WO2012153644A1 - Machine à fluide du type à volute - Google Patents

Machine à fluide du type à volute Download PDF

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Publication number
WO2012153644A1
WO2012153644A1 PCT/JP2012/061181 JP2012061181W WO2012153644A1 WO 2012153644 A1 WO2012153644 A1 WO 2012153644A1 JP 2012061181 W JP2012061181 W JP 2012061181W WO 2012153644 A1 WO2012153644 A1 WO 2012153644A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
bearing
boss portion
insertion member
orbiting
Prior art date
Application number
PCT/JP2012/061181
Other languages
English (en)
Japanese (ja)
Inventor
和英 渡辺
山崎　浩
源太 慶川
吉田　孝文
松尾　識
Original Assignee
三菱重工業株式会社
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 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to US13/988,830 priority Critical patent/US20130243635A1/en
Priority to CN2012800039138A priority patent/CN103370542A/zh
Priority to EP12782824.2A priority patent/EP2708749A4/fr
Publication of WO2012153644A1 publication Critical patent/WO2012153644A1/fr

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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
    • 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
    • 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
    • F04C29/0078—Fixing rotors on shafts, e.g. by clamping together hub and shaft
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/13—Noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/04—Thermal properties
    • F05C2251/042—Expansivity
    • F05C2251/046—Expansivity dissimilar

