WO2012144224A1 - スクロール型圧縮機 - Google Patents

スクロール型圧縮機 Download PDF

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Publication number
WO2012144224A1
WO2012144224A1 PCT/JP2012/002731 JP2012002731W WO2012144224A1 WO 2012144224 A1 WO2012144224 A1 WO 2012144224A1 JP 2012002731 W JP2012002731 W JP 2012002731W WO 2012144224 A1 WO2012144224 A1 WO 2012144224A1
Authority
WO
WIPO (PCT)
Prior art keywords
bush
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.)
Ceased
Application number
PCT/JP2012/002731
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
裕通 田邊
裕展 出口
教勝 木曽
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
Priority to EP12773817.7A priority Critical patent/EP2713053B1/en
Priority to CN201280018752.XA priority patent/CN103477079B/zh
Publication of WO2012144224A1 publication Critical patent/WO2012144224A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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 compressor used in a refrigeration cycle of a vehicle air conditioner, and more particularly to an eccentric shaft provided at an end portion of a drive shaft mounted on a boss portion of an orbiting scroll member via a bush and a radial bearing.
  • the present invention relates to a scroll-type compressor having a configuration to do so.
  • the scroll type compressor has a fixed scroll member having an end plate and a spiral wall standing upright from the end plate, and has an end plate opposed to the fixed scroll member and a spiral wall standing upright from the end plate. And a pair of scroll members combined with each of the spiral walls and rotating the orbiting scroll member in a state where rotation is restricted (revolving motion), so that the space between the spiral walls of both scroll members is reduced.
  • the compression chamber formed in the above is moved to the center while reducing the volume to compress the working fluid.
  • the orbiting scroll member has a boss portion formed on the back surface of the end plate, and an eccentric shaft provided at one end of the drive shaft is mounted on the boss portion via a radial bearing.
  • the shaft is supported so as to be able to oscillate (revolve) around the axis of the drive shaft.
  • the scroll compressor disclosed in Patent Document 1 has a bush 103 attached to the boss portion 102 of the orbiting scroll member 101 as shown in FIG.
  • This is a so-called slide-type bush that is relatively unrotatable with respect to the eccentric shaft 105 provided at one end of the shaft and can move slightly in the radial direction.
  • the eccentric shaft 105 is provided with a curved surface portion 106 so that even if the drive shaft 104 is deformed by the compressive force or centrifugal force of the orbiting scroll member 101, the bearing portion does not cause a single contact.
  • the publication also discloses a configuration in which the balance weight 107 is provided on the drive shaft 104 at a position shifted in the axial direction from the bush 103.
  • the scroll compressor disclosed in Patent Document 2 is configured such that an eccentric shaft 112 provided at one end of a drive shaft 111 is connected to a boss portion of an orbiting scroll member 115 via a bush 113 and a radial bearing 114.
  • the balance weight 116 is supported by being press-fitted into the outer peripheral surface of the bush 113, and rotates together with the bush 113.
  • the balance weight 116 extends outward in the radial direction of the boss portion 117 of the orbiting scroll member 115 so that the acting point of the centrifugal force acting on the balance weight 116 is as close as possible to the acting point of the centrifugal force acting on the orbiting scroll member 115. Is provided.
  • a bush 122 integrally provided with a balance weight 121 is assembled to an eccentric shaft 124 provided at the tip of a drive shaft 123.
  • the orbiting scroll member 125 is revolved by pivoting it on a boss portion 126 provided on the rear surface of the orbiting scroll member 125 via a radial bearing 127.
  • the balance weight 121 is provided so as to project outside the boss portion 126 of the orbiting scroll member 125, as in Patent Document 2, but it also projects to the opposite side (motor side) of the orbiting scroll member 125. Since it is provided, the overhang in the radial direction is suppressed, and a device for avoiding an increase in the diameter of the orbiting scroll member 125 is devised.
