EP3315777B1 - Scroll compressor and method for producing scroll compressor - Google Patents

Scroll compressor and method for producing scroll compressor Download PDF

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Publication number
EP3315777B1
EP3315777B1 EP16861893.2A EP16861893A EP3315777B1 EP 3315777 B1 EP3315777 B1 EP 3315777B1 EP 16861893 A EP16861893 A EP 16861893A EP 3315777 B1 EP3315777 B1 EP 3315777B1
Authority
EP
European Patent Office
Prior art keywords
rotary shaft
harness
axis
housing
scroll compressor
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
EP16861893.2A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3315777A4 (en
EP3315777A1 (en
Inventor
Yogo Takasu
Hajime Sato
Kazuki Takahashi
Yoshiyuki Kimata
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 EP3315777A1 publication Critical patent/EP3315777A1/en
Publication of EP3315777A4 publication Critical patent/EP3315777A4/en
Application granted granted Critical
Publication of EP3315777B1 publication Critical patent/EP3315777B1/en
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Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • F01C21/007—General arrangements of parts; Frames and supporting elements
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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

Definitions

  • the present invention a scroll compressor, and a method of producing the scroll compressor.
  • the scroll compressor includes a main axis that is rotationally driven by an electric motor, an eccentric shaft that is provided on a position offset with respect to the main axis, and an orbiting scroll that is supported on the eccentric shaft via a bearing device, a fixed scroll that forms a compression chamber variable in volume by facing an orbiting scroll, and a housing that houses the above members.
  • the orbiting scroll performs orbiting motion centering on an axis of the main axis, without rotation. As a result, the fluid introduced into the compression chamber is compressed.
  • the above main axis and eccentric shaft are supported on both sides in an axial direction of the main axis by a main bearing (upper bearing) provided inside the housing, and a sub bearing (lower bearing).
  • Patent Document 1 As a specific example of such the scroll compressor, an apparatus described in the following Patent Document 1 is known.
  • a second frame supporting the main axis from below is fixed by a spot welding with respect to an inner peripheral surface of an attachment via a plurality of ribs.
  • Patent Document 2 relates to a hermetic compressor and refrigeration cycle equipment using the same.
  • Patent Document 3 relates to a compressor having a counterweight shield.
  • Patent Document 4 relates to a support member for optimizing dynamic load distribution and attenuating vibration.
  • Patent Document 5 relates to a scroll compressor.
  • the orbiting scroll performs an orbiting motion about the axis of the main axis as the center by the eccentric shaft that is offset relative to the main axis as described above, and compressing a refrigerant gas. Therefore, the main bearing and the sub bearing are continuously subjected to a load caused by reaction force of the refrigerant compressor and moment caused by members, such as a rotor balance weight, for adjusting a balance during rotation. Furthermore, in association with enlargement in capacity and augmentation in output of the scroll compressor which has been conducted in recent years, the load also tends to increase.
  • the present invention has been made in view of such circumstances, and an object thereof is to provide a scroll compressor capable of stable operation.
  • the present invention employs the means of claim 1 or claim 3.
  • the scroll compressor 100 includes a housing 1 forming the outer shape of the device, and a drive unit 3 (an electric motor 3) provided in the housing 1, a rotary shaft 4 rotationally driven by the drive unit 3, a compression unit 2 (a scroll compressor body 2) driven by a rotation of the rotary shaft 4, a main bearing 9A and a sub bearing 9B rotatably supporting the rotary shaft 4, a harness 40 fitted within the housing 1, and a fixed portion (a bolt B, see FIG. 2 ) configured to fix the sub bearing 9B to the harness 40.
  • a drive unit 3 an electric motor 3
  • a rotary shaft 4 rotationally driven by the drive unit 3
  • a compression unit 2 (a scroll compressor body 2) driven by a rotation of the rotary shaft 4
  • a main bearing 9A and a sub bearing 9B rotatably supporting the rotary shaft 4
  • a harness 40 fitted within the housing 1
  • a fixed portion a bolt B, see FIG. 2
  • the compression unit 2 and the drive unit 3 are connected to each other by the rotary shaft 4 extending along an axis O1. That is, rotational energy by the drive unit 3 is transmitted immediately to the compression unit 2 through the rotary shaft 4.
