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EP2713053A1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

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Publication number
EP2713053A1
EP2713053A1 EP12773817.7A EP12773817A EP2713053A1 EP 2713053 A1 EP2713053 A1 EP 2713053A1 EP 12773817 A EP12773817 A EP 12773817A EP 2713053 A1 EP2713053 A1 EP 2713053A1
Authority
EP
European Patent Office
Prior art keywords
bushing
scroll member
radial bearing
balance weight
peripheral surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12773817.7A
Other languages
English (en)
French (fr)
Other versions
EP2713053B1 (de
EP2713053A4 (de
Inventor
Hiromichi Tanabe
Hironobu Deguchi
Norikatsu Kiso
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Japan Co Ltd
Original Assignee
Valeo Japan Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Japan Co Ltd filed Critical Valeo Japan Co Ltd
Publication of EP2713053A1 publication Critical patent/EP2713053A1/de
Publication of EP2713053A4 publication Critical patent/EP2713053A4/de
Application granted granted Critical
Publication of EP2713053B1 publication Critical patent/EP2713053B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of 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
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/51—Bearings for cantilever assemblies
    • 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
    • F04C2240/56—Bearing bushings or details thereof
    • 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

Definitions

  • the present invention relates to a scroll-type compressor which is used in a refrigerating cycle of an air conditioning device for a vehicle, and more particularly to a scroll-type compressor having the constitution where an eccentric shaft which is provided to an end portion of a drive shaft is pivotally supported on a boss portion of a revolving scroll member by way of a bushing and a radial bearing.
  • a scroll-type compressor includes: a fixed scroll member which has an end plate and a spiral wall formed on the end plate in an erected manner; and a revolving scroll member which is arranged so as to face the fixed scroll member in an opposed manner and has an end plate and a spiral wall formed on the end plate in an erected manner.
  • the revolving scroll member is configured such that a boss portion is formed on a back surface of the end plate and an eccentric shaft which is provided to one end of a drive shaft is pivotally supported on the boss portion by way of a radial bearing so that the revolving scroll member is supported in a state where the revolving scroll member performs the rocking rotation (revolving motion) about an axis of the drive shaft.
  • the scroll-type compressor disclosed in patent literature 1 is, as shown in Fig. 6 , configured such that a bushing 103 is fitted in a boss portion 102 of a revolving scroll member 101, and the bushing 103 is of a so-called slide-type bushing which is non-rotatable relative to an eccentric shaft 105 provided to one end of a drive shaft 104 and is slightly movable in the radial direction.
  • a curved surface portion 106 is formed on the eccentric shaft 105 so that even when the deformation by deflection is generated in the drive shaft 104 due to a compressive force or a centrifugal force of the revolving scroll member 101, the occurrence of a non-uniform contact on a bearing portion is prevented.
  • This publication also discloses the constitution where a balance weight 107 is mounted on the drive shaft 104 at a position axially displaced from the bushing 103.
  • the scroll-type compressor disclosed in patent literature 2 is, as shown in Fig. 7 , configured such that an eccentric shaft 112 provided to one end of a drive shaft 111 is pivotally supported on a boss portion 117 of a revolving scroll member 115 by way of a bushing 113 and a radial bearing 114, wherein a balance weight 116 is supported on the bushing 113 by being press-fitted on an outer peripheral surface of the bushing 113 so that the balance weight 116 is rotatable together with the bushing 113.
  • the balance weight 116 is arranged so as to project over the outer side of the boss portion 117 of the revolving scroll member 115 in a radial direction such that a point of action where a centrifugal force acts on the balance weight 116 is positioned as close as possible to a point of action where a centrifugal force acts on the revolving scroll member 115.
  • the scroll-type compressor disclosed in patent literature 3 is, as shown in Fig. 8 , configured such that a bushing 122 with which a balance weight 121 is integrally formed is assembled to an eccentric shaft 124 provided to a distal end of a drive shaft 123, and the bushing 122 is pivotally supported on a boss portion 126 formed on a back surface of a revolving scroll member 125 by way of a radial bearing 127 thus making the revolving scroll member 125 perform the revolving motion.