  • the balance weight 116 is provided so as to protrude outside the boss portion 117, the rotation prevention mechanism 118 is further provided to avoid interference with the balance weight 116. Therefore, the orbiting scroll member 115 is increased in size and hinders downsizing of the compressor. Further, since the weight of the orbiting scroll member 115 becomes heavy, there is also a disadvantage that the balance weight 116 must be increased in order to balance it.
  • the balance weight 121 is provided so as to protrude on the opposite side (motor side) from the orbiting scroll member 125, so the centrifugal force of the balance weight 121 is a radial bearing. It acts on the end of the bush 122 protruding from 127, and the shaft center of the bush 122 tends to tilt with respect to the shaft center of the eccentric shaft 124. For this reason, in order to reduce the inclination of the bush 122, conventionally, the clearance between the radial bearing 127 and the outer peripheral surface of the bush 122 is set as small as possible, and the force that the bush 122 tends to tilt by the radial bearing 127 is used. However, at the time of high-speed rotation, the local contact of the bearing inner ring exceeds the proof stress, and there is a disadvantage that flaking occurs.
  • a gap between the inner peripheral surface of the radial bearing 24 and the outer peripheral surface of the bush 23 is provided. Clearance (in the case of a needle bearing, the clearance between the roller 24a and the outer peripheral surface of the bush 23) C is made as small as possible (C is made smaller than the clearance A between the bush 23 and the eccentric shaft 17).
  • the balance weight 32 is provided at the end of the bush 23, and the center of gravity of the balance weight 32 is offset from the center of the eccentric shaft 17 provided at the end of the drive shaft 12, so that FIG. As shown in FIG.
  • the shaft center of the bush 23 is inclined with respect to the shaft center of the eccentric shaft 17, and the centrifugal force of the balance weight 32 in this state causes the bush 2 And acting on the orbiting scroll member 22 through a radial bearing 24.
  • the clearance C is formed smaller than the clearance A, two inner surfaces of the radial bearing 24 (the end portion provided with the balance weight 32 are provided to support the bush 23 inclined by the centrifugal force F1 of the balance weight 32.
  • the present invention has been made in view of such circumstances, and flaking is performed at a contact portion with a bush of a radial bearing while suppressing an increase in rolling resistance of a spiral wall of a scroll member that forms a pair even during high-speed rotation.
  • the main object is to provide a scroll compressor that avoids the occurrence of the above.
  • another object is to reduce the size of the compressor.
  • a scroll compressor is provided with a fixed scroll member that has an end plate and a spiral wall that is erected from the end plate, the movement in the radial direction of the housing being restricted,
  • the orbiting scroll member disposed opposite to the fixed scroll member and having an end plate and a spiral wall erected from the end plate, a drive shaft for transmitting rotational power, and an end portion of the drive shaft, the drive shaft
  • An eccentric shaft provided at a position shifted with respect to the axis of the shaft, a radial bearing fitted in a boss formed on the back surface of the orbiting scroll member, and an eccentric hole into which the eccentric shaft is inserted,
  • a bush that is externally fitted to the eccentric shaft through the eccentric hole and that is rotatably supported by the radial bearing, and a balance weight that is provided at one end of the bush and is integrated with the bush.
  • a scroll compressor characterized in that, when the bush is inclined, the outer peripheral surface of the bush is brought into contact with the radial bearing only at the
  • the balance weight centrifugal force acts on the portion that is axially displaced from the radial bearing (the end of the bush that protrudes from the radial bearing), the balance weight centrifugal force causes the bush axis to be eccentric.
  • the outer peripheral surface of the bush comes into contact with the radial bearing only at the end side where the balance weight is provided. It becomes possible to avoid a situation in which the end of the bush that moves the local load away from the balance weight abuts against the radial bearing to increase significantly.
