EP0075053A1 - Moyens anti-corrosion pour appareil de déplacement de fluide à volutes imbriquées - Google Patents

Moyens anti-corrosion pour appareil de déplacement de fluide à volutes imbriquées Download PDF

Info

Publication number
EP0075053A1
EP0075053A1 EP81304364A EP81304364A EP0075053A1 EP 0075053 A1 EP0075053 A1 EP 0075053A1 EP 81304364 A EP81304364 A EP 81304364A EP 81304364 A EP81304364 A EP 81304364A EP 0075053 A1 EP0075053 A1 EP 0075053A1
Authority
EP
European Patent Office
Prior art keywords
scroll
scroll member
plate
end plate
end surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP81304364A
Other languages
German (de)
English (en)
Other versions
EP0075053B1 (fr
Inventor
Takayuki Iimori
Kiyoshi Terauchi
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.)
Sanden Corp
Original Assignee
Sanden Corp
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 Sanden Corp filed Critical Sanden Corp
Priority to EP81304364A priority Critical patent/EP0075053B1/fr
Priority to DE8181304364T priority patent/DE3175720D1/de
Publication of EP0075053A1 publication Critical patent/EP0075053A1/fr
Application granted granted Critical
Publication of EP0075053B1 publication Critical patent/EP0075053B1/fr
Expired legal-status Critical Current

Links

Images

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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines 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
    • F01C1/0207—Rotary-piston machines or engines 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
    • F01C1/0215—Rotary-piston machines or engines 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C2230/00—Manufacture
    • 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
    • F04C2240/801—Wear plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2230/00—Manufacture