Definitions

  • the present invention relates to a scroll type fluid machine in which a pair of fixed scrolls and orbiting scrolls are engaged to form a sealed chamber for sealing a fluid.
  • a wall body is erected on one side surface of the end plate of the orbiting scroll, and a boss portion projects from the other side surface.
  • the bush portion of the crankshaft is inserted into the slewing bearing inserted into the boss portion, and the bush portion is rotationally supported by the slewing bearing.
  • the orbiting scroll rotates through the orbiting bearing and the boss portion. Since the axis of the bush portion is eccentric from the axis of the crankshaft, the orbiting scroll revolves.
  • Patent Document 1 discloses a technique that does not use a slewing bearing by making a drive bush made of polyimide resin and fitting the drive bush directly into the boss.
  • the slewing bearing when the slewing bearing is inserted and fixed in the boss portion at a low temperature, the slewing bearing is inserted (press-fitted) while applying pressure to the boss portion so that a gap does not occur when the temperature rises.
  • the opening side of the boss portion is deformed so as to open outward, and the end plate of the orbiting scroll is deformed accordingly.
  • the contact portion between the wall bodies of the fixed scroll and the orbiting scroll is not a line contact but a point contact, and the refrigerant leaks to the adjacent compression chamber during the orbit.
  • the tip of the boss part may be crimped (caulked) so that the slewing bearing does not come off.
  • the boss portion and the slewing bearing come into partial contact with each other, and there is a problem that surface damage (fretting) occurs due to vibration or repeated stress.
  • the present invention has been made in view of such circumstances, and an object of the present invention is to provide a scroll type fluid machine capable of reducing the deformation of the orbiting scroll that occurs when the bearing is fixed in the boss portion. To do.
  • the scroll fluid machine of the present invention employs the following means. That is, in the scroll type fluid machine according to the present invention, the fixed scroll and the orbiting scroll in which the spiral wall body is erected on one side surface of each end plate are meshed with each other to form a sealed chamber for sealing the fluid.
  • the scroll type fluid machine is a metal boss projecting on the other side of the end plate of the orbiting scroll, a metal bearing inserted into the boss, and a rotation inserted into the bearing and supported by the bearing.
  • a crank shaft that rotates around the axis, and an insertion member that is provided between the boss portion and the bearing and has a larger thermal expansion coefficient than the boss portion and the bearing.
  • the wall body is erected on one side surface of the end plate of the orbiting scroll, the boss portion is projected on the other side surface, the bush portion is inserted into the bearing inserted into the boss portion, The bush portion is rotatably supported by the bearing.
  • the orbiting scroll rotates via a bearing and a boss
  • an insertion member is provided between the boss portion and the bearing. Since the insertion member has a larger coefficient of thermal expansion than the metal boss portion and the bearing, the boss portion and the bearing are inserted by the insertion member at a high temperature. Securely fixed. Therefore, it is not necessary to press-fit the bearing into the boss portion in anticipation of a difference in expansion at high temperatures at low temperatures, and deformation of the orbiting scroll that occurs when the bearing is pressed into the boss portion can be reduced or prevented.
  • the insertion member is made of, for example, synthetic resin or synthetic rubber, and can reduce noise and vibration during rotation of the orbiting scroll.
  • the insertion member has a ring shape and may be provided along the inner surface of the boss portion.
  • the ring-shaped insertion member is provided along the inner surface of the boss portion, the metal boss portion and the bearing do not contact each other. Therefore, it is possible to reduce or prevent surface damage (fretting) that occurs when the boss portion and the bearing are in partial contact with each other when there is no insertion member and receives vibration, repeated stress, or the like.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor 1 according to an embodiment of the present invention.
  • the scroll compressor 1 has a housing 2 constituting an outer shell.
  • the housing 2 is configured by integrally fastening and fixing a front housing 3 and a rear housing 4 with bolts 5.
  • the front housing 3 and the rear housing 4 are integrally formed with flanges 3A, 4A for fastening at a plurality of positions on the circumference, for example, at four positions at equal intervals.
  • a crankshaft 6 is supported so as to be rotatable around its axis L via a main bearing 7 and a sub-bearing 8.
  • One end side (left side in FIG. 1) of the crankshaft 6 is a small-diameter shaft portion 6A, and the small-diameter shaft portion 6A penetrates the front housing 3 and protrudes to the left in FIG.
  • the protruding portion of the small-diameter shaft portion 6A is provided with an electromagnetic clutch, a pulley (not shown) that receives power as is well known, and power is transmitted from a drive source such as an engine via a V-belt or the like.
  • a mechanical seal (lip seal) 9 is installed between the main bearing 7 and the sub-bearing 8 and hermetically seals the inside of the housing 2 and the atmosphere.
  • a large-diameter shaft portion 6B is provided on the other end side (right side in FIG. 1) of the crankshaft 6.
  • the large-diameter shaft portion 6B has a crank pin that is eccentric from the axis L of the crankshaft 6 by a predetermined dimension.
  • 6C is provided integrally.
  • the crankshaft 6 is rotatably supported by the large-diameter shaft portion 6B and the small-diameter shaft portion 6A supported by the front housing 3 via the main bearing 7 and the sub-bearing 8.
  • the crank pin 6C is connected to a turning scroll 15 described later via a drive bush 10, a cylindrical ring (floating bush) 11 and a turning bearing 12, and the turning scroll 15 is driven to turn by rotating the crankshaft 6. It is like that.