  • a specific configuration in which the bush is brought into contact with the radial bearing only at the end portion side where the balance weight is provided is as follows: the eccentric shaft and the inner peripheral surface of the eccentric hole provided in the bush.
  • the clearance is A
  • the fitting length between the eccentric shaft and the inner peripheral surface of the eccentric hole provided in the bush is B
  • the clearance between the radial bearing and the outer peripheral surface of the bush is C
  • the fitting between the radial bearing and the outer peripheral surface of the bush When the length is D, it may be set so that A / B ⁇ C / D.
  • the offset load (the contact between the bush and the radial bearing) due to the inclination of the bush. (Local load at the contact point) can be suppressed within an allowable range. Therefore, when the anti-rotation mechanism is disposed on the radially outer side of the boss portion of the orbiting scroll member, the balance weight is removed from the orbiting scroll member. You may make it project so that it may protrude positively and may avoid interference with a rotation prevention mechanism.
  • Needle bearings are compact and lightweight, but contact surface pressure becomes excessive when the shaft is in contact with the shaft center of the bearing, so it is not suitable for supporting axial loads and shaft tilt. Since the local load with the bush can be reduced as described above, the proof stress can be relatively increased, and the needle bearing can sufficiently cope with it. For this reason, the weight of the bearing can be reduced, and the radial dimension can be made compact, so that the balance weight can also be reduced in weight.
  • the eccentric shaft provided at the end of the drive shaft is connected to the radial bearing provided at the boss portion of the orbiting scroll member via the bush provided integrally with the balance weight.
  • the bush When the bush is tilted, the outer peripheral surface of the bush is brought into contact with the radial bearing only at the end side where the balance weight is provided.
  • the local load is not significantly increased at the contact portion between the surface and the radial bearing, and flaking can be avoided at the contact portion between the radial bearing and the bush. For this reason, it is possible to avoid the occurrence of flaking at the contact portion with the bush of the radial bearing while suppressing an increase in rolling resistance of the spiral wall of the scroll member that makes a pair even at high speed rotation. It becomes.
  • the balance weight even when the balance weight is formed to protrude away from the orbiting scroll member, the local load at the contact portion between the outer peripheral surface of the bush and the radial bearing is within an allowable range. Therefore, by forming the balance weight so as to project away from the orbiting scroll member, even if a rotation prevention mechanism is provided close to the outside of the boss, interference with this is avoided. As a result, the outer diameter of the rotation prevention mechanism and the orbiting scroll member can be reduced.
  • the radial bearing can be sufficiently accommodated by the needle bearing.
  • the weight of the scroll member can be reduced, and the weight of the balance weight provided for canceling the centrifugal force of the orbiting scroll member can be reduced.
  • FIG. 1 is a cross-sectional view showing an example of the overall configuration of a scroll compressor according to the present invention.
  • FIG. 2A is a cross-sectional view showing a state in which a bush is externally fitted to an eccentric shaft provided at an end portion of a drive shaft, and this bush is supported by a radial bearing provided at a boss portion of the orbiting scroll member.
  • FIG. 2 (b) is an exploded perspective view of FIG. 2 (a).
  • 3A and 3B are diagrams showing the bush, wherein FIG. 3A is a view seen from one side in the axial direction, FIG. 3B is a side sectional view of the bush, and FIG. 3C is the other side in the axial direction. It is the figure seen from.
  • FIG. 4A and 4B are diagrams showing the balance weight, where FIG. 4A is a view seen from one side in the axial direction, FIG. 4B is a side sectional view of the balance weight, and FIG. 4C is the other side in the axial direction. It is the figure seen from the side.
