fixed scroll including a spiral unit, an orbiting scroll including a spiral unit and combined with the spiral unit of the fixed scroll to form a compression chamber for compressing refrigerant, a main shaft for transmitting drive power to the orbiting scroll, an electric motor unit configured to rotate the main shaft, and a first balancer for compensating unbalance of the orbiting scroll with respect to a rotation center of the main shaft.
  • the first balancer has an outline in a cylinder shape, and includes a high-density part made of a high-density material, and a low-density part made of a low-density material having a density lower than a density of the high-density material,
  • a balancer has an outline in a cylinder shape, which can prevent agitation of surrounding fluid when the balancer rotates. Moreover, no hollow space for eccentricity of a barycenter is provided inside the balancer, causing no difference in centrifugal force generated to the balancer from a designed value, and preventing an increase in vibration.
  • FIG. 1 is a vertical sectional view of a scroll compressor according to Embodiment 1 of the present invention.
  • FIGS. 2( a ) and 2( b ) are each a diagram illustrating a low-density part of a first balancer of the scroll compressor according to Embodiment 1 of the present invention.
  • FIGS. 3( a ) and 3( b ) are each a diagram illustrating a method of assembling the first balancer of the scroll compressor according to Embodiment 1 of the present invention.
  • FIG. 4 is an enlarged view of the vicinity of a balancer-attached slider ASSY of a scroll compressor according to Embodiment 2 of the present invention.
  • FIGS. 5( a ) and 5( b ) are each a diagram illustrating the balancer-attached slider ASSY of the scroll compressor according to Embodiment 2 of the present invention.
  • FIG. 6 is a diagram illustrating prevention of turnover of the balancer-attached slider ASSY of the scroll compressor according to Embodiment 2 of the present invention.
  • FIG. 7 is a vertical sectional view of a scroll compressor according to Embodiment 3 of the present invention.
  • FIGS. 8( a ) and 8( b ) are each a diagram illustrating a method of attaching, to a rotor, a second balancer of the scroll compressor according to Embodiment 3 of the present invention.
  • FIG. 9 is an enlarged view of the vicinity of the second balancer of the scroll compressor according to Embodiment 3 of the present invention.
  • FIG. 10 is a vertical sectional view of a scroll compressor according to Embodiment 4 of the present invention.
  • FIG. 1 is a vertical sectional view of the scroll compressor 100 according to Embodiment 1 of the present invention.
  • the scroll compressor 100 is configured to suck and compress refrigerant circulating in a refrigeration cycle, and discharge the refrigerant at high temperature and high pressure.
  • the scroll compressor 100 includes a compression mechanism unit and an electric motor unit in a shell, where the compression mechanism unit is arranged on an upper side, and the electric motor unit is arranged on a lower side.
  • the shell is a pressure resisting container including a middle shell 25 having a cylinder shape, a lower shell 26 sealed to an opening on a lower surface of the middle shell 25 by, for example, welding, and an upper shell 24 sealed to an upper surface opening of the middle shell 25 by, for example, welding.
  • the middle shell 25 is connected with a suction pipe 7 formed as part of a refrigerant circuit and configured to suck the refrigerant into the shell, and includes a frame 6 fixed to an inner periphery of an upper end part, and a stator 11 fixed to an inner periphery of a middle part.
  • a bottom part of the lower shell 26 serves as an oil reservoir 18 that accumulates therein oil for lubricating each bearing.
  • a bottom surface of the frame 6 is connected with an oil discharge pipe 8 for returning oil accumulated in the frame 6 to the oil reservoir 18 .
  • the upper shell 24 is connected with a discharge pipe 1 for discharging compressed refrigerant from the shell to the refrigerant circuit.
  • the compression mechanism unit includes at least a fixed scroll 4 provided with a spiral unit 4 a on one of its surfaces, an orbiting scroll 5 provided with, on one of its surfaces, a spiral unit 5 a having a spiral direction opposite to that of the fixed scroll 4 , an orbiting bearing 21 provided opposite to a compression chamber with reference to the orbiting scroll 5 and supported to orbit freely by an eccentric slider shaft portion 14 a , the frame 6 to which the fixed scroll 4 is fixed and that is provided with a main bearing 19 in a central part, and a main shaft 14 through which a rotor 12 adhered to an outer periphery transmits drive power to the orbiting scroll 5 .