  • the drive bush 10 is integrally formed with a balance weight 10 ⁇ / b> A that removes an unbalanced load generated when the orbiting scroll 15 is orbitally driven and is orbited together with the orbiting drive of the orbiting scroll 15.
  • the drive bush 10 is provided with a crank pin hole 10B into which the crank pin 6C is fitted at a position eccentric with respect to the center thereof. As a result, the drive bush 10 and the orbiting scroll 15 fitted to the crankpin 6C are rotated around the crankpin 6C under the gas compression reaction force, so that the orbiting radius of the orbiting scroll 15 is variable.
  • a crank mechanism is configured.
  • a scroll compression mechanism 13 including a pair of fixed scrolls 14 and a turning scroll 15 is incorporated.
  • the fixed scroll 14 includes a fixed end plate 14A and a fixed spiral wrap 14B (wall body) standing on the fixed end plate 14A.
  • the orbiting scroll 15 includes the orbiting end plate 15A and the orbiting end plate 15A. And a swirl spiral wrap 15B (wall body).
  • the fixed scroll 14 and the orbiting scroll 15 are separated from each other by the orbiting radius, and the phases of the spiral wraps 14B and 15B are shifted by 180 degrees to engage with each other. It is assembled so as to have a slight clearance (several tens to hundreds of microns) in the lap height direction at room temperature between the bottom surface.
  • a plurality of pairs of compression chambers 16 formed between the scrolls 14 and 15 are defined by the end plates 14A and 15A and the spiral wraps 14B and 15B.
  • the orbiting scroll 15 is configured to be point-symmetric with respect to the center of the scroll, and the orbiting scroll 15 can smoothly orbit around the fixed scroll 14.
  • the height in the swirl axis direction is set higher than the height on the inner peripheral side on the outer peripheral side of each spiral wrap 14B, 15B, so that the circumferential direction and height direction of each spiral wrap 14B, 15B are increased.
  • a scroll compression mechanism 13 capable of three-dimensional compression that can compress gas is formed on both sides.
  • Tip seals 17 and 18 for sealing a tip gap formed between the tooth bottom surfaces of the other scrolls are provided on the tooth tip surfaces of the spiral wraps 14B and 15B of the fixed scroll 14 and the orbiting scroll 15, respectively. It may be fitted into a seal groove provided on the surface.
  • the fixed scroll 14 is fixedly installed on the inner surface of the rear housing 4 via bolts 27. Further, as described above, the orbiting scroll 15 has a crank pin 6C provided on one end side of the crankshaft 6 with respect to the boss portion 15C provided on the back surface of the orbiting end plate 15A. (Floating bush) 11 and a swivel bearing 12 are connected to each other, and the swivel drive is configured.
  • the orbiting scroll 15 has a back surface of the orbiting end plate 15A supported on the thrust receiving surface 3B of the front housing 3, and a rotation prevention mechanism 19 provided between the thrust receiving surface 3B and the back surface of the orbiting end plate 15A. Rotation is driven around the fixed scroll 14 while being prevented from rotating via the.
  • the rotation prevention mechanism 19 of the present embodiment has a pin hole provided in the front housing 3 with respect to the inner peripheral surface of the rotation prevention ring 19A incorporated in the ring hole provided in the turning end plate 15A of the turning scroll 15.
  • the rotation prevention pin 19B incorporated into the pin ring type rotation prevention mechanism 19 is slidably fitted.
  • the fixed scroll 14 has a discharge port 14C that discharges the compressed refrigerant gas at the central portion of the fixed end plate 14A.
  • the discharge port 14C is attached to the fixed end plate 14A via a retainer 20.
  • a discharge reed valve 21 is installed.
  • a sealing member 22 such as an O-ring is interposed on the back side of the fixed end plate 14A so as to be in close contact with the inner surface of the rear housing 4.
  • a discharge chamber 23 partitioned from the space is formed. Thereby, the internal space of the housing 2 excluding the discharge chamber 23 is configured to function as the suction chamber 24.
  • Refrigerant gas returning from the refrigeration cycle is sucked into the suction chamber 24 through the suction port 25 provided in the front housing 3, and the refrigerant gas is sucked into the compression chamber 16 through the suction chamber 24.
  • a sealing material 26 such as an O-ring is interposed on the joint surface between the front housing 3 and the rear housing 4 to seal the suction chamber 24 formed in the housing 2 in an airtight manner against the atmosphere.
  • the scroll compressor 1 uses a lubricating oil for smoothly moving the sliding portion inside.
  • the lubricating oil coexists with the refrigerant at a predetermined ratio, and is sucked into the fixed scroll 14 and the orbiting scroll 15 together with the refrigerant.
  • This lubricating oil adheres to the inner wall surfaces of the fixed scroll 14 and the orbiting scroll 15 and can seal minute gaps.
  • the film thickness of the lubricating oil adhering to the inner wall surface is about 5 ⁇ m for the thin part and about 100 ⁇ m for the thick part, and is about 40 ⁇ m on average.
  • Lubricating oil is discharged from the scroll compressor 1 to, for example, refrigerant piping constituting the refrigeration circuit, passes through each component of the refrigeration circuit, returns to the scroll compressor 1 again, and is sucked into the scroll compressor 1.
  • Some refrigeration circuits are provided with an oil separator that separates lubricant and refrigerant on the discharge side of the scroll compressor 1, and the oil separator returns the separated lubricant to the scroll compressor 1. be able to.
  • the joint portion between the boss portion 15C and the slewing bearing 12 will be described.
  • the insertion member 31 is provided in a gap provided between the boss portion 15 ⁇ / b> C and the swivel bearing 12.
  • the boss portion 15C is made of a ring-shaped metal, for example, aluminum, and protrudes from the back surface of the turning end plate 15A.