  • FIG. 5 shows a state in which an eccentric shaft provided at the end of the drive shaft is mounted on a radial bearing provided at the boss portion of the orbiting scroll member via a bush having a balance weight provided at one end. It is an enlarged view shown, (a) is a figure which shows the state which the drive shaft is not rotating, (b) is a figure which shows the state in which the drive shaft rotated and the bush inclined.
  • FIG. 5 shows a state in which an eccentric shaft provided at the end of the drive shaft is mounted on a radial bearing provided at the boss portion of the orbiting scroll member via a bush having a balance weight provided at one end. It is an enlarged view shown, (a) is a figure which shows the
  • FIG. 6 is a cross-sectional view showing a conventional scroll compressor.
  • FIG. 7 is a cross-sectional view showing another conventional scroll compressor.
  • FIG. 8 is a cross-sectional view showing still another conventional scroll compressor.
  • FIG. 9 shows a conventional example in which an eccentric shaft provided at an end portion of a drive shaft is mounted on a radial bearing provided at a boss portion of an orbiting scroll member via a bush having a balance weight provided at one end portion. It is an enlarged view which shows a state, (a) is a figure which shows the state which the drive shaft is not rotating, (b) is a figure which shows the state in which the drive shaft rotated and the bush inclined.
  • a scroll compressor 1 is an electric compressor suitable for a refrigeration cycle using a refrigerant as a working fluid, and a compression mechanism 3 is arranged on the left side in the figure in a housing 2 made of an aluminum alloy.
  • an electric motor 4 for driving the compression mechanism 3 is disposed on the right side in the drawing.
  • the right side in the drawing is the front side of the compressor 1
  • the left side in the drawing is the rear side of the compressor.
  • the housing 2 includes a compression mechanism housing member 2 a that houses the compression mechanism 3, an electric motor housing member 2 b that houses the electric motor 4 that drives the compression mechanism 3, and an inverter that houses an inverter device (not shown) that drives and controls the electric motor 4.
  • the housing member 2c is positioned with the positioning pins 7 and fastened in the axial direction with the fastening bolts 8.
  • a partition wall 10 formed integrally with a shaft support portion 9a is provided on the side of the motor housing housing member 2b that faces the compression mechanism housing housing member 2a, and is opposed to the motor housing housing member 2b of the inverter housing housing member 2c.
  • a partition wall 11 in which a shaft support portion 9b is integrally formed is provided on the side to be supported, and a drive shaft 12 is rotatably supported by the shaft support portions 9a and 9b of the partition walls 10 and 11 via bearings 13 and 14, respectively.
  • the partition wall 10, 11 formed in the motor housing housing member 2 b and the inverter housing housing member 2 c has a compression mechanism housing portion 15 a in which the inside of the housing 2 houses the compression mechanism 3 from the rear, and a motor in which the motor 4 is housed.
  • the inverter accommodating portion 15c is defined by fixing the lid 16 to the inverter accommodating housing member 2c with a bolt or the like (not shown).
  • the compression mechanism 3 is of a scroll type having a fixed scroll member 21 and an orbiting scroll member 22 disposed to face the fixed scroll member 21, and the fixed scroll member 21 is allowed to move in the axial direction with respect to the housing 2.
  • the movement in the radial direction is restricted by the positioning pin 28, a disc-shaped end plate 21a, and a cylinder that is provided over the entire periphery along the outer edge of the end plate 21a and is erected forward.
  • An outer peripheral wall 21b and a spiral spiral wall 21c extending forward from the end plate 21a inside the outer peripheral wall 21b.
  • the orbiting scroll member 22 is composed of a disc-shaped end plate 22a and a spiral spiral wall 22c erected rearward from the end plate 22a, and is erected on the back surface of the end plate 22a.
  • the eccentric shaft 17 provided at the rear end portion of the drive shaft 12 and eccentrically with respect to the shaft center of the drive shaft 12 is supported by the boss portion 22b via the bush 23 and the radial bearing 24. It is provided so that it can revolve around the axis.
