EP2921706B1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
EP2921706B1
EP2921706B1 EP13862467.1A EP13862467A EP2921706B1 EP 2921706 B1 EP2921706 B1 EP 2921706B1 EP 13862467 A EP13862467 A EP 13862467A EP 2921706 B1 EP2921706 B1 EP 2921706B1
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EP
European Patent Office
Prior art keywords
balance weight
scroll
orbiting scroll
main shaft
oldham ring
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.)
Active
Application number
EP13862467.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2921706A4 (en
EP2921706A1 (en
Inventor
Shunsuke Yakushiji
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems 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 Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP2921706A1 publication Critical patent/EP2921706A1/en
Publication of EP2921706A4 publication Critical patent/EP2921706A4/en
Application granted granted Critical
Publication of EP2921706B1 publication Critical patent/EP2921706B1/en
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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
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/066—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with an intermediate piece sliding along perpendicular axes, e.g. Oldham coupling
    • 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
    • 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
    • F04C29/0042—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

Definitions

  • the present invention relates to a scroll compressor and in particular, to a scroll compressor in which vibration due to the movement of an Oldham ring that prevents an orbiting scroll from rotating is suppressed.
  • a scroll compressor which is used in an air conditioner or a refrigeration unit is provided with a stationary scroll and an orbiting scroll each having a spiral scroll wall. Then, the orbiting scroll performs revolving motion without rotating with respect to the stationary scroll, and thus the volume of a compression chamber which is formed between the scroll walls of the two is reduced, whereby a refrigerant in the compression chamber is compressed.
  • an Oldham ring is interposed between the orbiting scroll and a housing which supports the orbiting scroll.
  • the Oldham ring linearly reciprocates, as is well known, and therefore, it becomes a source of generation of an excitation force which causes the entire compressor to vibrate in a direction. In a case where a rotation speed of the compressor is low, the excitation force is also allowable. However, if it becomes high-speed rotation, vibration and noise become significant.
  • PTL 1 proposes an Oldham coupling in which a pair of ring members (a ring member which is disposed outside and a ring member which is disposed on the inside thereof) is provided and the respective ring members are disposed with the same mass and on the same plane such that a resultant force of the individual ring members which linearly reciprocate becomes the same centrifugal force as a centrifugal force which is generated by the revolution of an orbiting scroll.
  • vibration which is generated due to the motion of the pair of ring members is regarded as being able to be reduced by a conventional balance weight or counterweight and a reduction of noise of a device as a whole and avoidance of an adverse effect on equipment on the inside of the device are regarded as being able to be achieved.
  • a resultant force of the outer ring member and the inner ring member (the new balance weight) is applied in the same direction as a direction in which a centrifugal force of the orbiting scroll acts, and thus a tooth surface load of the orbiting scroll is increased by an amount corresponding to the resultant force, and therefore, it can become a new source of generation of vibration and noise, and uneasiness occurs in terms of the strength of the orbiting scroll itself or a stationary scroll.
  • the present invention has been made based on such technical problems and has an object to provide a scroll compressor which is provided with an Oldham coupling which enables a new balance weight which is used along with an Oldham ring to move in an arbitrary direction independently of the movement of an orbiting scroll.
  • the present invention is defined by claim 1.
  • a new balance weight is moved by using an eccentric cam which is provided in an eccentric bushing of a main shaft which drives an orbiting scroll.
  • an angle at which the eccentric cam is provided can be arbitrarily set, it is possible to move the new balance weight (a second balance weight) in an arbitrary direction independently of the movement of the orbiting scroll.
  • a scroll compressor is provided with a main shaft which is provided with an eccentric bushing and rotationally driven by a driving source, an orbiting scroll which is rotatably connected to the eccentric bushing of the main shaft, and a stationary scroll which faces the orbiting scroll, thereby forming a compression chamber which compresses a refrigerant, and has, at an end plate, a port which discharges the compressed refrigerant toward a high-pressure chamber.
  • the scroll compressor according to the present invention is provided with an Oldham ring which restricts movement of the orbiting scroll such that the orbiting scroll revolves without rotating with respect to the stationary scroll, a first balance weight which turns along with the eccentric bushing, an eccentric cam which turns along with the eccentric bushing, and a second balance weight which linearly reciprocates through the eccentric cam by rotational drive of the main shaft.
  • the first balance weight to function as the eccentric cam, dispose the second balance weight in the same plane on the inside of the Oldham ring, and make a direction of reciprocating linear motion of the Oldham ring and a direction of reciprocating linear motion of the second balance weight be orthogonal to each other.