  • the balance weight 121 is arranged so as to project over an outer side of the boss portion 126 of the revolving scroll member 125 in the same manner as patent literature 2, the balance weight 121 is also arranged such that the balance weight 121 further projects toward a side opposite to the revolving scroll member 125 (motor side).
  • the scroll-type compressor disclosed in patent literature 3 is designed such that the projecting of the balance weight 121 in the radial direction is suppressed thus preventing the revolving scroll member 125 from becoming large-sized.
  • the portion on which the balance weight 107 is mounted is not the bushing 103 but the drive shaft 104. Accordingly, centrifugal forces are cancelled each other and balanced in the compressor as a whole. However, the balance weight 107 does not act so as to cancel a centrifugal force of the revolving scroll member 101 which acts so as to push out the revolving scroll member 101 radially outward.
  • the balance weight 116 is formed so as to project over the outside of the boss portion 117 and hence, a rotation prevention mechanism 118 is disposed radially outside the balance weight 116 so as to prevent the interference with the balance weight 116. Accordingly, the revolving scroll member 115 becomes large-sized thus hampering the miniaturization of the compressor. Further, a weight of the revolving scroll member 115 is also increased and hence, there also arises a drawback that it is necessary to make the balance weight 116 large-sized to take a balance with the revolving scroll member 115.
  • the balance weight 121 is formed such that the balance weight 121 projects also toward the side opposite to the revolving scroll member 125 (motor side) and hence, a centrifugal force of the balance weight 121 acts on an end portion of the bushing 122 which projects from the radial bearing 127 whereby an axis of the bushing 122 tends to be inclined with respect to an axis of the eccentric shaft 124.
  • the scroll-type compressor is designed such that a clearance between the radial bearing 127 and an outer peripheral surface of the bushing 122 is set as small as possible so as to make the radial bearing 127 support a force by which the bushing 122 is inclined.
  • a local contact of an inner ring of the bearing exceeds a yield strength thus giving rise to a drawback that flaking occurs.
  • the scroll-type compressor is designed such that a clearance between an inner peripheral surface of a radial bearing 24 and an outer peripheral surface of a bushing 23 (a clearance between a roller 24a and an outer peripheral surface of the bushing 23 in the case of the needle bearing) C is made as small as possible (such that the clearance C becomes smaller than a clearance A between the bushing 23 and an eccentric shaft 17).
  • a balance weight 32 is mounted on an end portion of the bushing 23 so that the center of gravity of the balance weight 32 is displaced from the center of the eccentric shaft 17 provided to an end portion of a drive shaft 12 and hence, as shown in Fig. 9B , an axis of the bushing 23 is inclined with respect to the axis of the eccentric shaft 17.
  • a centrifugal force of the balance weight 32 acts on a revolving scroll member 22 by way of the bushing 23 and the radial bearing 24.
  • the present invention has been made in view of the above, and it is a primary object of the present invention to provide a scroll-type compressor which can, even at the high speed rotation, prevent the occurrence of flaking at a contact portion of a radial bearing which is in contact with a bushing while suppressing the increase in rolling resistance of spiral walls of a pair of scroll members. It is another object of the present invention to realize the miniaturization of the compressor. Solution to Problem
  • a scroll-type compressor is directed to a scroll-type compressor which includes: a fixed scroll member whose movement in the radial direction with respect to a housing is restricted, the fixed scroll member having an end plate and a spiral wall which is formed on the end plate in an erected manner; a revolving scroll member which is arranged so as to face the fixed scroll member in an opposed manner, the revolving scroll member having an end plate and a spiral wall which is formed on the end plate in an erected manner; a drive shaft which transmits rotational power; an eccentric shaft which is provided to an end portion of the drive shaft at a position offset from an axis of the drive shaft; a radial bearing which is fitted into a boss portion formed on a back surface of the revolving scroll member; a bushing which has an eccentric hole into which the eccentric shaft is inserted, the bushing being fitted on the eccentric shaft by way of the eccentric hole, and the bushing being relatively rotatably supported on the
  • an offset load generated in the radial bearing can be decreased and hence, a yield strength of the radial bearing is relatively enhanced whereby the occurrence of flaking which occurs at a contact portion of the radial bearing which is in contact with the outer peripheral surface of the bushing can be suppressed.