  • the fixed scroll member 21 and the orbiting scroll member 22 are meshed with each other with respective spiral walls 21c and 22c.
  • the end plate 21a and the spiral wall 21c of the fixed scroll member 21 and the end plate 22a and the spiral of the orbiting scroll member 22 are engaged with each other.
  • a compression chamber 25 is defined in a space surrounded by the wall 22c.
  • a thin plate-shaped annular thrust trace 26 is sandwiched between the outer peripheral wall 21 b of the fixed scroll member 21 and the partition wall 10, and the fixed scroll member 21 and the partition wall 10 are interposed via the thrust trace 26. It is faced.
  • the thrust trace 26 is formed of a material having excellent wear resistance, and a central hole through which a boss portion 22b of the orbiting scroll member 22 and an Oldham ring 27 described later are inserted is formed in the center.
  • the fixed scroll member 21, the thrust trace 26, and the motor housing housing member 2 b are defined in the radial direction by positioning pins 28 that are inserted into pin insertion holes formed in the thrust trace 26.
  • the shaft support portion 9a formed integrally with the partition wall 10 of the electric motor housing member 2b has a through hole in the center, and the inner surface thereof is formed in a stepwise manner toward the thrust trace 26, From the front side farthest from the thrust trace 26, the bearing housing 31 in which the bearing 13 is housed, is integrally formed with the bush 23, or is externally fitted to the bush so as not to rotate relative to the bush 23.
  • a weight accommodating portion that accommodates a balance weight 32 that rotates with the rotation of the drive shaft 12 (in this example, the balance weight 32 is formed separately from the bush 23 and is fitted on the bush 23 so as not to rotate relative to the bush 23). 33, formed following the weight accommodating portion 33, and prevents the orbiting scroll member 22 from rotating with the orbiting scroll member 22.
  • Oldham Oldham accommodating portion 34 for accommodating the ring 27 is formed that.
  • the orbiting scroll member 22 generates a rotation force by the rotation of the drive shaft 12
  • the orbiting scroll member 22 revolves around the axis of the drive shaft 12 while being restricted by the Oldham ring 27.
  • the suction chamber for sucking the refrigerant introduced from the suction port 40 described later through the suction passage 45. 35 is formed, and behind the fixed scroll member 21 in the housing, the refrigerant gas compressed in the compression chamber 25 is discharged through a discharge hole 36 formed substantially at the center of the fixed scroll member 21.
  • a chamber 37 is defined between the rear end wall of the compression mechanism housing member 2a. The refrigerant gas discharged into the discharge chamber 37 is pumped to an external refrigerant circuit through the discharge port 38.
  • a stator 41 and a rotor 42 constituting the electric motor 4 are provided in the electric motor accommodating portion 15b formed in the front part of the partition wall 10 in the housing 2.
  • the stator 41 includes a cylindrical iron core 43 and a coil 44 wound around the iron core 43, and is fixed to the inner surface of the housing 2 (electric motor housing member 2b).
  • the drive shaft 12 is fixedly mounted with a rotor 42 made of a magnet rotatably accommodated inside the stator 41, and the rotor 42 is rotated by a rotating magnetic force formed by the stator 41. It is designed to rotate.
  • the stator 41 and the rotor 42 constitute an electric motor 4 composed of a brushless DC motor.
  • a suction port 40 for sucking refrigerant gas into the motor housing portion 15b is formed on the side surface of the housing 2 (motor housing housing member 2b), and a gap between the stator 41 and the housing 2 (motor housing housing member 2b).
  • the refrigerant flowing from the suction port 40 into the motor housing portion 15b is guided to the suction chamber 35 through a hole formed in the partition wall 10 and a gap formed between the fixed scroll member 21 and the housing 2.
  • a suction path 45 is configured.
  • the inverter device housed in the inverter housing member 2c is electrically connected to the stator 41 via a terminal (airtight terminal) 60 attached to a through hole 61 formed in the partition wall 11, and is connected to the motor 4. Power is supplied from the inverter device.