Definitions

  • This invention relates to scroll type fluid displacement apparatus.
  • Scroll type apparatus are well known in the prior art.
  • U.S. Patent No. 801,182 discloses a scroll type apparatus including two scroll members each having a circular end plate and a spiroidal or involute spiral element. These scroll members are maintained angularly and radially offset so that both spiral elements interfit to make a plurality of line contacts between both spiral curved surfaces, thereby sealing off and defining at least one pair of fluid pockets.
  • the relative orbital motion of the two scroll members shifts the line contacts along the spiral curved surfaces to change the volume of the fluid pockets. Since the volume of the fluid pockets increases or decreases, dependent on the direction of the orbiting motion, the scroll type apparatus is applicable to compress, expand or pump fluids.
  • the scroll type compressor In comparison with conventional compressors of the piston type, the scroll type compressor has certain advantages, such as fewer parts and continuous compression of fluid.
  • one of the problems with scroll type compressors is the ineffective sealing of the fluid pockets. Axial and radial sealing of the fluid pockets must be maintained in a scroll type compressor in order to achieve efficient operation.
  • the fluid pockets are defined by the line contacts between the interfitting two spiral elements and the axial contacts between the axial end surface of one spiral element and the inner end surface of the end plate supporting the other spiral element.
  • the seal element inthe above patent is urged toward the facing end surface of the end plate by a spring or other axial force urging mechanism, over a period of time, abrasions occur between the end surface of the seal element and the end plate of the scroll member, especially when light weight alloys, such as aluminum alloys, are used as material of the spiral element.
  • These abrasions cause the occurrence of wear dust, which, in turn, not only creates damages on the parts of the apparatus, for example, the surface of the scroll members and the gearings, but also adversely affects the operation of the filter and expansion valve for the refrigerant circuit.
  • the seal elements are also damaged, and the axial contact between the end surface of spiral element and the inner end surface of the end plate becomes imperfect, thereby reducing compressor efficiency.
  • a scroll type fluid displacement apparatus including a pair of scroll members each having an end plate and a spiral wrap extending from one side of said end plate, said spiral wraps interfitting at an angular and radial offset to make a plurality of line contacts between the spiral curved surfaces which define fluid pockets, and drive means operatively connected to one of said scroll member for orbiting said one scroll member relative to the other scroll member while preventing rotation of said one scroll member to thereby change the volume of the fluid pockets, wherein an anti-wear plate is disposed on an end surface of said end plate of at least one of said scroll members, said anti-wear plate facing the axial end surface of said spiral wrap of the other of said scroll members to prevent wear and maintain axial sealing.
  • a scroll type fluid displacement apparatus comprising:
  • One embodiment of the invention is a scroll type fluid displacement apparatus which includes a pair of scroll members, each comprising an end plate and a spiral wrap extending from one side of the end plate. Both spiral wraps interfit to make a plurality of line contacts between the spiral curved surfaces of the spiral wraps. These spiral wraps are angularly and radially offset.
  • a driving mechanism includes a drive shaft which is rotatably supported by a housing and operatively connected to one of the scroll members to cause the one scroll member to undergo orbital motion relative to the other scroll member, while preventing rotation of the one orbiting scroll member. The relative motion of the scroll members changes the volume of the fluid pockets.
  • the fluid displacement apparatus In order to. effectively change the volume of the fluid pockets, the fluid displacement apparatus must provide axial and radial sealing between the scroll members.
  • the axial sealing is more critical and involute shape seal elements are used on the end surfaces of both spiral wraps which are formed of an aluminum alloy to reduce the weight of the apparatus, the softness of the aluminum alloy results in considerable abrasion and wear between the scroll member and axial seal element over a period of time.
  • the present invention provides an involute plate formed of a hard material such as hardened steel between the axial end surface of the spiral wrap of the orbiting scroll member and the circular end plate' of the fixed scroll member.