  • the relationship A/B ⁇ C/D may preferably be established.
  • a needle bearing may preferably be used as the radial bearing.
  • the needle bearing has a compact shape and is light-weighted, a contact face pressure becomes excessively large when a shaft is brought into contact with the needle bearing in a state that the shaft is inclined with respect to an axis of the bearing and hence, the use of the needle bearing is supposed not to be desirable for supporting an axial load or the inclining of the shaft.
  • a local load between the radial bearing and the bushing can be decreased as described above and hence, a yield strength of the radial bearing can be relatively enhanced whereby the needle bearing can sufficiently cope with the supporting of an axial load or the inclining of the shaft as the radial bearing.
  • a weight of the bearing can be reduced, and a size of the radial bearing in the radial direction can be also made compact so that the balance weight can be also made light-weighted.
  • the needle bearing can be sufficiently used as the radial bearing.
  • the revolving scroll member in which the needle bearing is mounted becomes light-weighted, and a weight of the balance weight which is provided for canceling a centrifugal force of the revolving scroll member can be also decreased.
  • a scroll-type compressor 1 is an electrically-operated compressor suitable for a refrigerating cycle which uses a refrigerant as a working fluid, wherein, in the inside of a housing 2 which is made of an aluminum alloy, a compression mechanism 3 is arranged on a left side in the drawing, and an electrically-operated motor 4 for driving the compression mechanism 3 is arranged on a right side in the drawing.
  • a front side of the compressor 1 is arranged on a right side in the drawing, and a rear side of the compressor is arranged on a left side in the drawing.
  • the housing 2 includes: a compression mechanism housing member 2a which houses the compression mechanism 3 therein, an electrically-operated motor housing member 2b which houses the electrically-operated motor 4 for driving the compression mechanism 3 therein; and an inverter housing member 2c which houses an inverter device not shown in the drawing for controlling driving of the electrically-operated motor 4 therein.
  • These housing members are positioned by positioning pins 7 and are fastened to each other in the axial direction using fastening bolts 8.
  • a partition wall 10 which is integrally formed with a shaft support portion 9a is provided on a side which faces the compression mechanism housing member 2a. Also in the inverter housing member 2c, a partition wall 11 which is integrally formed with a shaft support portion 9b is provided on a side which faces the electrically-operated motor housing member 2b.
  • a drive shaft 12 is rotatably supported on the shaft support portions 9a, 9b of the partition walls 10, 11 by way of bearings 13, 14.
  • the inside of the housing 2 is partitioned into: a compression mechanism housing portion 15a which houses the compression mechanism 3 therein; an electrically-operated motor housing portion 15b which houses the electrically-operated motor 4 therein; and an inverter housing portion 15c which houses the inverter device therein in order from a rear side of the housing 2.
  • the inverter housing portion 15c is defined by fixing a lid body 16 to the inverter housing member 2c using bolts or the like not shown in the drawing.
  • the compression mechanism 3 is a scroll-type compression mechanism which includes a fixed scroll member 21, and a revolving scroll member 22 which is arranged so as to face the fixed scroll member 21 in an opposed manner.
  • the fixed scroll member 21 is configured such that, while the movement of the fixed scroll member 21 in the axial direction with respect to the housing 2 is allowed, the movement of the fixed scroll member 21 in the radial direction relative to the housing 2 is restricted by a positioning pin 28.