  • the present invention is not limited to a form of causing the first balance weight to function as the eccentric cam, and it is possible to provide an eccentric cam separately from the first balance weight.
  • the eccentric cam can be provided at a different position of a rotation angle from the first balance weight. This suggests that it is possible to provide the eccentric cam at an arbitrary rotation angle.
  • the second balance weight is disposed inside the Oldham ring.
  • the rotation of the main shaft moves the second balance weight 50 through the eccentric cam which is provided at the eccentric bushing.
  • the eccentric cam can be mounted at an arbitrary angle on the eccentric bushing. Therefore, according to this embodiment, a direction in which the second balance weight linearly reciprocates can be arbitrarily set. For example, according to the present invention, it is possible to move the second balance weight in a direction opposite to a direction in which a centrifugal force of the orbiting scroll is generated.
  • a vertical type scroll compressor 10 is provided with a main shaft 12, an orbiting scroll 20 which rotates along with the main shaft 12, and a stationary scroll 30 fixed to a housing 11, on the inside of the housing 11.
  • a refrigerant is introduced from a refrigerant introduction port P1 formed in the housing 11 into the housing 11, and the refrigerant is compressed in a compression chamber which is formed between the orbiting scroll 20 and the stationary scroll 30. Then, the compressed refrigerant is discharged from a refrigerant discharge port P2 formed in the housing 11.
  • a spiral wrap wall 22 having a predetermined height is integrally formed at a disk-shaped end plate 21.
  • the orbiting scroll 20 is supported on a bearing 14 of the housing 11 through an Oldham ring 40 (described later).
  • a spiral wrap wall 32 facing and meshed with the wrap wall 22 of the orbiting scroll 20 is formed at an end plate 31 facing the orbiting scroll 20.
  • the refrigerant introduced from the outer periphery sides of the orbiting scroll 20 and the stationary scroll 30 into the compression chamber PR is compressed by being sequentially sent from the outer periphery side to the inner periphery side by the revolving motion of the orbiting scroll 20 with respect to the stationary scroll 30.
  • the refrigerant compressed in the compression chamber PR is discharged from the refrigerant discharge port P2 formed on the other end side of the housing 11 through a discharge hole 37 formed in the stationary scroll 30, a reed valve 38 provided in the discharge hole 37, and a reed valve 38 provided at an upper cover 39 provided so as to cover the stationary scroll 30.
  • the main shaft 12 is rotatably supported, at both end portions thereof, on the housing 11 through bearings 13 and 14.
  • the main shaft 12 is rotationally driven by a motor 17 composed of a stator 15 fixed to the inner surface of the housing 11 and a rotor 16 fixed to the outer peripheral surface of the main shaft 12 and facing the stator 15.
  • the main shaft 12 may have a configuration in which one end penetrates the housing 11, thereby protruding to the outside, and a driving source (not shown) such as an engine or a motor provided outside is connected to the one end of the main shaft 12, whereby the main shaft 12 is rotationally driven.
  • an eccentric bushing 18 is formed to protrude at a position eccentric by a predetermined dimension from a central axis of the main shaft 12.
  • a concave portion 23 accommodating the eccentric bushing 18 is formed.
  • the eccentric bushing 18 is inserted into the concave portion 23 through a drive bushing (a bearing) 24, whereby the orbiting scroll 20 is rotatably retained on the eccentric bushing 18.
  • the orbiting scroll 20 is provided to be eccentric by a predetermined dimension with respect to the center of the main shaft 12, and thus, if the main shaft 12 rotates around its axis, the orbiting scroll 20 performs a rotation (a revolution) with a dimension eccentric with respect to the center of the main shaft 12 as a radius.
  • the Oldham ring 40 is interposed between the orbiting scroll 20 and the main shaft 12 such that the orbiting scroll 20 does not rotate even while revolving.
  • the Oldham ring 40 is composed of a main body 41 having an annular shape, a pair of upper claws 43 which is provided at positions facing each other across the center of the main body 41 on the upper surface of the main body 41, and a pair of lower claws 45 which is provided on the lower surface at positions shifted by 90° in a circumferential direction of the main body 41 with respect to the upper claws 43, as shown in Fig. 2 .
  • the upper side as referred to herein means a side facing the orbiting scroll 20. The same applies to the following.
  • the main shaft 12 is provided with a first balance weight 25.
  • the first balance weight 25 is for balancing dynamic unbalance due to the revolving motion of the orbiting scroll 20 and is disposed at and fixed to the main shaft 12 symmetrically to the eccentric bushing 18, that is, so as to rotate with a phase shifted by 180 degrees with respect to the revolving motion of the orbiting scroll 20.
  • the first balance weight 25 is composed of a connection piece 25a which is fixed to the eccentric bushing 18 of the main shaft 12 and has an approximate fan shape in a plan view, as shown in Figs. 4(a) to 4(d) , and a main body 25b which is provided to be erect upward from the connection piece 25a.
  • a guide surface 25c of the outer periphery thereof has an arc shape in a plan view.
  • the guide surface 25c acts on a second balance weight 50 (described next) from the inside of a cam groove 53 of the second balance weight 50, thereby being able to drive the second balance weight 50.