  • This involute palte covers only the area of the surface of the circular end plate of the fixed scroll member where the spiral wrap makes axial contact during the orbital motion of the orbiting scroll member to thereby prevent excessive wear and abrasion.
  • a similar involute plate could be placed on the circular end plate of the orbiting scroll member to prevent excessive wear between the circular end plate of the orbiting scroll member and the axial end surface of the spiral wrap of the fixed scroll member.
  • both scroll members are formed of aluminium alloy
  • the rubbing or contact surface of one of the scroll members is hardened by covering it with a hard material and the other scroll member is provided with an involute plate as described above.
  • an elastic spring member or an elastic sheet is disposed between the inner end surface of the circular end plate and the involute plate.
  • This elastic spring member is to vary its thickness on necessity.
  • a fluid displacement apparatus which consists of a refrigerant compressor 1.
  • the compressor 1 includes a compressor housing 10 formed by a cylindrical housing 11, a front end plate 12 and a rear end plate 13.
  • a drive shaft 15 is rotatably supported in an opening in front end plate 12 by a bearing, such as a ball bearing 14.
  • Front end plate 12 has a sleeve portion 16 projecting from the front surface thereof to surround drive shaft 15 and define a shaft seal cavity.
  • a shaft seal assembly 17 is assembled on drive shaft 15 within the shaft seal cavity.
  • a pulley 19 is rotatably supported by bearing 18 on the outer surface of sleeve portion 16.
  • An electromagnetic annular coil 20 is mounted within an annular cavity in the outer part of sleeve portion 16.
  • An armature plate 21 is supported on the end of drive shaft 15 which extends from sleeve portion 16.
  • the pulley 19, magnetic coil 20 and armature plate 21 form a magnetic clutch.
  • drive shaft 15 is driven by an external power source, such as an engine of a vehicle through a rotational force transmitting device, such as a magnetic clutch.
  • Front end plate 12 which is fixed to the front end of cylindrical housing 11 by a bolt (not shown), covers an opening in the front end of cylindrical housing 11. An 0-ring 22 seals this opening.
  • Rear end plate 13 has an annular projection 23 on its inner surface to partition suction chamber 24 from discharge chamber 25.
  • Rear end plate 13 also has a fluid inlet port 26 and a fluid outlet port (not shown) which are connected to the suction and discharge chamber 24 and 25, respectively.
  • Rear end plate 13 is fixed to rear end of cylindrical housing 11 by bolts and nuts 27.
  • Circular end palte 281 of fixed scroll member 28, which is also fixed to housing 11 by bolts and nuts 27, is located between cylindrical housing 11 and rear end plate 13. Gaskets 2 and 3 prevent fluid leakage past the outer perimeter. of circular end plate 281 and between discharge chamber 25 and suction chamber 24.
  • Fixed scroll member 28 includes circular end plate 281 and a wrap or spiral element 282 extending from one side of circular end plate 281. An opening in the rear end of cylindrical hbusing 11 is covered by circular end plate 281. Spiral element 282 is disposed in inner chamber 29 of cylindrical housing 11. Circular end plate 281 has one hole or suction port 283 which communicates between suction chamber 24 and inner chamber 29 of cylinderical housing 11 and another hole or discharge port 284 at a position near the center of spiral element 282 which is connected to discharge chamber 25.
  • An orbiting scroll member 30 is also disposed in inner chamber 29.
  • Orbiting scroll emmber 30 compresses circular end plate 301 and wrap or spiral element 302 extending from one side of circular end plate 301, Both spiral elements 282 and 302 interfit at an angular offset of 180° and at a predetermined radial offset to make a plurality of line contacts to define at least one pair of sealed off fluid pockets 'between the spiral element 282 and 302.
  • Each of the spiral elements 282 and 302 has a groove in its axial end surface and a seal element 285, 304 is disposed in the groove for preventing fluid leakage between the end surface of each circular end plate and the axial end surface of each spiral element.
  • Orbiting scroll member 30 is connected to a driving mechanism, including drive shaft 15, and to a rotation preventing mechanism. These last two mechanism effect orbital motion of orbiting scroll member 30 at a circular radius R o to thereby compress fluid passing through the compressor.
  • the raius R o generally is given by the following formula:
  • the pitch (P) of the spiral elements can be define by 2 ⁇ rg, where rg is the involute generating circle radius.
  • the radius of orbital motion R o is also illustrated in Fig. 8 as the locus of an arbitrary point Q on orbiting scroll member 30.
  • the spiral leement 302 is radially offset from spiral element 282 of fixed scroll member 28 by the distance R o .
  • orbiting scroll member 30 undergoes orbital motion of a radius R o upon rotation of drive shaft 15.