  • the fixed scroll member 21 is constituted of: a circular disc-shaped end plate 21a; a cylindrical outer peripheral wall 21b which is formed on and along an outer periphery of the end plate 21a over the whole circumference in an erected manner toward a front side; and a spiral wall 21c having a spiral shape which is formed on the end plate 21a in an erected manner inside the outer peripheral wall 21b such that the spiral wall 21c extends toward a front side.
  • the revolving scroll member 22 is constituted of: a circular disc-shaped end plate 22a; and a spiral wall 22c having a spiral shape which is formed on the end plate 22a in an erected manner such that the spiral wall 22c extends toward a rear side.
  • An eccentric shaft 17 which is provided to a rear end portion of the drive shaft 12 and is disposed eccentrically with respect to an axis of the drive shaft 12 is supported on a boss portion 22b which is formed on a back surface of the end plate 22a in an erected manner by way of a bushing 23 and a radial bearing 24 so that the eccentric shaft 17 is capable of performing the revolving motion about the axis of the drive shaft 12.
  • the spiral wall 21c of the fixed scroll member 21 and the spiral wall 22c of the revolving scroll member 22 are meshed with each other so that a compression chamber 25 is defined in a space surrounded by the end plate 21a of the fixed scroll member 21, the spiral wall 21c of the fixed scroll member 21, the end plate 22a of the revolving scroll member 22, and the spiral wall 22c of the revolving scroll member 22.
  • An annular thrust race 26 having a thin plate shape is sandwiched between the outer peripheral wall 21b of the fixed scroll member 21 and the partition wall 10, and the fixed scroll member 21 and the partition wall 10 are made to abut to each other by way of the thrust race 26.
  • the thrust race 26 is formed using a material having excellent wear resistance, and a center opening through which the boss portion 22b of the revolving scroll member 22 and an Oldham ring 27 described later pass is formed in a center portion of the thrust race 26. Further, the respective positions of the fixed scroll member 21, the thrust race 26, and the electrically-operated motor housing member 2b in the radial direction are restricted by the positioning pin 28 which is inserted into a pin insertion hole formed in the thrust race 26.
  • the shaft support portion 9a which is integrally formed with the partition wall 10 of the electrically-operated motor housing member 2b has a through hole at the center thereof, and a diameter of an inner surface of the shaft support portion 9a is increased toward the thrust race 26 in a stepwise manner.
  • a bearing housing portion 31 in which the bearing 13 is housed a weight housing portion 33 in which a balance weight 32 which is integrally formed with the bushing 23 or is fitted on the bushing in a non-rotatable manner relative to the bushing 23 and is rotatable along with the rotation of the drive shaft 12 as an integral body with the busing 23 (in this embodiment, the balance weight 32 being formed as a body separate from the bushing 23, and being fitted on the bushing 23 in a non-rotatable manner relative to the bushing 23) is housed, and an Oldham housing portion 34 which is formed continuously with the weight housing portion 33 and in which the Oldham ring 27 which prevents the rotation between the revolving scroll member 22 and the Oldham housing portion 34 is housed are formed.
  • the revolving scroll member 22 generates a rotational force due to the rotation of the drive shaft 12
  • the revolving scroll member 22 performs the revolving motion about the axis of the drive shaft 12 while the rotation of the revolving scroll member 22 is restricted by the Oldham ring 27.
  • a suction chamber 35 which sucks a refrigerant introduced from a suction port 40 described later through an intake passage 45 is formed between the outer peripheral wall 21b of the above-mentioned fixed scroll member 21 and an outermost peripheral portion of the spiral wall 22c of the revolving scroll member 22.
  • a discharge chamber 37 into which a refrigerant gas which is compressed in the compression chamber 25 is discharged through a discharge hole 36 which is formed on the approximately center of the fixed scroll member 21 is formed between a rear end wall of the compression mechanism housing member 2a and the fixed scroll member 21.
  • a refrigerant gas discharged into the discharge chamber 37 is pressure-fed to an external refrigerant circuit through the discharge port 38.