  • the orbiting scroll member 22 rotates around the eccentric shaft 17 in the compression mechanism 3. It revolves around the axis of the member 21. At this time, since the orbiting scroll member 22 is prevented from rotating by the rotation preventing mechanism including the Oldham ring 27, only the revolving motion is allowed.
  • the compression chamber 25 moves while gradually reducing the volume from the outer peripheral side of the scroll walls 21c, 22c of both scroll members to the center side, so that the suction chamber 35 sucks into the compression chamber 25.
  • the compressed refrigerant gas is compressed, and the compressed refrigerant gas is discharged into the discharge chamber 37 through the discharge hole 36 formed in the end plate 21 a of the fixed scroll member 21. Then, it is sent to the external refrigerant circuit through the discharge port 38.
  • the bush 23 described above has a columnar shape as shown in FIGS. 2 and 3 and extends in the axial direction at a position shifted in the radial direction from the axial center, and the eccentric shaft. 17 is formed, and a concave portion 23b having a diameter larger than that of the eccentric hole 23a is formed at the end portion on the orbiting scroll member side.
  • a weight fitting allowance 23c for reducing the outer diameter and fitting the balance weight 32 is formed.
  • the balance weight 32 includes an annular fitting portion 32a, and a fan-shaped weight body 32b integrally formed on the periphery of the fitting portion 32a over a predetermined angular range.
  • the fitting portion 32a is externally fitted to the outer periphery of the weight fitting allowance 23c of the bush 23 by, for example, press fitting, and rotates together with the bush 23.
  • This balance weight is formed so as to project closer to the orbiting scroll member and also to extend away from the orbiting scroll member, thereby shortening the radial dimension and preventing interference with the Oldham ring 27. The required mass is secured while avoiding it.
  • the eccentric shaft 17 has a cylindrical shape in which an annular groove 17a is formed in the vicinity of one end, and an annular groove 17a is formed in a fitting hole 12a formed in an end surface of the drive shaft 12 facing the orbiting scroll member 22.
  • the end on the opposite side is press-fitted and fixed, and the end on the annular groove side is inserted into the eccentric hole 23a of the bush 23 so as to be relatively rotatable and protruded into the recessed portion 23b and protruded into the recessed portion 12b.
  • the bush 23 is attached to the portion by fitting the circlip 29 into the annular groove 17a. For this reason, the bush 23 is attached so as to be rotatable relative to the eccentric shaft 17 while restricting movement of the eccentric shaft 17 in the axial direction.
  • the radial bearing 24 fitted in the boss portion 22b of the orbiting scroll member 22 is constituted by a needle bearing in which a large number of needle-like rollers 24a are arranged at equal intervals in the circumferential direction, and the bush 23 is interposed between the outer peripheral surface and the bush 23.
  • a predetermined clearance is provided so as to allow relative rotation.
  • the radial bearing 24 has 14 rollers, the length of the roller portion (the axial fitting length with the outer peripheral surface of the bush 23) is set to 10 mm, and the roller diameter is set to 2.5 mm. Further, the fitting length in the axial direction between the bush and the eccentric shaft is set to 15 mm, and the diameter of the eccentric shaft is set to 6 mm.
  • the radial bearing and the member supported by the radial bearing are in contact with each other in a state as parallel as possible to allow for clearance of the member. Is usually set as small as possible. That is, the radial bearing 24 using a needle bearing is light and compact, but is not suitable for supporting an axial load or a shaft inclination.
  • the common sense in design is to reduce the eccentric load with the needle by suppressing the inclination of the bush by managing to the same.
  • the shaft center of the bush 23 is made eccentric by the centrifugal force of the balance weight 32 (drive shaft 12). ) To be tilted with respect to the axis. For this reason, if the inclination of the bush 23 is compensated by reducing the clearance between the outer peripheral surface of the bush 23 and the radial bearing 24, as described above, the bush 23 is moved to the radial bearing 24 at two different locations in the axial direction. There is an inconvenience that flaking occurs due to a significant increase in the offset load at the abutting portion of the bush 23 on the end where the balance weight 32 of the bush 23 is provided.