  • the insertion member 31 and the swivel bearing 12 are inserted inside the boss portion 15C.
  • the slewing bearing 12 is a needle bearing made of metal, for example, steel.
  • the outer diameter of the slewing bearing 12 is smaller than the inner diameter of the boss portion 15C.
  • the slewing bearing 12 includes an outer ring 28, a plurality of needle rollers 29, and a cage 30.
  • the outer ring 28 has a substantially hollow cylindrical shape, and, for example, hook portions that are bent at substantially right angles toward the inside are formed at both ends in the direction of the axis L of the crankshaft 6.
  • the cage 30 holds a plurality of needle rollers 29 at substantially equal intervals in the circumferential direction, and is attached to the inner side of the outer ring 28.
  • the insertion member 31 has a ring shape as shown in FIG.
  • the insertion member 31 has a larger coefficient of thermal expansion than the metal boss portion 15C and the slewing bearing 12, and is made of synthetic resin, for example, nylon 66 or synthetic rubber.
  • two insertion members 31 are provided between the boss portion 15 ⁇ / b> C and the swivel bearing 12.
  • the insertion member 31 is first installed on the inner surface of the boss portion 15C at normal temperature, and then the swivel bearing 12 is inserted inside the insertion member 31.
  • a groove portion may be formed on the inner surface of the boss portion 15C so that the insertion member 31 does not shift in position.
  • the one end side 31a of the insertion member 31 may be R chamfered or C chamfered as shown in FIG. With this shape, the swivel bearing 12 is smoothly inserted into the insertion member 31.
  • the other end 31b may be chamfered or may remain in a right-angle shape as shown in FIG.
  • the insertion member 31 and the orbiting bearing 12 are securely fixed to the boss portion 15C, that is, the orbiting scroll 15 at normal temperature.
  • the insertion member 31 since the insertion member 31 has a larger coefficient of thermal expansion than the metal boss portion 15C and the slewing bearing 12, each member expands at a high temperature when the scroll compressor 1 is operating. Even so, the swivel bearing 12 is securely fixed to the boss portion 15C by the insertion member 31.
  • the orbiting scroll 15 and the boss portion 15C is made of aluminum
  • the rotary bearing 12 is made of steel
  • they are each a linear thermal expansion coefficient of 22.0 ⁇ 10 -6 /°C,12.5 ⁇ 10 -6 / °C
  • orbiting bearing If the outer diameter of 12 is 36 mm, a difference of 27 ⁇ m occurs when the temperature rises by 80 ° C., and a gap is generated between the boss portion 15C and the slewing bearing 12. Therefore, conventionally, the inside diameter of the boss portion 15C is set to be small at room temperature, and the slewing bearing 12 is press-fitted into the boss portion 15C.
  • the thermal expansion coefficient is larger than that of the boss portion 15C and the slewing bearing 12. Therefore, the swivel bearing 12 is securely fixed to the boss portion 15C by the insertion member 31.
  • the thickness, material, etc. of the insertion member 31 are set so that both the gap generated between the boss portion 15C and the slewing bearing 12 at high temperature and the difference in expansion of the insertion member 31 when transitioning from normal temperature to high temperature are equal. ⁇ It is desirable to be selected.
  • the insertion member 31 has a ring shape and is evenly disposed between the boss portion 15C and the slewing bearing 12, the metal boss portion 15C and the slewing bearing 12 do not contact each other. Therefore, it is possible to prevent surface damage (fretting) that occurs due to vibration, repeated stress, or the like, which has conventionally occurred at the contact portion between the boss portion 15C and the swivel bearing 12 when there is no insertion member 31. Since the boss portion 15C and the slewing bearings 12 do not need to contact each other, the shape of the insertion member 31 is not limited to the ring shape, and may be other shapes.
  • the insertion member 31 is made of synthetic resin or synthetic rubber, for example, and can reduce noise and vibration when the orbiting scroll 15 rotates.
  • the boss portion 15 ⁇ / b> C and the slewing bearing 12 need only be securely fixed by the insertion member 31, and there is no need to perform groove processing for fixing the insertion member 31 to the outer surface of the outer ring 31.
  • this embodiment can also be applied when the outer ring is thin, such as a needle bearing, that is, when a groove cannot be formed on the outer surface of the outer ring unlike the outer ring of a ball bearing.
  • the insertion member of the present invention is not limited to the insertion member 31 described above.
  • the insertion member 32 shown in FIGS. 5 and 6 it may be a sheet-like member having a longer width than the examples of FIGS. 1 to 4, or an NBR O-ring. Good.
  • the insertion member 31 or the insertion member 32 is made of nylon, as shown in FIGS. 5 and 6, a slit 33 may be provided.
  • nylon since it is relatively hard, it is difficult to insert the insertion members 31 and 32 into the boss portion 15C.
  • the slit 33 the insertion members 31 and 32 are smoothly installed in the boss portion 15C. it can.
  • the insertion members 31 and 32 are provided between the boss portion 15C and the slewing bearing 12, and the boss portion 15C and the slewing bearing 12 are not in contact with each other.
  • the present invention is limited to this example.
  • the slewing bearing 12 may be inserted into the boss portion 15C while compressing the insertion members 31 and 32 with the press-fitting allowance set to 0 or a smaller value than the conventional one.
  • the boss portion 15C and the slewing bearing 12 are in partial contact with each other.
  • the present invention is not limited to this example.
  • the present invention can be similarly applied even when the cylindrical ring 11 is not provided and the drive bush 10 is directly inserted into the slewing bearing 12.
  • an example in which the present invention is applied to a scroll compressor has been described.
  • the present invention can be similarly applied to a scroll expander.