  • the compression unit 2 compresses a working fluid by this rotational energy and discharges it to the outside in a high pressure state.
  • the working fluid in a high pressure state is used, for example, as a refrigerant in air conditioners and the like.
  • the housing 1 is provided with a suction pipe 11 for sucking a refrigerant gas as the working fluid from the outside, and a discharge pipe 12 for discharging the refrigerant gas that is in a high pressure state in a discharge chamber 67 after being compressed by the compression unit 2.
  • the rotary shaft 4 has a columnar shape centering on the axis O1.
  • the rotary shaft 4 rotatably supported within the housing 1 by the main bearing 9A provided at an end portion (first end portion) on one side of the rotary shaft 4 in an axis O1 direction and the sub bearing 9B provided at the other end portion (second end portion) on the other side of the rotary shaft 4 which is the opposite side in the axis O1 direction when viewed from the main bearing 9A.
  • the main bearing 9A has a main bearing body 75 which rotatably supports the rotary shaft 4.
  • an eccentric shaft 5 having a columnar shape and centering on an eccentric axis O2 that is different from the axis O1 is provided at an offset (eccentric) position with respect to the axis O1.
  • the eccentric axis O2 is parallel to the axis O1.
  • the eccentric shaft 5 has a columnar shape protruding from the end portion of the rotary shaft 4 toward the one side in the axis O1 direction. Accordingly, in a state in which the rotary shaft 4 is rotating about the axis O1, the eccentric shaft 5 revolves around the axis O1 of the rotary shaft 4.
  • the fixed scroll 6 is a member having a substantially disc shape and fixed inside the housing 1.
  • the orbiting scroll 7 faces the fixed scroll 6 from the axis O1 direction to form a compression chamber C therebetween.
  • the fixed scroll 6 includes an end plate 61 having a disc shape, and a fixed wrap 62 erected on a surface of the other side in the axis O1 direction of the end plate 61 from the one side toward the other side in the axis O1 direction.
  • the end plate 61 extends along a plane substantially perpendicular to the axis O1.
  • the fixed wrap 62 is a wall body which is formed in a spiral shape when viewed from the axis O1 direction.
  • an outer peripheral wall 63 extending in a tubular shape along an outer periphery of the end plate 61 is formed. Further, on an edge at the other side in the axis O1 direction of the outer peripheral wall 63, a flange 64 having an annular shape and extending outward in a radial direction is provided.
  • the fixed scroll 6 is fixed to the main bearing 9A by bolts or the like via the flange 64. Furthermore, a fixed scroll discharge port 65 is formed in a center portion of the spiral of the fixed scroll 6 is.
  • the orbiting scroll 7 includes the end plate 71 having the disc shape, and the orbiting wrap 72 having a spiral shape and provided on a surface on one side in the axis O1 direction in the end plate 71.
  • the orbiting wrap 72 may also desirably be configured to form an involute curve centering on the axis O2.
  • the orbiting wrap 72 faces the fixed wrap 62 from the axis O1 direction and is disposed so as to overlap each other in a direction intersecting with the axis O1.
  • the fixed wrap 62 and the orbiting wrap 72 are engaged with each other.
  • a predetermined space is formed between the fixed wrap 62 and the orbiting wrap 72.
  • the volume of this space varies while the orbiting wrap 72 orbits. Thereby, it is possible to compress the refrigerant gas.
  • the orbiting scroll 7 configured as described above is connected to one side in the axis O1 direction of the above rotary shaft 4 via a bushing assembly 10.
  • a boss 73 having a cylindrical shape is formed on a surface at the other side in the axis O1 direction of the end plate 71 of the orbiting wrap 72.
  • a central axis of the boss 73 is coaxial with the axis O2.
  • the eccentric shaft 5 formed on the rotary shaft 4 is fitted into an internal space of the boss 73 from the axis O1 direction through the bushing assembly 10.
  • lubricant oil is supplied to the rotary shaft 4 (the eccentric shaft 5) from a lubrication pump 80. After lubricating a portion between the bush 101 of the bushing assembly 10 and the bearing 74 of the orbiting scroll 7, the lubricating oil is collected downwardly in the housing 1.
  • the sub bearing 9B includes a sub-bearing body 76, a holder 78 having a tubular shape and supporting the sub-bearing body 76 from the outer peripheral side of the sub-bearing body 76, and a plurality (three) of arms 79 that extends radially so that the holder 78 is provided as a center.
  • the holder 78 is provided at a position substantially coaxial with the axis O1.