  • the line contacts between spiral elements 282 and 302 moves toward the center of the spiral elements along the surfaces of the spiral elements.
  • the fluid pockets which are defined by spiral elements 282 and 302, also move to the center with a consequent reduction in volume and compression of the fluid in the pockets.
  • the fluid or refrigerant gas which is introduced into chamber 29 from an external fluid circuit through inlet port 26, suction chamber 24 and hole 283, is drawn into fluid pockets formed between spiral elements 282 and 302.
  • the fluid then is discharged through an outlet port to an external fluid circuit, for example, a cooling circuit.
  • Drive shaft 15 which is rotatably supported by front end plate 12 through ball bearing 14, has a disk portion 151 at its inner end.
  • Disk 151 is rotatably supported by cylindrical housing 11 through bearing 31 at an opening in the front end of cylindrical housing 11.
  • Ball bearing 31 fits between coolar 152 on disk.151 and collar 111 at the opening of cylindrical housing 11.
  • An inner ring of ball bearing 14 fits against stepped portion 153 of drive shaft 15 and an outer_ring fits against shoulder portion 121 of front end plate 12. Therefore, ball bearings 14 and 31 permit the drive shaft to undergo rotation while preventing axial motion.
  • a crank pin or drive pin 154 axailly projects from an end surface of disk 151 at a position which is radially offset from the center of drive shaft 15.
  • Circular plate 301 of orgiting scroll member 30 has a tubular boss 303 axially projecting from the end surface opposite the surface from which spiral element 302 extends.
  • a discoid or short axial bushing 33 fits into boss 303 and is rotatably supported therein by a bearing such as a needle bearing 34.
  • Bushing 33 has a balance weight 331 which is radially connected to bushing 33 along a front surface thereof.
  • An eccentric hole 332 is formed in bushing 33 at a position radially offset from center of bushing 33.
  • Drive pin 154 fits into eccentric hole 332 together with bearing 32. As a result, bushing 33, which is driven by the rotation of drive pin 154,. rotates within bearing 34.
  • bushing center Oc swings about the center Od of drive pin 154 at a radius E2, as shown in Fig. 3.
  • the swing of center Oc is illustrated as are Oc'-Oc" in Fig.3.
  • a drive force is exerted at center Od to the left, and a reaction force of gas compression occurs ' at center Oc to the right, both forces being parallel to line Ll.
  • the moment art Od-Oc swings outwardly and spiral element 302 of orbiting scroll member 30. is forced toward spiral element 282 to fixed scroll member 28 so that the line contacts between spiral elements 282 and 302 necessarily orbit with the center Os of drive shaft 15.
  • orbiting scroll member 30 does not rotate because of the operation of a rotation preventing/thrust bearing mechanism, which is described more fully hereinafter.
  • the orbiting scroll member 30 orbits while maintaining its angular orientation.
  • the fluid pockets move because of orbital motion of the orbition scroll member 30 to thereby compress the fluid in these fluid pockets.
  • bushing 33 does not have balance weight 331-, a centrifugal force caused by the orbiting motion of orbiting parts, i.e., orbiting scroll member 30, bearing means 34 and bushing 33, is added to the urgiing force of spiral element 302 acting on spiral element 282, In this event, the contact force between the spiral elements 282 and 302 would increase as shaft speed increases, which would increase the friction force between spiral elements 302 and 282 and increase wearing of both spiral elements as well as increase the mechanical friction loss.
  • the centrifugal force can be cancelled by the centrifagal force of the balance weight.
  • the mass of balance weight 331 is selected so that the centrifugal force is equal in magnitude to the total centrifugal force of the orbiting parts and it is positioned so that the centrifagal forces are in the opposite direction.
  • Rotation preventing/thrust bearing device 37 which is integral with a thrust bearing device.
  • Rotation preventing/thrust bearing device 37 surrounds boss 303 and includes fixed ring 371 and Oldham ring 372.
  • Fixed ring 371 is attached to stepped portion 112 of the inner surface of cylindrical housing 11 by pin 373.
  • Fixed ring 371 is provided iwht a pair of keyways 371a and 371b in an axial end surface facing orbiting scroll member 30.
  • Oldham ring 371 is positioned between fixed 371 and circular plate 301 or orbiting scroll member 30.
  • Oldham ring 372 includes a pair of keys 372a and 372b facing fixed ring 371; these keys are received in keyways 371a and 371b. Therefore, Oldham ring 372 can slide in a radial direction on keys 372a and 372b within keyways 371a and 371b.
  • Olaham ring 372 has a pair of keys 372c and 372d on its opposite surface. Keys 372c and 372d are located along a radial line perpendicular to the radial line on which keys 372a and 372b are located.