  • stator 41 is constituted of a core 43 having a cylindrical shape and a coil 44 which is wound around the core 43, and is fixed to an inner surface of the housing 2 (the electrically-operated motor housing member 2b).
  • the rotor 42 made of magnet which is housed in the inside of the stator 41 in a rotatable manner is fixedly mounted on the drive shaft 12. The rotor 42 is rotated by a rotational magnetic force generated by the stator 41 so that the drive shaft 12 is rotated.
  • the electrically-operated motor 4 which is formed of a brushless DC motor is constituted of the stator 41 and the rotor 42.
  • the suction port 40 through which a refrigerant gas is sucked into the electrically-operated motor housing portion 15b is formed in a side surface of the housing 2 (electrically-operated motor housing member 2b).
  • the suction passage 45 which introduces a refrigerant flown into the electrically-operated motor housing portion 15b from the suction port 40 into the suction chamber 35 is formed through a gap formed between the stator 41 and the housing 2 (electrically-operated motor housing member 2b), a hole formed in the partition wall 10, and a gap formed between the fixed scroll member 21 and the housing 2.
  • the inverter device which is housed in the inverter housing member 2c is electrically connected with the stator 41 via a terminal (airtight terminal) 60 which is mounted in a through hole 61 formed in the partition wall 11, and electricity is supplied to the electrically-operated motor 4 from the inverter device.
  • the revolving scroll member 22 is rotated around an axis of the eccentric shaft 17 and hence, the revolving scroll member 22 revolves around the axis of the fixed scroll member 21. Since the rotation of the revolving scroll member 22 is prevented by the rotation prevention mechanism which is constituted of the Oldham ring 27, only the revolving motion of the revolving scroll member 22 is allowed.
  • the compression chamber 25 is moved toward the center from outer peripheral sides of the spiral walls 21c, 22c of both the scroll members while a volume of the compression chamber 25 is gradually decreased and hence, a refrigerant gas sucked into the compression chamber 25 from the suction chamber 35 is compressed, and the compressed refrigerant gas is discharged into the discharge chamber 37 through the discharge hole 36 which is formed in the end plate 21a of the fixed scroll member 21. Then, the refrigerant gas is fed out to the external refrigerant circuit through the discharge port 38.
  • the bushing 23 has a columnar shape.
  • An eccentric hole 23a which extends in the axial direction and allows the insertion of the eccentric shaft 17 therein is formed in the bushing 23 at a position offset from the axis of the bushing 23 in the radial direction.
  • a recessed portion 23b whose diameter is set larger than a diameter of the eccentric hole 23a is formed in a revolving scroll member -side end portion of the bushing 23.
  • a weight fitting margin 23c which has a small outer diameter and on which the balance weight 32 is fitted is formed on the periphery of an electrically-operated-motor-side end portion of the bushing 23.
  • the balance weight 32 is constituted of a fitting portion 32a which is formed in an annular shape, and a fan-shaped weight body 32b which is integrally formed on the periphery of the fitting portion 32a over a predetermined angular range.
  • the fitting portion 32a is fitted on the outer periphery of the weight fitting margin 23c of the bushing 23 by press-fitting, for example, so that the balance weight 32 is rotatable with the bushing 23.
  • the balance weight is formed such that the balance weight projects in the direction that the balance weight approaches the revolving scroll member and also in the direction away from the revolving scroll member. Due to such a constitution, it is possible to ensure a required mass while preventing the balance weight from interfering with the Oldham ring by decreasing a size of the balance weight in the radial direction.
  • the eccentric shaft 17 is a shaft having a circular columnar shape.
  • An annular groove 17a is formed on the eccentric shaft 17 at a position in the vicinity of one end of the eccentric shaft 17.
  • An end portion of the eccentric shaft 17 on a side opposite to a side where the annular groove 17a is formed is press-fitted into and fixed to a fitting hole 12a formed in an end surface of the drive shaft 12 which faces the revolving scroll member 22 in an opposed manner.