  • the compression mechanism unit is coupled with the electric motor unit and configured to compress the refrigerant.
  • the eccentric slider shaft portion 14 a is a slider mounting shaft installed on an upper part of the main shaft 14 to achieve eccentricity of a slider 22 with respect to the main shaft 14 .
  • the spiral units 4 a and 5 a are combined with each other to form a plurality of compression chambers (not illustrated) between the fixed scroll 4 and the orbiting scroll 5 .
  • a plurality of compression chambers (not illustrated) between the fixed scroll 4 and the orbiting scroll 5 .
  • sealing (not illustrated) is provided to the apical surface of the spiral unit 4 a of the fixed scroll 4 and the apical surface of the spiral unit 5 a of the orbiting scroll 5 .
  • a discharge port 28 for discharging refrigerant gas compressed to high pressure is formed in a central part of the fixed scroll 4 .
  • the refrigerant gas compressed to high pressure is ejected into a high pressure part (not illustrated) in the upper shell 24 .
  • the refrigerant gas ejected into the high pressure part is discharged into the refrigeration cycle through the discharge pipe 1 .
  • the discharge port 28 is provided with a discharge valve 29 for preventing backflow of refrigerant from the high pressure part to the discharge port 28 .
  • the electric motor unit includes the rotor 12 fixed to the main shaft 14 and the stator 11 fixed to the middle shell 25 .
  • the electric motor unit is configured to be driven at start of power supply to the stator 11 and rotate the main shaft 14 , causing the orbiting scroll 5 to perform orbiting movement through the main shaft 14 .
  • the scroll compressor 100 includes a thrust plate 30 as a thrust bearing that supports the orbiting scroll 5 in an axial center direction, an Oldham's coupling 23 supported to orbit freely by the frame 6 to prevent spin of the orbiting scroll 5 and provide orbiting movement, the slider 22 that supports the orbiting scroll 5 to allow the orbiting scroll 5 to orbit, a sleeve 20 provided near the eccentric slider shaft portion 143 to smoothly rotate the main bearing 19 of the frame 6 and the main shaft 14 , and a first balancer 27 and a second balancer 13 for compensating unbalance of the orbiting scroll 5 performing orbiting movement through the eccentric slider shaft portion 14 a , with respect to a rotation center of the main shaft 14 .
  • the first balancer 27 is provided above the electric motor unit, whereas the second balancer 13 is provided below the electric motor unit.
  • the main shaft 14 rotates with rotation of the rotor 12 to cause the orbiting scroll 5 to orbit.
  • the upper part of the main shaft 14 is supported by the main bearing 19 formed in the frame 6 .
  • a lower part of the main shaft 14 is rotatably supported by a sub bearing 16 formed in a central part of a sub frame 15 provided to a lower part of the shell.
  • the sub bearing 16 has its outer ring fitted by pressing in a bearing housing part formed in the central part of the sub frame 15 .
  • the sub frame 15 is provided with a displacement oil pump 17 configured to pump oil from the oil reservoir 18 in the bottom part of the shell and supply the oil to each sliding unit, and a pump shaft portion 14 b for transmitting rotational force to the oil pump 17 is integrally formed the main shaft 14 .
  • the main shaft 14 includes inside a vertical lubricating hole 14 c that penetrates from a lower end of the pump shaft portion 14 b to an upper end of the eccentric slider shaft portion 14 a in the vertical direction (axial direction) and supplies oil o bearings and sliding units of the compression mechanism unit.
  • the first balancer 27 includes a high-density part 10 and a low-density part 9 having a density lower than that of the high-density part 10 , and is formed by attaching the high-density part 10 to the low-density part 9 .
  • the first balancer 27 has an outline in a cylinder shape not to agitate surrounding fluid when rotating.
  • the high-density part 10 is made of a high-density material such as metal
  • the low-density part 9 is made of a low-density material such as resin material.
  • the first balancer 27 has a barycenter that is eccentric toward the high-density part 10 , and is capable of generating centrifugal force necessary as a balancer.
  • the first balancer 27 is substantially solid inside and has an extremely small hollow space to prevent generation of a difference in centrifugal force due to oil flowed into the first balancer 27 .