  • Circular plate 301 of orbiting scroll member 30 has a pair of keyways (in Fig.4 only one keyway 301a is shown; the other keyway is located diamerically opposite keyway 301a) on the surface facing Oldham ring 392 for receiving keys 372c and 372d. Therefore, orbiting scroll member 30 can slide in a radial direction on keys 372c. 372d within the keyways of circular plate 301.
  • orbiting scroll member 30 slides in two perpendicular directions on Oldham ring 372.
  • the ring 372 prevents rotation of orbiting scroll member 30, but permits the orbiting scroll member to move in two perpendicular radial direction, which results in a freedoms of orbital motion of the orbiting scroll member with radius R o .
  • Oldham ring 372 also has a plurality of holes 38.
  • Bearing elements such as balls 39 each having a diameter greater than the thickness of Oldham ring 372, are placed in holes 38. Balls 39 contact and roll on the surfaces of fixed ring 371 and circular plate 301. Therefore, the thrust load from orbiting scroll member 30 is supported by fixed ring 371 through balls 39.
  • Both spiral elements 282 and 302 of the scroll members have a groove on the axial end surface and seal elements 285 and 304 for providing a seal between the end surface of each circular end plate and the axial end surface of each spiral element.
  • An involute plate 40 which is formed of hard meral, such as hardened steel, is fitted to the end surface of circular end plate 281 facing orbiting scroll member'30.
  • a screw 41 can be used to prevent the touch of involute plate from flapping, as shown in Fig. 5.
  • the involute plate is necessary because, in the embodiment shown in Fig. 1, both scroll members 28 and 30 are formed of aluminum alloy to reduce the weight of the compressor. However, because aluminum alloy is soft, considerable abrasion occrus between the contact surfaces formed by aluminum parts and sealing element 304. Thus, use of involute plate 40 minimizes the abrasion and reduces wear.
  • the rubbing surfaces of orbiting scroll member 30, that is the end surface of circular palte 301 facing fixed scroll member 28 and all surfaces of spiral element 302 are surface hardened.
  • Fixed scroll member 28, which is also formed of aluminum alloy, is not surface hardened.
  • FIG. 6 another embodiment is shown which is directed to a modification of the axial sealing between the axial end surface of the spiral elements and the end surfaces of the circular end plates.
  • the seal element described in connection with Fig. 1 is not used.
  • Similar parts in Fig. 6 are represented by the same reference numerals as the embodiment shown in Fig. 1.
  • Orbiting scroll member 30 of Fig. 6 is operatively connected to the drive mechanism, fixed scroll member 28 is fastened to cylindrical housing 11 of housing 10 by bolts and nuts 29, and these bolts and nuts 29 also fasten rear end plate 13 to cylindrical housing 11, in the same manner as in Fig. 1.
  • Fig. 7 (a) the surfaces of circular end plate 301 and spiral element 302 of orbiting scroll member 30 are coated with a hard material.
  • An involute plate 40 which is formed of hard metal such as steel, is placed'to the end surface of circular plate 281 of fixed scroll, menber 28 facing orbiting scroll member 30. The involute plate 40 covers the contact surface between the extended portion of the spiral element 302 and the circular end plate 281 in the same manner as in the forst embodiment.
  • an elastic plate 41 for example a rubber plate, is disposed between involute plate 40 and the end surface of circular end plate 281.
  • the thickness of elastic plate 41 varies in response to relative position of orbiting scroll member 30 against involute plate 40. Therefore, if a manufacturing error exists with the axial dimentions of the spiral element, elastic plate 41 compensates for this error by changing its thickness. As a result, the axial sealing between the axial end surface of the spiral element and the end surface of the circular end plate is secured without wear or damage to the scroll member.
  • Fig.7(a) can be modified by placing another seal element 304 in a groove on the axial end surface of spiral element 302 to further prevent fluid leakage between spiral element 302 and circular end plate 281.
  • involute plate 40 of hard anti-wear material (as best shown in Fig. 5(b)) is disposed on the end surface of at least one scroll member.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP81304364A 1981-09-22 1981-09-22 Moyens anti-corrosion pour appareil de déplacement de fluide à volutes imbriquées Expired EP0075053B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP81304364A EP0075053B1 (fr) 1981-09-22 1981-09-22 Moyens anti-corrosion pour appareil de déplacement de fluide à volutes imbriquées
DE8181304364T DE3175720D1 (en) 1981-09-22 1981-09-22 Wear-resisting means for scroll-type fluid-displacement apparatuses