  • a lubricating oil flow path 12a for supplying lubricating oil sucked up from an oil reservoir of a bottom portion of the housing 11 from an upper end portion of the main shaft 12 to the drive bushing 24 between the main shaft 12 and the concave portion 23 is formed.
  • the main shaft 12 is provided with the second balance weight 50.
  • the second balance weight 50 is for balancing dynamic unbalance due to the reciprocating linear motion of the Oldham ring 40 and performs reciprocating linear motion in a direction orthogonal to a movement direction of the Oldham ring 40 according to the rotation of the first balance weight 25. For this reason, the second balance weight 50 is disposed around the first balance weight 25.
  • the second balance weight 50 is provided with a main body 51 having a rectangular shape in a plan view, the cam groove 53 having a rounded rectangular shape and penetrating the front and the back at the center of the main body 51, and a pair of lower claws 55 which is provided at positions facing each other across the center of the main body 51 on the lower surface of the main body 51, as shown in Fig. 3 .
  • the cam groove 53 has a major axis formed along a short side direction (or a width direction) of the main body 61, and the pair of lower claws 55 is formed at both end portions of the main body 51 along a longitudinal direction (or a length direction) of the main body 51.
  • the pair of lower claws 55 is slidably fitted into the pair of guide grooves which is formed in the bearing 14, and therefore, even if the second balance weight 50 is applied with a driving force, a direction of the motion thereof is restricted so as to follow the longitudinal direction of the main body 51.
  • the guide grooves are common to the guide grooves for the Oldham ring 40.
  • the first balance weight 25 is accommodated in the cam groove 53. If the first balance weight 25 performs turning motion according to the rotation of the main shaft 12, the guide surface 25c acts on the second balance weight 50 from the inside of the cam groove 53, thereby being able to drive the second balance weight 50.
  • the lower claws 55 are slidably fitted into the guide grooves, and therefore, the second balance weight 50 linearly reciprocates along the longitudinal direction of the main body 51.
  • the main shaft 12 rotates about the shaft center.
  • the eccentric bushing 18 revolves with respect to the shaft center of the main shaft 12.
  • the orbiting scroll 20 with which the eccentric bushing 18 is linked revolves with respect to the stationary scroll 30 due to rotation being prevented by the Oldham ring 40. Due to this, the respective contact places between the wrap walls 22 and 32 of the scrolls 20 and 30 move toward a central portion of a scroll mechanism, and accordingly, the compression chamber PR is shrunk while spirally moving toward the central portion. Due to a series of these operations, low-pressure refrigerant gas flows from the refrigerant introduction port P1 into the compression chamber PR. Then, the refrigerant having flowed into the compression chamber PR is compressed to high pressure and reaches a central portion of the compression chamber PR, and is then discharged from the refrigerant discharge port P2 through the discharge hole 37.
  • the lubricating oil pumped up by an oil feed pump (illustration is omitted) is supplied to a radial bearing on the outer periphery side of the main shaft 12 or a thrust bearing of the upper end portion of the main shaft 12 by way of the lubricating oil flow path 12a and lubricates a sliding portion of the main shaft 12 or the orbiting scroll 20.
  • the Oldham ring 40 interposed between the orbiting scroll 20 and the bearing 14 slides in a right-left direction in Fig. 1 , that is, a direction (a first direction) orthogonal to the axis of the main shaft 12, according to the revolution motion of the orbiting scroll 20 described above, thereby generating an excitation force which causes the compressor 10 to vibrate in the slide direction.
  • the second balance weight 50 which is disposed inside the Oldham ring 40 slides in a direction perpendicular to the plane of Fig. 1 , that is, a direction (a second direction) orthogonal to an axial direction of the main shaft 12 and the first direction, thereby generating an excitation force which causes the compressor 10 to vibrate in the slide direction.
  • a direction (a second direction) orthogonal to an axial direction of the main shaft 12 and the first direction thereby generating an excitation force which causes the compressor 10 to vibrate in the slide direction.
  • An example of an operation of the second balance weight 50 is shown in Figs. 4(a) to 4(d) and 5(a) to 5(d) .
  • the first balance weight 25 turns with the central axis of the eccentric bushing 18 as a rotation axis. Then, the first balance weight 25 acts on the second balance weight 50 from the inside of the cam groove 53, thereby turning the second balance weight 50. That is, apparently, the second balance weight 50 performs reciprocating motion in up-down and right-left directions in the drawing with the rotation axis of the main shaft 12 as the center. However, as described above, the pair of lower claws 55 of the second balance weight 50 is fitted into the pair of guide grooves formed in the bearing 14.
  • a rotation angle in Figs. 4(a) to 4(d) and 5(a) to 5(d) refers to a rotation angle of the eccentric bushing 18, and the definition of the rotation angle of 0° will be described later.
  • the second balance weight 50 is displaced in a rightward direction as well as an upward direction as the eccentric bushing 18 rotates in the clockwise direction, and if the rotation angle reaches 90°, the second balance weight 50 is shifted to the uppermost side. With respect to the right-left direction, the second balance weight 50 is located at the center of a displacement stroke. The Oldham ring 40 is located at the center of a displacement stroke with respect to the right-left direction.