  • the arm 79 is a rod-like member that connects an inner peripheral surface 1A of the housing 1 and an outer peripheral surface of the holder 78.
  • the three arms 79 in the present embodiment have substantially the same shape and size with each other.
  • the end portion (an outer peripheral end 79A) at the outer side in the radial direction of the arm 79 has a first hole 79H through which a fastening bolt B is inserted.
  • the first hole 79H has an inner diameter that is slightly larger than a shaft diameter of the fastening bolt B. That is, when the fastening bolt B is inserted into the first hole 79H, a slight gap is formed between the outer peripheral surface of the fastening bolt B and an inner peripheral surface of the first hole 79H.
  • the harness 40 is fixed to the inner peripheral surface of the housing 1 by shrink fitting. More specifically, the harness 40 is fixed to the housing 1 by the following method (a method for producing the scroll compressor). The method includes an assembling process, a shrink fitting process, and a fixation process. In the assembling process, the electric motor 3 (the drive unit 3), the rotary shaft 4, the scroll compressor body 2 (the compression unit 2), and the main bearing 9A are housed within the housing 1. Then, in the shrink fitting process, the harness 40 is fixed by shrink fitting with respect to the inner peripheral surface of the housing 1.
  • the harness 40 is formed line-symmetrically with respect to an object axis Os extending in a horizontal plane that intersects the axis O1. Further, when viewed from the axis O1 direction, an outer peripheral portion of the harness 40 is cut out at four portions and the four portions are respectively defined as a cutout portion 41. These four cutout portions 41 are respectively defined as a first cutout 41A and a second cutout 41B which are line symmetrical with respect to the object axis Os described above.
  • the first cutout 41A has a curved edge that curves radially inward from the outer peripheral edge (outer peripheral side) of the harness 40, when viewed from the axis O1 direction.
  • the second cutout 41B is a straight edge forming a chord of the harness 40.
  • the harness 40 has a plurality of second holes 40H for fixing the arms 79 of the sub bearing 9B. More specifically, each of the second holes 40H is formed at a position corresponding to the first hole 79H formed in each of the three the arms 79, when viewed from the axis O1 direction.
  • the bolt B is inserted so as to penetrate both the first hole 79H and the second hole 40H and is fastened by a nut or the like.
  • the harness 40 in the state of being fixed in the housing 1, the harness 40 is in a state of substantially abutting the drive unit 3 (the electric motor 3) described above from the axis O1 direction.
  • an inner diameter of the first hole 79H formed in the arm 79 is slightly larger than the shaft diameter of the bolt B.
  • the sub bearing 9B has a room for slightly pivots around the axis O1 with respect to the harness 40.
  • a central axis of the sub bearing 9B (the sub-bearing body 76) is possible to be matched with respect to the axis O1 of the housing 1 (the rotary shaft 4).
  • the sub bearing 9B is capable of carrying out centering with respect the axis O1.
  • the eccentric shaft 5 described above revolves around the axis O1, and the orbiting scroll 7 attached thereto orbits the axis O1 as the center.
  • the rotation of the orbiting scroll 7 is restricted by the Oldham ring 91 described above. Therefore, the orbiting scroll 7 performs a circular motion (orbits) along a locus drawn by the eccentric axis O2 so that the axis O1 of the rotary shaft 4 is provided as a center.
  • the orbiting wrap 72 of the orbiting scroll 7 repeats a continuous relative movement relative to the fixed wrap 62 of the fixed scroll 6. Due to this relative movement, the volume of the compression chamber C formed between the fixed wrap 62 and orbiting wrap 72 varies with time.
  • the refrigerant gas as the working fluid is introduced into the compression chamber C from an opening created at an outside in the radial direction of the orbiting wrap 72 (and the fixed wrap 62).
  • the opening described above is closed.
  • the refrigerant gas is confined within the compression chamber C.
  • the orbiting scroll 7 still orbits, the refrigerant gas moves radially inward (i.e., the eccentric axis O2 side).
  • the orbiting wrap 72 and the fixed wrap 62 are formed in the spiral shape as described above, the volume of the compression chamber C formed by the both is contracted gradually toward the inner side in the radial direction.
  • the refrigerant gas is compressed.
  • the refrigerant gas reaches the maximum pressure, and then is supplied to the outside through the above fixed scroll discharge port 65 and the discharge pipe 12 of the housing 1.