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP81304364A EP0075053B1 (fr) 1981-09-22 1981-09-22 Moyens anti-corrosion pour appareil de déplacement de fluide à volutes imbriquées

Publications (2)

Publication Number Publication Date
EP0075053A1 true EP0075053A1 (fr) 1983-03-30
EP0075053B1 EP0075053B1 (fr) 1986-12-17

Family

ID=8188405

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81304364A Expired EP0075053B1 (fr) 1981-09-22 1981-09-22 Moyens anti-corrosion pour appareil de déplacement de fluide à volutes imbriquées

Country Status (2)

Country Link
EP (1) EP0075053B1 (fr)
DE (1) DE3175720D1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3442619A1 (de) * 1984-11-19 1986-05-22 Sanden Corp., Isesaki, Gunma Spiralfluidverdraengervorrichtung
EP0122722B1 (fr) * 1983-03-15 1988-03-16 Sanden Corporation Dispositif d'étanchéité axiale pour un appareil à volutes de déplacement de fluide
JPH0968175A (ja) * 1995-09-01 1997-03-11 Tokico Ltd スクロール式流体機械
EP0855510A3 (fr) * 1997-01-27 1998-09-02 Sanden Corporation Appareil à spirales de déplacement de fluide
WO2000006906A1 (fr) * 1998-07-30 2000-02-10 Varian, Inc. Pompe a vide de type a spirale
JP2023143657A (ja) * 2022-03-23 2023-10-06 日立ジョンソンコントロールズ空調株式会社 圧縮機

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2519588A (en) * 1943-12-24 1950-08-22 Borg Warner Pump housing
US3552895A (en) * 1969-05-14 1971-01-05 Lear Siegler Inc Dry rotary vane pump
US3888746A (en) * 1974-01-04 1975-06-10 Ford Motor Co Method of providing an intermediate steel layer for chrome plating on rotor housings
US3986799A (en) * 1975-11-03 1976-10-19 Arthur D. Little, Inc. Fluid-cooled, scroll-type, positive fluid displacement apparatus
FR2363010A1 (fr) * 1976-08-24 1978-03-24 Bosch Gmbh Robert Electropompe a carburant
FR2370185A1 (fr) * 1976-11-09 1978-06-02 Nippon Piston Ring Co Ltd Pompe ou compresseur rotatif a palettes
EP0012615A1 (fr) * 1978-12-15 1980-06-25 Sankyo Electric Company Limited Améliorations à des compresseurs à fluide du type à volutes imbriquées

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6041237B2 (ja) * 1981-03-09 1985-09-14 サンデン株式会社 スクロ−ル型流体装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2519588A (en) * 1943-12-24 1950-08-22 Borg Warner Pump housing
US3552895A (en) * 1969-05-14 1971-01-05 Lear Siegler Inc Dry rotary vane pump
US3888746A (en) * 1974-01-04 1975-06-10 Ford Motor Co Method of providing an intermediate steel layer for chrome plating on rotor housings
US3986799A (en) * 1975-11-03 1976-10-19 Arthur D. Little, Inc. Fluid-cooled, scroll-type, positive fluid displacement apparatus
FR2363010A1 (fr) * 1976-08-24 1978-03-24 Bosch Gmbh Robert Electropompe a carburant
FR2370185A1 (fr) * 1976-11-09 1978-06-02 Nippon Piston Ring Co Ltd Pompe ou compresseur rotatif a palettes
EP0012615A1 (fr) * 1978-12-15 1980-06-25 Sankyo Electric Company Limited Améliorations à des compresseurs à fluide du type à volutes imbriquées