  • the following describes an operation of the scroll compressor 100 .
  • the rotor 12 when the stator 11 is supplied with power, the rotor 12 is rotated by rotational force from a rotating magnetic field generated by the stator 11 , and the main shaft 14 is rotated by the rotation of the rotor 12 .
  • the eccentric slider shaft portion 14 a is rotated in the orbiting bearing 21 through the slider 22 , transmitting drive power to the orbiting scroll 5 .
  • the orbiting scroll 5 performs orbiting movement while being prevented from spinning by the Oldham's coupling 23 reciprocating inside an Oldham groove (not illustrated) of the orbiting scroll 5 housing a key part (not illustrated) formed on one of surfaces of the Oldham's coupling 23 , and an Oldham groove (not illustrated) of the frame 6 housing a key part (not illustrated) formed on the other surface of the Oldham's coupling 23 .
  • the frame 6 and the sub frame 15 are fixed inside the shell, and thus an accuracy variation of the fixation and an accuracy variation in an individual component lead to an axial center difference between the main bearing 19 and the sub bearing 16 . Because of these accuracy variations as well as deflection of the main shaft 14 , the main bearing 19 and the main shaft 14 , and the sub bearing 16 and the main shaft 14 are not always parallel to each other.
  • the sleeve 20 is housed between the main shaft 14 and the main bearing 19 .
  • the main shaft 14 is tilted to the main bearing 19 , but this tilt of the main shaft 14 is canceled by a pivot part (not illustrated) of the main shaft 14 in contact with an inner periphery of the sleeve 20 . Accordingly, an outer periphery of the sleeve 20 is always slidable in parallel with the main bearing 19 .
  • Centrifugal force is generated to the orbiting scroll 5 by its orbiting movement, causing the eccentric slider shaft portion 14 a of the main shaft 14 to slide within a slidable range of a sliding surface (not illustrated) of the slider 22 . Then, the spiral unit 5 a of the orbiting scroll 5 and the spiral unit 4 a of the fixed scroll 4 become in contact with each other to form a compression chamber.
  • the centrifugal force of the orbiting scroll 5 and a load in the radial direction generated to compress refrigerant act on the eccentric slider shaft portion 14 a of the main shaft 14 , and accordingly, in some cases, the eccentric slider shaft portion 14 a becomes deflected to be not parallel to an inner surface of the orbiting bearing 21 provided in a central part of a lower surface of the orbiting scroll 5 .
  • the slider 22 is housed between the eccentric slider shaft portion 14 a of the main shaft 14 and the orbiting bearing 21 .
  • the tilt of the eccentric slider shaft portion 14 a of the main shaft 14 with respect to the orbiting bearing 21 which is caused by the deflection of the eccentric slider shaft portion 14 a , is canceled by a pivot part (not illustrated) of the eccentric slider shaft portion 14 a in contact with the sliding surface of the slider 22 .
  • an outer periphery of the slider 22 is always slidable in parallel with the orbiting bearing 21 .
  • the refrigerant in the refrigerant circuit is sucked into the shell through the suction pipe 7 , and flows, through a suction port (not illustrated) of the frame 6 , into the compression chamber formed by the spiral unit 5 a of the orbiting scroll 5 and the spiral unit 4 a of the fixed scroll 4 .
  • the compression chamber is moved toward the center of the orbiting scroll 5 by the orbiting movement of the orbiting scroll 5 , and the refrigerant is thereby reduced in volume to be compressed.
  • the compressed refrigerant applies a load to separate the fixed scroll 4 and the orbiting scroll 5 from each other, but this load on the orbiting scroll 5 is supported by a bearing formed by the orbiting bearing 21 and the thrust plate 30 .
  • the compressed refrigerant passes through the discharge port 28 of the fixed scroll 4 , pushes to open the discharge valve 29 , and passes through the high pressure part in the upper shell 24 , before being discharged from the shell to the refrigerant circuit through the discharge pipe 1 .
  • the oil pump 17 is driven by the pump shaft portion 14 b of the main shaft 14 in rotation to pump oil from the oil reservoir 18 at the bottom part of the shell through the vertical lubricating hole 14 c.