  • the arm 79 in the sub bearing 9B is directly fixed to the inner peripheral surface of the housing 1 by for example welding, the arm 79 is subjected to a load acting inwardly or outwardly in the radial direction with a sinusoidal increase and decrease by reaction force when compressing the refrigerant gas and moment of the member such as a balance weight for adjusting balance during rotation.
  • the arm 79 (the sub bearing 9B) is fixed to the housing 1 via the harness 40 as described above.
  • the harness 40 is fixed by shrink fitting with respect to the inner peripheral surface of the housing 1. That is, the outer peripheral surface of the harness 40 and the inner peripheral surface of the housing 1 abut to each other and are held in a state of interference fit.
  • the inner diameter of the first hole 79H formed the arm 79 (the sub bearing 9B) is slightly larger relative the shaft diameter of the bolt B. That is, in the stage before tightening complete the bolt B, the sub bearing 9B for the harness 40, there is room for slightly pivots around the axis O1. By using this room, the central axis of the sub bearing 9B (the sub-bearing body 76) is matched against the axis O1 of the housing 1 (the rotary shaft 4). In other words, it is possible to center the sub bearing 9B against the axis O1.
  • the shape of the arm 79 in the sub bearing 9B and the shape of the harness 40 are different from the first embodiment.
  • a region including the outer peripheral end 79A of the arm 79 is formed thinner than other portions of the outer peripheral end 79A, and is defined as a thin portion 79B.
  • an end face at one side in the axis O1 direction of the arm 79 (the drive unit 3 side) has a counterbore that slightly deepens toward the other side in the axis O1 direction.
  • a step is formed between the thin portion 79B and the other portions of the arm 79 (the radially inward portion with respect to the axis O1).
  • a shim S having an extremely thin plate-like shape is disposed as needed.
  • the shim S being interposed, it is possible to easily carry out alignment (the alignment in the axis O1 direction) of the sub bearing 9B with respect to the harness 40.
  • the harness 40 is fixed to the inner peripheral surface 1A of the housing 1 by shrink fitting, it is conceivable that the precise alignment of the harness 40 in the axis O1 direction is difficult. That is, by the disposition of the harness 40 in a slightly deviated position in the axis O1 direction with respect to the housing 1, there may be a possibility in that the positional deviation of the sub bearing 9B in the axis O1 direction is occurred.
  • the shim S between the sub bearing 9B and the harness 40 as described in the above, such deviation is offset and it is possible to optimize the position of the sub bearing 9B in the axis O1 direction.
  • the shim S a plurality types of shims in different thickness is prepared and it is preferable to appropriately select and used a properly shim S according to the deviation amount between the harness 40 and the sub bearing 9B.
  • a size in the radial direction (thickness) in a region at one side in the axis O1 direction of the harness 40 is smaller than that in the first embodiment. More particularly, by setting a distance in the radial direction between the outer peripheral surface of the harness 40 and the inner peripheral surface thereof smaller than that in the first embodiment, a constricted part 40C are formed. According to the constricted part 40C, it is possible to ensure a larger gap between an inner peripheral surface 40A of the harness 40 and the drive unit 3.
  • lubricant oil is continuously supplied by the lubrication pump 80.
  • the gap between the harness 40 and the drive unit 3 is not large enough, there is a possibility of affecting a flow of the lubricant oil.
  • the constricted part 40C is formed in the harness 40, it is possible to reduce the possibility in that the harness 40 affects a flow state of the lubricant oil.
  • the end face at one side in the axis O1 direction of the harness 40 abuts the drive unit 3.
  • the aspect of the harness 40 is not limited thereto, and for example, as shown in FIG. 5 , a gap along the axis O1 direction may be formed between the harness 40 and the drive unit 3. In this case, it is possible to further reduce the possibility in that the harness 40 affects a flow state of the lubricant oil.
  • the sub bearing 9B has been described with three arms 79.
  • the aspect of the sub bearing 9B is not limited thereto, and for example, as shown in FIG. 6 , four arms 79 extending in a radial fashion in the radial direction from the holder 78 may be provided. In this case, it is desirable to form four second holes 40H in the harness 40 so as to corresponding to the four arms 79.