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0122722B1 (fr) * 1983-03-15 1988-03-16 Sanden Corporation Dispositif d'étanchéité axiale pour un appareil à volutes de déplacement de fluide
DE3442619A1 (de) * 1984-11-19 1986-05-22 Sanden Corp., Isesaki, Gunma Spiralfluidverdraengervorrichtung
FR2574869A1 (fr) * 1984-11-19 1986-06-20 Sanden Corp Appareil de deplacement de fluide de type a spirale
JPH0968175A (ja) * 1995-09-01 1997-03-11 Tokico Ltd スクロール式流体機械
US5775888A (en) * 1995-09-01 1998-07-07 Tokico Ltd. Scroll fluid machine having end plate with greater center thickness
EP0855510A3 (fr) * 1997-01-27 1998-09-02 Sanden Corporation Appareil à spirales de déplacement de fluide
US6068458A (en) * 1997-01-27 2000-05-30 Sanden Corporation Scroll-type fluid displacement apparatus
WO2000006906A1 (fr) * 1998-07-30 2000-02-10 Varian, Inc. Pompe a vide de type a spirale
JP2023143657A (ja) * 2022-03-23 2023-10-06 日立ジョンソンコントロールズ空調株式会社 圧縮機

Also Published As

Publication number Publication date
DE3175720D1 (en) 1987-01-29
EP0075053B1 (fr) 1986-12-17

Similar Documents

Publication Publication Date Title
EP0061698B1 (fr) Appareil avec un piston tournant pour déplacer un fluide et ayant un dispositif empêchant la rotation
US4460321A (en) Axial clearance adjustment mechanism for scroll type fluid displacement apparatus
EP0052461B1 (fr) Appareil à déplacement de fluide à volutes imbriquées ayant des moyens pour compenser des forces centrifuges
EP0060495B1 (fr) Dispositif empêchant la rotation pour un appareil à piston à mouvement orbital
US4645436A (en) Scroll type fluid displacement apparatus with improved anti-wear device
US4645435A (en) Rotation preventing device for an orbiting member of a fluid displacement apparatus
EP0122722B1 (fr) Dispositif d'étanchéité axiale pour un appareil à volutes de déplacement de fluide
US4492543A (en) Orbiting member fluid displacement apparatus with rotation preventing mechanism
EP0099740B1 (fr) Machine à déplacement de fluide à volutes imbriquées et procédé d'assemblage
CA1222985A (fr) Pompe centrifuge
US4545746A (en) Rotation-preventing device for an orbiting piston-type fluid displacement
EP0122723B1 (fr) Mécanisme d'ajustement du jeu axial pour appareil à volutes à déplacement de fluide
EP0012615A1 (fr) Améliorations à des compresseurs à fluide du type à volutes imbriquées
US4548556A (en) Interfitting mechanism of spiral elements for scroll-type fluid displacement apparatus
US5738504A (en) Rotation preventing device for orbiting member of fluid displacement apparatus
EP0457603B1 (fr) Appareil de déplacement de fluide à spirales
EP0065261B1 (fr) Joint d'étanchéité axial pour une machine à déplacement à volutes imbriquées
US5435706A (en) Orbiting member fluid displacement apparatus with rotation preventing mechanism
EP0075053A1 (fr) Moyens anti-corrosion pour appareil de déplacement de fluide à volutes imbriquées
EP0122068B1 (fr) Mécanisme d'emboîtement des volutes pour un appareil à volutes à déplacement de fluide
US6033194A (en) Scroll-type fluid displacement apparatus with anti-wear plate mechanism
CA1259970A (fr) Dispositif du type a volutes et son organe anti-usure perfectionne pour la pompage de fluides
GB2167131A (en) Scroll-type rotary fluid-machine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): DE FR GB IT SE

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SANDEN CORPORATION

17P Request for examination filed

Effective date: 19830928

ITF It: translation for a ep patent filed

Owner name: BARZANO' E ZANARDO MILANO S.P.A.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REF Corresponds to:

Ref document number: 3175720

Country of ref document: DE

Date of ref document: 19870129

ET Fr: translation filed
RIN2 Information on inventor provided after grant (corrected)

Free format text: IIMORI, TAKAYUKI * TERAUCHI, KIYOSHI

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
EAL Se: european patent in force in sweden

Ref document number: 81304364.3

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20000906

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20000912

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20000918

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20000920

Year of fee payment: 20

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20010921

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 20010929

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Effective date: 20010921

EUG Se: european patent has lapsed

Ref document number: 81304364.3