  • the second balance weight 50 begins to be displaced in a downward direction and is displaced in the rightward direction, and if the rotation angle reaches 180°, with respect to the up-down direction, the second balance weight 50 is located at the center of the displacement stroke.
  • the Oldham ring 40 is located on the leftmost side.
  • the second balance weight 50 continues to be displaced in the downward direction and the rightward direction, and if the rotation angle reaches 270°, with respect to the up-down direction, the second balance weight 50 is located near the lowermost side.
  • the Oldham ring 40 is located at the center of the displacement stroke in the right-left direction.
  • the second balance weight 50 returns to the state in which the rotation angle is 0° ( Fig. 6(a) ).
  • the Oldham ring 40 and the second balance weight 50 which is disposed on the inside thereof linearly reciprocate in directions (respectively referred to as an X direction and a Y direction) orthogonal to each other.
  • the Oldham ring 40 and the second balance weight 50 can be regarded as being located on the same plane and mass is set to be equal to each other. Therefore, excitation forces (referred to as F 40 and F 50 ) in the X direction and the Y direction by each of the Oldham ring 40 and the second balance weight 50 are the same, and the resultant force thereof acts on the entire device.
  • both of the excitation forces respectively increase and decrease according to the amount of displacement in the X direction and the amount of displacement in the Y direction of the orbiting scroll 20, and the respective excitation forces F 40 and F 50 sinusoidally change according to slide movements (the respective movements in the X direction and the Y direction) of the Oldham ring 40 and the second balance weight 50.
  • the resultant force of the excitation forces F 40 and F 50 acts as a certain centrifugal force.
  • the Oldham ring 40 and the second balance weight 50 are provided in a pair inside and outside, whereby forces which are generated according to the respective movements of the Oldham ring 40 and the second balance weight 50 can be treated in the same manner as a centrifugal force which is generated according to the rotation of the orbiting scroll 20.
  • a direction of a centrifugal force which is generated by the resultant force occurs in the same direction as a centrifugal force which is generated by the revolution of the orbiting scroll 20.
  • the mass of the first balance weight 25 it is possible to offset the centrifugal force due to the movements of the Oldham ring 40 and the second balance weight 50.
  • the mass of the first balance weight 25 is set to be slightly large, as compared to a case where the second balance weight 50 is not provided.
  • the second balance weight 50 is provided in addition to the Oldham ring 40 and the first balance weight 25, and thus the resultant force of the Oldham ring 40 and the second balance weight 50 which linearly reciprocate becomes the same centrifugal force as the centrifugal force which is generated by the revolution of the orbiting scroll 20.
  • the compressor 10 can reduce vibration according to an operation of the Oldham ring 40.
  • a role as an eccentric cam for driving the second balance weight 50 is given to the first balance weight 25.
  • an eccentric cam 60 can also be provided at the eccentric bushing 18.
  • the eccentric cam 60 has the same shape as the first balance weight 25.
  • a mounting angle on the eccentric bushing 18 is different from that of the first balance weight 25. That is, the first balance weight 25 is provided in a direction opposite to the direction of the eccentricity of the orbiting scroll 20 by 180 degrees.
  • the eccentric cam 60 can be mounted on the eccentric bushing 18 at an arbitrary angle with respect to the orbiting scroll 20.
  • the rotation of the main shaft 12 moves the second balance weight 50 through the eccentric cam (the first balance weight 25 or the eccentric cam 60) provided at the eccentric bushing 18.
  • the eccentric cam can be mounted at an arbitrary angle on the eccentric bushing 18. Therefore, according to this embodiment, a direction in which the second balance weight 50 performs reciprocating linear motion can be arbitrarily set. For example, it is possible to move the second balance weight 50 in a direction opposite to a direction in which the centrifugal force of the orbiting scroll 20 is generated.
  • a reciprocating movement distance (a stroke amount) of the second balance weight 50 can be arbitrarily set. That is, according to this embodiment, the stroke amount can be arbitrarily set by changing the eccentricity amount of the eccentric cam (the first balance weight 25 or the eccentric cam 60). This suggests that it is possible to arbitrarily set the mass of the second balance weight 50.
  • the inertia force of the second balance weight 50 in order to make the inertia force of the second balance weight 50 be equivalent to the inertia force of the Oldham ring 40, it is favorable if any one of the eccentricity amount and the mass is adjusted. For example, while the mass of the second balance weight 50 is reduced, the eccentricity amount is increased, alternatively, while the mass of the second balance weight 50 is increased, the eccentricity amount is reduced, whereby it is possible to obtain a necessary inertia force.
  • the scroll compressor in which the motor 17 which is a driving source of a compression mechanism is mounted on the inside of the housing 11 has been taken as an example.
  • the present invention can be applied to a scroll compressor in which a driving source of a compression mechanism is provided outside the housing 11.
EP13862467.1A 2012-12-14 2013-09-03 Scroll compressor Active EP2921706B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012272959A JP6066708B2 (ja) 2012-12-14 2012-12-14 スクロール型圧縮機
PCT/JP2013/005194 WO2014091641A1 (ja) 2012-12-14 2013-09-03 スクロール型圧縮機