  • the pumped oil is supplied to the main bearing 19 , the sub bearing 16 , and the orbiting bearing 21 .
  • the oil lubricates the main bearing 19 and the sub bearing 16 and drops down back to the oil reservoir 18 at the bottom of the shell.
  • Oil having lubricated the orbiting bearing 21 is stored in a space 6 a in the frame.
  • the oil in the space 6 a in the frame is supplied to the thrust bearing, the Oldham's coupling 23 , the spiral units 4 a and 5 a , and the main bearing 19 , and also used to, for example, cool the orbiting bearing 21 and the main bearing 19 .
  • the space 6 a in the frame is provided with the oil discharge pipe 8 , through which excessive oil is returned to the oil reservoir 18 at the bottom part of the shell from the space 6 a in the frame.
  • FIGS. 2( a ) and 2( b ) are each a diagram illustrating the low-density part 9 of the first balancer 27 of the scroll compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 2( a ) is a plan view of the low-density part 9 of the first balancer 27
  • FIG. 2( b ) is a sectional view taken along line A-A in FIG. 2( a ) .
  • the low-density part 9 of the first balancer 27 includes a low-density main part 9 c and a cover part 9 d , and is provided with a shaft hole 9 a through which the main shaft 14 is provided, a high-density part housing hole 9 b for housing the high-density part 10 , and a low-density part fastening hole 9 e for fastening with the high-density part 10 .
  • the low-density part 9 has an outline in a cylinder shape with hollowed parts corresponding to the shaft hole 9 a , the high-density part housing hole 9 b , and the low-density part fastening hole 9 e.
  • FIGS. 3( a ) and 3( b ) are each a diagram illustrating a method of assembling the first balancer 27 of the scroll compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 3( a ) illustrates the first balancer 27 before assembly
  • FIG. 3( b ) illustrates the first balancer 27 after assembly.
  • a high-density part fastening hole 10 a for fastening with the low-density part 9 is formed in the high-density part 10 of the first balancer 27 , and the high-density part 10 is fitted into the high-density part housing hole 9 b of the low-density part 9 while positions of the high-density part fastening hole 10 a and the low-density part fastening hole 9 e of the low-density part 9 are aligned.
  • the low-density part 9 and the high-density part 10 are fastened to the low-density part fastening hole 9 e and the high-density part fastening hole 10 a through a first fastening member 2 such as a bolt or a rivet.
  • the high-density part 10 is supported by the low-density part 9 through frictional force between the cover part 9 d of the low-density part 9 and a fastening surface of the high-density part 10 , and thus, centrifugal force generated by the first balancer 27 in rotation prevents shifting of the low-density part 9 and the high-density part 10 from each other. This can prevent oil from flowing into the first balancer 27 , thereby preventing a difference in centrifugal force.
  • the first balancer 27 has an outline in a cylinder shape, and thus can prevent agitation of surrounding fluid when rotating.
  • the first balancer 27 includes the low-density part 9 and the high-density part 10 , and thus has a barycenter that is eccentric toward the high-density part 10 , thereby generating centrifugal force necessary as a balancer.
  • the configuration of the first balancer 27 is substantially solid inside and has a small hollow space, preventing generation of a difference in centrifugal force due to oil flowing into the first balancer 27 . This can prevent a difference in centrifugal force generated to the balancer from a designed value, and prevent an increase in vibration.
  • Embodiment 2 Any description duplicating with that in Embodiment 1 will be omitted, and any part identical or equivalent to that in Embodiment 1 will be denoted by the same reference numeral.
  • FIG. 4 is an enlarged view of the vicinity of a balancer-attached slider ASSY 40 of the scroll compressor 100 according to Embodiment 2 of the present invention.
  • FIGS. 5( a ) and 5( b ) are each a diagram illustrating the balancer-attached slider ASSY 40 of the scroll compressor 100 according to Embodiment 2 of the present invention.
  • FIG. 5( a ) is a side view of the balancer-attached slider ASSY 40
  • FIG. 5( b ) is a sectional view taken along line B-B in FIG. 5( a ) .
  • the compression mechanism unit is provided with the balancer-attached slider ASSY 40 .