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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)
EP16861893.2A 2015-11-05 2016-10-12 Scroll compressor and method for producing scroll compressor Active EP3315777B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015217463A JP2017089427A (ja) 2015-11-05 2015-11-05 スクロール圧縮機、スクロール圧縮機の製造方法
PCT/JP2016/080210 WO2017077826A1 (ja) 2015-11-05 2016-10-12 スクロール圧縮機、スクロール圧縮機の製造方法

Publications (3)

Publication Number Publication Date
EP3315777A1 EP3315777A1 (en) 2018-05-02
EP3315777A4 EP3315777A4 (en) 2018-08-22
EP3315777B1 true EP3315777B1 (en) 2019-10-23

Family

ID=58661979

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16861893.2A Active EP3315777B1 (en) 2015-11-05 2016-10-12 Scroll compressor and method for producing scroll compressor

Country Status (4)

Country Link
EP (1) EP3315777B1 (enrdf_load_stackoverflow)
JP (1) JP2017089427A (enrdf_load_stackoverflow)
CN (1) CN107923396A (enrdf_load_stackoverflow)
WO (1) WO2017077826A1 (enrdf_load_stackoverflow)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111237188B (zh) * 2018-11-29 2024-04-26 谷轮环境科技（苏州）有限公司 涡旋压缩机及用于涡旋压缩机的静涡旋部件的定位方法
DE102021206432A1 (de) 2021-06-22 2022-12-22 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Scrollmaschine
EP4382750A4 (en) * 2021-08-05 2024-08-28 Daikin Industries, Ltd. SCROLL COMPRESSOR AND REFRIGERATION CYCLE DEVICE

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JP2697278B2 (ja) * 1990-10-05 1998-01-14 三菱電機株式会社 スクロール圧縮機の製造方法
JP3198576B2 (ja) * 1992-01-31 2001-08-13 松下電器産業株式会社 スクロール圧縮機
JPH0842471A (ja) * 1994-07-29 1996-02-13 Sanyo Electric Co Ltd スクロール圧縮機
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JPH1047269A (ja) * 1996-08-01 1998-02-17 Mitsubishi Electric Corp スクロール圧縮機
JP3550940B2 (ja) * 1997-04-24 2004-08-04 三菱電機株式会社 流体機械
JP2000104691A (ja) * 1998-09-25 2000-04-11 Sanyo Electric Co Ltd スクロール圧縮機の副軸受
JP2000274362A (ja) * 1999-03-25 2000-10-03 Hitachi Ltd 圧縮機及びその組立方法
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JP4376554B2 (ja) * 2003-06-12 2009-12-02 パナソニック株式会社 スクロール圧縮機
US8147229B2 (en) * 2005-01-20 2012-04-03 Tecumseh Products Company Motor-compressor unit mounting arrangement for compressors
JP5114710B2 (ja) * 2007-10-16 2013-01-09 株式会社前川製作所 密閉形スクロール圧縮機およびその組立方法
JP2009228441A (ja) * 2008-03-19 2009-10-08 Sanyo Electric Co Ltd スクロール圧縮機
US8342795B2 (en) * 2008-04-24 2013-01-01 Emerson Climate Technologies, Inc. Support member for optimizing dynamic load distribution and attenuating vibration
US9080570B2 (en) * 2009-09-25 2015-07-14 Toshiba Carrier Corporation Hermetic compressor and refrigeration cycle equipment using the same
JP5984787B2 (ja) * 2013-12-04 2016-09-06 三菱電機株式会社 スクロール圧縮機
CN104165142B (zh) * 2014-08-01 2017-02-22 广东美芝制冷设备有限公司 旋转式压缩机

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Also Published As

Publication number Publication date
EP3315777A4 (en) 2018-08-22
JP2017089427A (ja) 2017-05-25
WO2017077826A1 (ja) 2017-05-11
EP3315777A1 (en) 2018-05-02
CN107923396A (zh) 2018-04-17

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