  • the present invention as shown in FIG. 5 (a), it is inserted into the eccentric hole 23a in order to reduce the local load (eccentric load) on the end portion side where the balance weight of the bush is provided.
  • the clearance A between the outer peripheral surface of the eccentric shaft 17 and the inner peripheral surface of the eccentric hole 23 a is set to be smaller than the clearance C between the outer peripheral surface of the bush 23 and the inner peripheral surface of the radial bearing 24. Yes.
  • the clearance between the outer peripheral surface of the eccentric shaft 17 and the inner peripheral surface of the eccentric hole 23a provided in the bush 23 is A
  • the clearance between the outer peripheral surface of the eccentric shaft 17 and the inner peripheral surface of the eccentric hole 23a is
  • the fitting length is B
  • the clearance between the outer peripheral surface of the bush 23 and the inner peripheral surface of the radial bearing 24 is C
  • the fitting length between the outer peripheral surface of the bush 23 and the inner peripheral surface of the radial bearing 24 is D.
  • A 6-22 ⁇ m
  • C 24-48 ⁇ m
  • the center of gravity of the balance weight 32 provided at the end of the bush 23 protruding from the radial bearing 24 is displaced from the center of the eccentric shaft 17 (the centrifugal force of the balance weight). 5 acts on the end of the bushing 23 protruding from the radial bearing 24), the axis of the bushing 23 is tilted with respect to the axis of the eccentric shaft 17, as shown in FIG. In this state, the outer peripheral surface of the bush 23 comes into contact with the radial bearing 24, and the centrifugal force of the balance weight 32 acts on the orbiting scroll member 22 via the bush 23 and the radial bearing 24. Offset power.
  • the clearance A between the outer peripheral surface of the eccentric shaft 17 inserted into the eccentric hole 23 a and the inner peripheral surface of the eccentric hole 23 a is between the outer peripheral surface of the bush 23 and the inner peripheral surface of the radial bearing 24. Since the clearance is set to be smaller than the clearance C, the inclination of the bush 23 is regulated by the eccentric shaft 17 (mainly supported by the eccentric shaft 17), and comes into contact with the radial bearing 24 only at one place (the outer periphery of the bush 23). The surface abuts only on the end side where the balance weight 32 is provided, and does not abut on the radial bearing on the end side away from the balance weight 32). For this reason, since F3 (shown in FIG. 9) does not occur, the load F2 acting on the portion that comes into contact with the radial bearing 24 on the end side where the balance weight 32 is provided is not significantly increased. No, it is almost the same size as F1.
  • the inclination of the bush 23 is supported by the outer peripheral surface of the eccentric shaft 17 and the fitting portion of the eccentric hole 23a provided in the bush 23. Therefore, the eccentric shaft 17 and the eccentric hole 23a are supported. However, since the bush 23 does not rotate relative to the eccentric shaft 17, no slip or rolling occurs in the contact portion. There is no risk of flaking or wear.
  • C is managed by processing the outer peripheral surface of the bush 23 according to the dimension of the inner peripheral surface of the radial bearing 24 (so-called matching processing).
  • matching processing is omitted.
  • the balance weight 32 is formed so as to protrude in a direction away from the orbiting scroll member 22, so that it is possible to suppress the length of the balance weight in the radial direction and to rotate the balance weight 32.
  • the balance weight 32 can be provided so as not to interfere with the prevention mechanism (Oldham ring 27). For this reason, an increase in the diameter of the Oldham ring 27 can be avoided, and the outer diameter of the orbiting scroll member can be reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2012/002731 2011-04-22 2012-04-20 スクロール型圧縮機 Ceased WO2012144224A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP12773817.7A EP2713053B1 (en) 2011-04-22 2012-04-20 Scroll compressor
CN201280018752.XA CN103477079B (zh) 2011-04-22 2012-04-20 涡旋型压缩机