  • the balancer-attached slider ASSY 40 includes a balancer-attached slider 40 a in which a slider 40 d is attached to a high-density balancer 40 f , and a low-density part 40 b attached to the balancer-attached slider 40 a .
  • the balancer-attached slider 40 a rotates in a space filled with oil, and thus reduction in an oil scattering loss can be achieved by attaching the low-density part 40 b to the balancer-attached slider 40 a.
  • the low-density part 40 b is attached to the balancer-attached slider ASSY 40 to cover the high-density balancer 40 f.
  • the balancer-attached slider 40 a is provided with an oil drain gap 40 c having a dimension of about 0.5 mm to 3 mm for draining oil leaking from a lower part of the orbiting bearing 21 .
  • the oil drain gap 40 c allows efficient drain of the oil through a shortest flow path.
  • An eccentric slider fitting hole 40 e for fitting with the eccentric slider shaft portion 14 a is provided in a central part of the balancer-attached slider ASSY 40 .
  • Fig, 6 is a diagram illustrating prevention of turnover of the balancer-attached slider ASSY 40 of the scroll compressor 100 according to Embodiment 2 of the present invention.
  • an action central point of orbiting bearing reaction force exists at a position in a height direction of the center of the orbiting bearing 21 .
  • a position in a height direction of an action central point of centrifugal force of the entire balancer-attached slider ASSY 40 is set to be equal to the position in the height direction of the center of the orbiting bearing, the centrifugal force (arrow ⁇ 41 ) and the orbiting bearing reaction force (arrow ⁇ 42 ) act at the same position in the height direction, preventing generation of a moment to turn over the balancer-attached slider ASSY 40 .
  • This configuration can prevent partial contact of the orbiting bearing 21 , thereby securing the reliability of the orbiting bearing 21 .
  • Embodiment 3 Any description duplicating with that in Embodiment 1 will be omitted, and any part identical or equivalent to that in Embodiment 1 will be denoted by the same reference numeral.
  • FIG. 7 is a vertical sectional view of the scroll compressor 100 according to Embodiment 3 of the present invention.
  • the second balancer 13 includes a high-density part 52 and a low-density part 51 having a density lower than that of the high-density part 52 .
  • FIGS. 8( a ) and 8( b ) are each a diagram illustrating a method of attaching, to the rotor 12 , the second balancer 13 of the scroll compressor 100 according to Embodiment 3 of the present invention.
  • FIG. 8( a ) is a plan view of the second balancer 13
  • FIG. 8( b ) is a side view of the second balancer 13 .
  • a high-density part fastening hole 52 a is formed in the high-density part 52 of the second balancer 13
  • a low-density part fastening hole 51 a is formed in the low-density part 51 of the second balancer 13
  • a shaft hole 50 is formed by the high-density part 52 and the low-density part 51 .
  • a second fastening member 3 such as a bolt or a rivet is provided through the high-density part fastening hole 52 a and the low-density part fastening hole 51 a to swage the high-density part 52 and the low-density part 51 together with the rotor 12 , thereby attaching the second balancer 13 to the rotor 12 .
  • This assembly can achieve a high productivity.
  • FIG. 9 is an enlarged view of the vicinity of the second balancer 13 of the scroll compressor 100 according to Embodiment 3 of the present invention.
  • the second balancer 13 including the high-density part 52 and the low-density part 51 may be provided separately from the rotor 12 at a position closer to the sub bearing 16 than the rotor 12 .
  • the centrifugal force of the orbiting scroll 5 can be compensated even when the first balancer 27 and the second balancer 13 are downsized.
  • the second balancer 13 is likely to be immersed into oil. Since the second balancer 13 is solid and has an outline in a cylinder shape, however, no oil scattering nor increase in vibration is caused unlike a case in which only a second balancer in a semi-cylinder shape is provided.
  • Embodiment 4 Any description duplicating with that in Embodiment 1 will be omitted, and any part identical or equivalent to that in Embodiment 1 will be denoted by the same reference numeral.
  • FIG. 10 is a vertical sectional view of the scroll compressor 100 according to Embodiment 4 of the present invention.
  • the first balancer 27 is provided below the main bearing 19 .
  • Embodiment 4 differs in the position of the first balancer 27 from Embodiment 1 in which the first balancer 27 is provided above the main bearing 19 as illustrated in FIG. 1 .