  • An annular-groove-side end portion of the eccentric shaft 17 is inserted into the eccentric hole 23a of the bushing 23 in a relatively rotatable manner, and is projected into the recessed portion 23b.
  • a snap ring 29 is fitted in the annular groove 17a at the portion of the eccentric shaft 17 projected into the recessed portion 12b.
  • the bushing 23 is mounted on the eccentric shaft 17 in the above-mentioned manner. Accordingly, the bushing 23 is mounted on the eccentric shaft 17 in a relatively rotatable manner with respect to the eccentric shaft 17 while the movement of the bushing 23 in the axial direction is restricted.
  • the radial bearing 24 which is fitted into the boss portion 22b of the revolving scroll member 22 is constituted of a needle bearing where a large number of needle-shaped rollers 24a are arranged equidistantly in the circumferential direction, and the bushing 23 can be fitted into the radial bearing 24 in a relatively rotatable manner with a predetermined clearance between an outer peripheral surface of the bushing 23 and the radial bearing 24.
  • the radial bearing 24 is configured such that the number of rollers is set to 14, a length of a roller portion (a length of fitting between the roller and the outer peripheral surface of the bushing 23 in the axial direction) is set to 10mm, and a diameter of the roller is set to 2.5mm. Further, a length of fitting between the bushing and the eccentric shaft in the axial direction is set to 15mm, and a diameter of the eccentric shaft is set to 6mm.
  • a clearance between a radial bearing and a member which is supported on the radial bearing is usually set as small as possible by taking into account tolerance of the member such that the radial bearing and the member are brought into contact with each other in a state where they are arranged as parallel as possible. That is, although the radial bearing 24 formed of the needle bearing is light-weighted and has a compact shape, the radial bearing 24 is not suitable for supporting an axial load or an inclination of the shaft.
  • the balance weight 32 is mounted on a portion of one end portion of the bushing 23 projecting from the radial bearing 24 in the axial direction and hence, the axis of the bushing 23 tends to be inclined with respect to the axis of the eccentric shaft 17 (drive shaft 12) due to a centrifugal force of the balance weight 32.
  • the bushing 23 is brought into non-uniform contact with the radial bearing 24 at two different portions in the axial direction whereby an offset load is remarkably increased at a contact portion of an end portion side of the bushing 23 where the balance weight 23 is mounted thus giving rise to a drawback that flaking occurs at the contact portion.
  • a clearance A between the outer peripheral surface of the eccentric shaft 17 which is inserted into the eccentric hole 23a and the inner peripheral surface of the eccentric hole 23a is set smaller than a clearance C between the outer peripheral surface of the bushing 23 and the inner peripheral surface of the radial bearing 24.
  • the center of gravity of the balance weight 32 which is mounted on the end portion of the bushing 23 projecting from the radial bearing 24 is displaced from the center of the eccentric shaft 17 (a centrifugal force of the balance weight acts on the end portion of the bushing 23 projecting from the radial bearing 24). Accordingly, as shown in Fig. 5B , the axis of the bushing 23 is inclined with respect to the axis of the eccentric shaft 17.
  • the clearance A between the outer peripheral surface of the eccentric shaft 17 which is inserted into the eccentric hole 23a and the inner peripheral surface of the eccentric hole 23a is set smaller than the clearance C between the outer peripheral surface of the bushing 23 and the inner peripheral surface of the radial bearing 24 and hence, the inclination of the bushing 23 is restricted by the eccentric shaft 17 (the bushing 23 being mainly supported on the eccentric shaft 17), and the bushing 23 is brought into contact with the radial bearing 24 only at one portion (the outer peripheral surface of the bushing 23 being brought into contact with only the end portion side of the radial bearing 24 on which the balance weight 32 is mounted but not being brought into contact with the end portion side of the radial bearing remote from the balance weight 32).
  • the previously-mentioned load F3 (shown in Fig. 9 ) is not generated and hence, there exists no possibility that a load F2 which acts on a portion of the end portion side of the bushing 23 which is brought into contact with the radial bearing 24 on which the balance weight 32 is mounted is remarkably increased whereby the load F2 becomes substantially equal to a load F1.