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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)

Abstract

L'invention porte sur une machine à fluide du type à volute dans laquelle la déformation d'une volute tournante peut être réduite lorsqu'un palier est fixé à l'intérieur d'une partie formant bossage. Dans un compresseur à volute, une chambre étanche au fluide est formée en faisant coopérer une volute fixe et une volute tournante ayant chacune une paroi en spirale sur un côté d'une plaque terminale. Le compresseur à volute comprend : une partie formant bossage métallique (15c) qui fait saillie sur l'autre côté de la plaque d'extrémité de la volute tournante; un palier rotatif métallique (12) inséré dans la partie formant bossage (15c); un vilebrequin conçu pour être mis en rotation autour d'une ligne d'axe et qui comprend une partie coussinet, la partie coussinet étant emboîtée dans le palier rotatif (12) et étant convenablement supportée par le palier rotatif (12); et un élément rapporté (31) disposé entre la partie formant bossage (15c) et le palier rotatif (12), l'élément rapporté (31) ayant un coefficient de dilatation thermique supérieur à ceux de la partie formant bossage (15c) et du palier rotatif (12).
PCT/JP2012/061181 2011-05-12 2012-04-26 Machine à fluide du type à volute WO2012153644A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US13/988,830 US20130243635A1 (en) 2011-05-12 2012-04-26 Scroll-type fluid machine
CN2012800039138A CN103370542A (zh) 2011-05-12 2012-04-26 涡旋式流体机械
EP12782824.2A EP2708749A4 (fr) 2011-05-12 2012-04-26 Machine à fluide du type à volute