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
JP2011-096236 2011-04-22

Publications (1)

Publication Number Publication Date
WO2012144224A1 true WO2012144224A1 (ja) 2012-10-26

Family

ID=47041354

Family Applications (1)

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

Country Status (4)

Country Link
EP (1) EP2713053B1 (OSRAM)
JP (1) JP5594846B2 (OSRAM)
CN (1) CN103477079B (OSRAM)
WO (1) WO2012144224A1 (OSRAM)

Cited By (4)

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Publication number Priority date Publication date Assignee Title
EP2913531A1 (en) * 2014-02-28 2015-09-02 Mitsubishi Heavy Industries, Ltd. Scroll compressor with balance weight
EP3109474A4 (en) * 2013-10-25 2018-01-17 Valeo Japan Co., Ltd. Electric scroll compressor
CN111089055A (zh) * 2018-10-23 2020-05-01 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
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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* Cited by examiner, † Cited by third party
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JP6149429B2 (ja) 2013-03-06 2017-06-21 株式会社豊田自動織機 スクロール型圧縮機
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
EP3193020B1 (en) * 2014-09-10 2019-06-05 Hitachi Industrial Equipment Systems Co., Ltd. Scroll fluid machine
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
JP7017485B2 (ja) * 2018-08-13 2022-02-08 三菱重工サーマルシステムズ株式会社 スクロール圧縮機
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
KR102503234B1 (ko) * 2018-11-30 2023-02-24 한온시스템 주식회사 스크롤 압축기
GB2583373A (en) * 2019-04-26 2020-10-28 Edwards Ltd Scroll pump crank sleeve
CN211598997U (zh) 2020-01-21 2020-09-29 艾默生环境优化技术(苏州)有限公司 一种涡旋压缩机
DE102020211559A1 (de) 2020-09-15 2022-03-17 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Scrollverdichter
TWI853669B (zh) * 2023-08-11 2024-08-21 復盛股份有限公司 壓縮機

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0842467A (ja) 1995-06-23 1996-02-13 Mitsubishi Electric Corp スクロール圧縮機
JPH0842477A (ja) 1994-07-27 1996-02-13 Toyota Autom Loom Works Ltd スクロール型圧縮機
JPH11141472A (ja) * 1997-11-11 1999-05-25 Daikin Ind Ltd スクロール型流体機械
JPH11236886A (ja) * 1997-12-03 1999-08-31 Sanden Corp スクロール型圧縮機
JP2010196630A (ja) 2009-02-26 2010-09-09 Denso Corp 圧縮機

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6015277A (en) * 1997-11-13 2000-01-18 Tecumseh Products Company Fabrication method for semiconductor substrate
EP0921316A1 (en) * 1997-12-03 1999-06-09 Sanden Corporation Scroll compressor with radial guiding pin in eccentric bush
JP2001093554A (ja) * 1999-09-28 2001-04-06 Toyota Autom Loom Works Ltd 燃料電池用圧縮回生機
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

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0842477A (ja) 1994-07-27 1996-02-13 Toyota Autom Loom Works Ltd スクロール型圧縮機
JPH0842467A (ja) 1995-06-23 1996-02-13 Mitsubishi Electric Corp スクロール圧縮機
JPH11141472A (ja) * 1997-11-11 1999-05-25 Daikin Ind Ltd スクロール型流体機械
JPH11236886A (ja) * 1997-12-03 1999-08-31 Sanden Corp スクロール型圧縮機
JP2010196630A (ja) 2009-02-26 2010-09-09 Denso Corp 圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2713053A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3109474A4 (en) * 2013-10-25 2018-01-17 Valeo Japan Co., Ltd. Electric scroll compressor
EP2913531A1 (en) * 2014-02-28 2015-09-02 Mitsubishi Heavy Industries, Ltd. Scroll compressor with balance weight
CN111089055A (zh) * 2018-10-23 2020-05-01 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
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

Also Published As

Publication number Publication date
CN103477079B (zh) 2016-01-20
EP2713053A4 (en) 2014-11-26
CN103477079A (zh) 2013-12-25
JP2012225328A (ja) 2012-11-15
JP5594846B2 (ja) 2014-09-24
EP2713053A1 (en) 2014-04-02
EP2713053B1 (en) 2016-04-13

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