  • the inclination of the bushing 23 is supported by the outer peripheral surface of the eccentric shaft 17 and the fitting portion of the eccentric hole 23a which is formed in the bushing 23 and hence, local loads ( ⁇ 1, ⁇ 2) are generated at contact portions between the eccentric shaft 17 and the eccentric hole 23a.
  • the bushing 23 is not rotatable relative to the eccentric shaft 17 and hence, sliding and rolling are not generated at the contact portion whereby there exists no possibility that flaking or wear is generated.
  • the clearance C is controlled by applying forming (so-called matching forming) to the outer peripheral surface of the bushing 23 in conformity with a size of the inner peripheral surface of the radial bearing 24.
  • forming so-called matching forming
  • the clearance A may be set to 6 to 12 ⁇ m by applying matching forming to the control of clearance A (by forming the outer peripheral surface of the eccentric shaft 17 in accordance with a size of the inner peripheral surface of the eccentric hole 23a). Due to such a constitution, the inclination of the bushing which is supported with the clearance A can be further decreased without increasing man-hours for forming compared to the conventional technique.
  • an offset load which acts on the radial bearing 24 (roller 24a) can be decreased. Even when the bushing 23 is brought into local contact with the roller 24a of the radial bearing 24 due to a non-uniform contact, the generation of flaking can be suppressed and hence, a yield strength of the radial bearing 24 can be relatively enhanced (resulting in that large-sizing of the radial bearing 24 for ensuring a yield strength of the radial bearing 24 becomes unnecessary).
  • the balance weight 32 is formed such that the balance weight 32 projects also in the direction away from the revolving scroll member 22 and hence, a length of the balance weight in the radial direction can be suppressed and, further, the balance weight 32 can be mounted such that the balance weight 32 does not interfere with the rotation prevention mechanism (Oldham ring 27). Accordingly, the increase in diameter of the Oldham ring 27 can be prevented so that an outer diameter of the revolving scroll member can be made small.
  • the needle bearing is used as the radial bearing 24 and hence, a weight of the bearing per se can be decreased. Further, a size of the radial bearing in the radial direction can be also made compact and hence, the balance weight can be made light-weighted.

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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)
EP12773817.7A 2011-04-22 2012-04-20 Spiralverdichter Not-in-force EP2713053B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011096236A JP5594846B2 (ja) 2011-04-22 2011-04-22 スクロール型圧縮機
PCT/JP2012/002731 WO2012144224A1 (ja) 2011-04-22 2012-04-20 スクロール型圧縮機

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EP2713053A1 true EP2713053A1 (de) 2014-04-02
EP2713053A4 EP2713053A4 (de) 2014-11-26
EP2713053B1 EP2713053B1 (de) 2016-04-13

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EP2913531A1 (de) * 2014-02-28 2015-09-02 Mitsubishi Heavy Industries, Ltd. Spiralverdichter mit ausgleichsgewicht
US9670927B2 (en) 2013-03-06 2017-06-06 Kabushiki Kaisha Toyota Jidoshokki Scroll compressor with a balancer and elastic member