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011107196A JP2012237251A (ja) 2011-05-12 2011-05-12 スクロール型流体機械
JP2011-107196 2011-05-12

Publications (1)

Publication Number Publication Date
WO2012153644A1 true WO2012153644A1 (fr) 2012-11-15

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ID=47139128

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PCT/JP2012/061181 WO2012153644A1 (fr) 2011-05-12 2012-04-26 Machine à fluide du type à volute

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Country Link
US (1) US20130243635A1 (fr)
EP (1) EP2708749A4 (fr)
JP (1) JP2012237251A (fr)
CN (1) CN103370542A (fr)
WO (1) WO2012153644A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2806164B1 (fr) * 2013-05-22 2015-09-09 Obrist Engineering GmbH Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale
EP2806165B1 (fr) * 2013-05-22 2015-09-09 Obrist Engineering GmbH Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale
US9611846B2 (en) * 2014-12-31 2017-04-04 Smith International, Inc. Flow restrictor for a mud motor
JP6596787B2 (ja) * 2015-08-03 2019-10-30 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

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JPS63100293A (ja) * 1986-10-17 1988-05-02 Mitsui Seiki Kogyo Co Ltd スクロ−ル圧縮機の旋回スクロ−ル支持構造
JPH0357893A (ja) * 1989-07-26 1991-03-13 Mitsubishi Electric Corp スクロール流体機械
JPH09314695A (ja) * 1996-05-30 1997-12-09 Koyo Seiko Co Ltd 軸受のクリープ防止用樹脂
JPH11153092A (ja) * 1997-11-20 1999-06-08 Mitsubishi Heavy Ind Ltd 圧縮機
US6126423A (en) * 1998-11-13 2000-10-03 Ford Global Technologies, Inc. Preloaded spring mount for crank pin/rotor bearing assembly

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US2466428A (en) * 1945-06-20 1949-04-05 Weatherhead Co Piston seal
US3572729A (en) * 1968-05-23 1971-03-30 Olin Corp Expanding ring seal
CA2182923C (fr) * 1995-08-10 2006-10-10 Walter P. Waskiewicz Garniture de coussinet/palier
FR2759129B1 (fr) * 1997-01-31 1999-03-05 Roulements Soc Nouvelle Roulement et palier comportant un insert de compensation thermique
JP2006112379A (ja) * 2004-10-18 2006-04-27 Matsushita Electric Ind Co Ltd 流体機械の製造方法および流体機械
US20070222162A1 (en) * 2006-03-24 2007-09-27 Stoner Jack C Back-up ring and sealing assembly
JP2009264370A (ja) * 2008-03-31 2009-11-12 Hitachi Ltd 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
JPS63100293A (ja) * 1986-10-17 1988-05-02 Mitsui Seiki Kogyo Co Ltd スクロ−ル圧縮機の旋回スクロ−ル支持構造
JPH0357893A (ja) * 1989-07-26 1991-03-13 Mitsubishi Electric Corp スクロール流体機械
JPH09314695A (ja) * 1996-05-30 1997-12-09 Koyo Seiko Co Ltd 軸受のクリープ防止用樹脂
JPH11153092A (ja) * 1997-11-20 1999-06-08 Mitsubishi Heavy Ind Ltd 圧縮機
US6126423A (en) * 1998-11-13 2000-10-03 Ford Global Technologies, Inc. Preloaded spring mount for crank pin/rotor bearing assembly

Also Published As

Publication number Publication date
EP2708749A1 (fr) 2014-03-19
EP2708749A8 (fr) 2015-02-25
EP2708749A4 (fr) 2015-01-14
JP2012237251A (ja) 2012-12-06
US20130243635A1 (en) 2013-09-19
CN103370542A (zh) 2013-10-23

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