  • the same effect as that of Embodiment 1 is obtained with this position in the present Embodiment 4.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US15/311,868 2014-06-18 2014-06-18 Scroll compressor and method of manufacturing the same Abandoned US20170089341A1 (en)

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PCT/JP2014/066215 WO2015194000A1 (ja) 2014-06-18 2014-06-18 スクロール圧縮機およびその製造方法

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020050618A1 (en) * 2018-09-05 2020-03-12 Lg Electronics Inc. Compressor
US10859083B2 (en) 2016-05-20 2020-12-08 Mitsubishi Electric Corporation Scroll compressor
US11193488B2 (en) * 2017-08-04 2021-12-07 Mitsubishi Electric Corporation Scroll compressor
WO2021244013A1 (zh) * 2020-06-01 2021-12-09 珠海格力节能环保制冷技术研究中心有限公司 压缩机
US11261867B2 (en) * 2017-01-11 2022-03-01 Mitsubishi Electric Corporation Compressor comprising a compression mechanism driven by a main shaft having a balance weight comprising an annular oil-receiving recessed portion communicating with a part of a hollow portion of the balance weight
CN114439747A (zh) * 2021-12-24 2022-05-06 珠海格力节能环保制冷技术研究中心有限公司 涡旋压缩机轴系润滑结构、涡旋压缩机、空调器
US20220412352A1 (en) * 2020-01-22 2022-12-29 Mitsubishi Electric Corporation Compressor

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JP6444535B2 (ja) * 2015-11-17 2018-12-26 三菱電機株式会社 スクロール圧縮機
DE102019006665A1 (de) * 2019-09-23 2021-03-25 KSB SE & Co. KGaA Einschaufelrad
CA3188503A1 (en) * 2020-08-31 2022-03-03 Baiying Huang Scroll compressor

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JPS61118579A (ja) * 1984-11-14 1986-06-05 Matsushita Electric Ind Co Ltd スクロ−ル圧縮機
JPH0185481U (ja) * 1987-11-30 1989-06-06
JP2902793B2 (ja) * 1991-02-20 1999-06-07 株式会社日立製作所 スクロール圧縮機
JPH10281083A (ja) * 1997-04-04 1998-10-20 Mitsubishi Electric Corp スクロール圧縮機
JP5836845B2 (ja) * 2012-03-05 2015-12-24 三菱電機株式会社 スクロール圧縮機
JP5999974B2 (ja) * 2012-05-14 2016-09-28 三菱電機株式会社 スクロール圧縮機

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10859083B2 (en) 2016-05-20 2020-12-08 Mitsubishi Electric Corporation Scroll compressor
US11261867B2 (en) * 2017-01-11 2022-03-01 Mitsubishi Electric Corporation Compressor comprising a compression mechanism driven by a main shaft having a balance weight comprising an annular oil-receiving recessed portion communicating with a part of a hollow portion of the balance weight
US11193488B2 (en) * 2017-08-04 2021-12-07 Mitsubishi Electric Corporation Scroll compressor
EP3663583B1 (en) * 2017-08-04 2023-11-15 Mitsubishi Electric Corporation Scroll compressor
WO2020050618A1 (en) * 2018-09-05 2020-03-12 Lg Electronics Inc. Compressor
US11486397B2 (en) * 2018-09-05 2022-11-01 Lg Electronics Inc. Compressor
US11566623B2 (en) 2018-09-05 2023-01-31 Lg Electronics Inc. Compressor
US20220412352A1 (en) * 2020-01-22 2022-12-29 Mitsubishi Electric Corporation Compressor
US11953005B2 (en) * 2020-01-22 2024-04-09 Mitsubishi Electric Corporation Compressor having orbiting scroll supply hole to lubricate thrust surface
WO2021244013A1 (zh) * 2020-06-01 2021-12-09 珠海格力节能环保制冷技术研究中心有限公司 压缩机
CN114439747A (zh) * 2021-12-24 2022-05-06 珠海格力节能环保制冷技术研究中心有限公司 涡旋压缩机轴系润滑结构、涡旋压缩机、空调器

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WO2015194000A1 (ja) 2015-12-23
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