DE102020211559A1 (de) 2020-09-15 2022-03-17 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Scrollverdichter
US20220213894A1 (en) * 2019-04-26 2022-07-07 Edwards Limited Scroll pump crank sleeve
US11655819B2 (en) 2018-08-13 2023-05-23 Mitsubishi Heavy Industries Thermal Systems, Ltd. Scroll compressor
US11867182B2 (en) 2020-01-21 2024-01-09 Copeland Climate Technologies (Suzhou) Co. Ltd. Scroll compressor
US20250052239A1 (en) * 2023-08-11 2025-02-13 Fu Sheng Industrial Co. Ltd. Compressor

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JP6208534B2 (ja) * 2013-10-25 2017-10-04 株式会社ヴァレオジャパン 電動スクロール圧縮機
CN104047851A (zh) * 2014-07-11 2014-09-17 湖南联力精密机械有限公司 动盘和静盘可径向密封的涡旋空气压缩机
US10415389B2 (en) * 2014-09-10 2019-09-17 Hitachi Industrial Equipment Systems Co., Ltd. Scroll fluid machine with improved reliability and performance of components thereof
KR102291952B1 (ko) * 2015-03-04 2021-08-23 한온시스템 주식회사 스크롤 압축기의 편심부쉬 결합구조
JP2019100246A (ja) * 2017-11-30 2019-06-24 サンデン・オートモーティブコンポーネント株式会社 スクロール型流体機械
JP7056821B2 (ja) * 2018-08-31 2022-04-19 サンデン・オートモーティブコンポーネント株式会社 スクロール圧縮機
KR102097499B1 (ko) * 2018-09-17 2020-04-06 엘지전자 주식회사 스크롤형 압축기
CN111089055B (zh) * 2018-10-23 2024-09-06 谷轮环境科技（苏州）有限公司 涡旋压缩机
KR102503234B1 (ko) * 2018-11-30 2023-02-24 한온시스템 주식회사 스크롤 압축기
CN113530814A (zh) * 2020-04-17 2021-10-22 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

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JP2734408B2 (ja) 1995-06-23 1998-03-30 三菱電機株式会社 スクロール圧縮機
JP3214417B2 (ja) * 1997-11-11 2001-10-02 ダイキン工業株式会社 スクロール型流体機械
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AU9519298A (en) * 1997-12-03 1999-06-24 Sanden Corporation Scroll compressor in which an eccentric bush is radially movable with being guide by a guide pin
JP4958329B2 (ja) * 1997-12-03 2012-06-20 サンデン株式会社 スクロール型圧縮機
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JP4597358B2 (ja) * 2000-12-22 2010-12-15 株式会社日本自動車部品総合研究所 スクロール型圧縮機
GB0426937D0 (en) * 2004-12-08 2005-01-12 Boc Group Plc Scroll-type apparatus
CN2821227Y (zh) * 2005-07-14 2006-09-27 乐金电子(天津)电器有限公司 具有活动平衡锤的涡旋压缩机
JP5075810B2 (ja) * 2008-12-26 2012-11-21 株式会社日立産機システム スクロール式流体機械
JP2010196630A (ja) 2009-02-26 2010-09-09 Denso Corp 圧縮機

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9670927B2 (en) 2013-03-06 2017-06-06 Kabushiki Kaisha Toyota Jidoshokki Scroll compressor with a balancer and elastic member
EP2913531A1 (de) * 2014-02-28 2015-09-02 Mitsubishi Heavy Industries, Ltd. Spiralverdichter mit ausgleichsgewicht
US11655819B2 (en) 2018-08-13 2023-05-23 Mitsubishi Heavy Industries Thermal Systems, Ltd. Scroll compressor
US20220213894A1 (en) * 2019-04-26 2022-07-07 Edwards Limited Scroll pump crank sleeve
US11867182B2 (en) 2020-01-21 2024-01-09 Copeland Climate Technologies (Suzhou) Co. Ltd. Scroll compressor
DE102020211559A1 (de) 2020-09-15 2022-03-17 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Scrollverdichter
US20250052239A1 (en) * 2023-08-11 2025-02-13 Fu Sheng Industrial Co. Ltd. Compressor
US12320352B2 (en) * 2023-08-11 2025-06-03 Fu Sheng Industrial Co. Ltd. Compressor

Also Published As

Publication number Publication date
CN103477079B (zh) 2016-01-20
EP2713053B1 (de) 2016-04-13
EP2713053A4 (de) 2014-11-26
JP2012225328A (ja) 2012-11-15
WO2012144224A1 (ja) 2012-10-26
CN103477079A (zh) 2013-12-25
JP5594846B2 (ja) 2014-09-24

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