Publications (3)

Publication Number Publication Date
EP2921706A1 EP2921706A1 (en) 2015-09-23
EP2921706A4 EP2921706A4 (en) 2016-03-16
EP2921706B1 true EP2921706B1 (en) 2019-03-20

Family

ID=50933956

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Application Number Title Priority Date Filing Date
EP13862467.1A Active EP2921706B1 (en) 2012-12-14 2013-09-03 Scroll compressor

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EP (1) EP2921706B1 (ja)
JP (1) JP6066708B2 (ja)
WO (1) WO2014091641A1 (ja)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106574612B (zh) * 2014-07-31 2018-11-09 日立汽车系统株式会社 往复式压缩机
US9790942B2 (en) 2015-08-21 2017-10-17 Honeywell International Inc. Low vibration scroll compressor for aircraft application
WO2017199435A1 (ja) * 2016-05-20 2017-11-23 三菱電機株式会社 スクロール圧縮機

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61261689A (ja) * 1985-05-15 1986-11-19 Matsushita Electric Ind Co Ltd スクロ−ル圧縮機
US5017107A (en) * 1989-11-06 1991-05-21 Carrier Corporation Slider block radial compliance mechanism
JPH0826761B2 (ja) * 1989-12-25 1996-03-21 三菱電機株式会社 スクロール流体機械
JP2818023B2 (ja) * 1990-06-27 1998-10-30 株式会社日立製作所 スクロール圧縮機
JP3211593B2 (ja) * 1994-12-02 2001-09-25 ダイキン工業株式会社 スクロール型流体装置
JPH08261165A (ja) * 1995-03-23 1996-10-08 Matsushita Electric Ind Co Ltd スクロール圧縮機
JPH10122164A (ja) * 1996-10-18 1998-05-12 Mitsubishi Heavy Ind Ltd オルダムリング機構及びそれを用いたスクロール型流体機械

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JP6066708B2 (ja) 2017-01-25
JP2014118847A (ja) 2014-06-30
EP2921706A4 (en) 2016-03-16
WO2014091641A1 (ja) 2014-06-19
EP2921706A1 (en) 2015-09-23

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