EP0012615A1 - Améliorations à des compresseurs à fluide du type à volutes imbriquées - Google Patents

Améliorations à des compresseurs à fluide du type à volutes imbriquées Download PDF

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Publication number
EP0012615A1
EP0012615A1 EP79302900A EP79302900A EP0012615A1 EP 0012615 A1 EP0012615 A1 EP 0012615A1 EP 79302900 A EP79302900 A EP 79302900A EP 79302900 A EP79302900 A EP 79302900A EP 0012615 A1 EP0012615 A1 EP 0012615A1
Authority
EP
European Patent Office
Prior art keywords
fluid
end plate
orbiting scroll
affixed
scroll member
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.)
Withdrawn
Application number
EP79302900A
Other languages
German (de)
English (en)
Inventor
Kiyoshi Terauchi
Eizi Fukusima
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 Holdings Corp
Original Assignee
Sankyo Electric Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP15559078A external-priority patent/JPS5581294A/ja
Priority claimed from JP15559178A external-priority patent/JPS5581295A/ja
Application filed by Sankyo Electric Co Ltd filed Critical Sankyo Electric Co Ltd
Publication of EP0012615A1 publication Critical patent/EP0012615A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • 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
    • F04C2230/20—Manufacture essentially without removing material
    • 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
    • F04C2230/40—Heat treatment
    • F04C2230/41—Hardening; Annealing
    • 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
    • F05B2230/20—Manufacture essentially without removing material
    • 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
    • F05B2230/40—Heat treatment
    • F05B2230/41—Hardening; Annealing

Definitions

  • This invention relates to scroll type fluid compressor units.
  • a scroll type apparatus has been well known in the prior art as disclosed in, for example, U.S. Patent No. 801,182, and others, which comprises two scroll members each having an end plate and a spiroidal or involute spiral element. These scroll members are so maintained angularly and radially offset that their spiral elements interfit to make a plurality of line contacts between their spiral curved surfaces, thereby to seal off and define at least one fluid pocket. The relative orbital motion of these scroll members shifts the line contacts along the spiral curved surfaces and, therefore, the volume of the fluid pocket increases or decreases in dependence on the direction of the orbital motion. Therefore, a scroll type apparatus is suitable for handling fluids or for compressing, expanding or pumping them.
  • a scroll type compressor In comparison with conventional compressors of a piston type, a scroll type compressor has some advantages such as less number of parts, continuous compression of fluid and others. But, there have been several problems; primarily sealing of the fluid pocket, wearing of the spiral elements, and inlet and outlet porting.
  • the scroll members and other parts can be made of aluminium or aluminium alloy. If the scroll members are made of aluminium or an aluminium alloy, the sealing of the fluid pockets becomes insufficient owing to wearing.
  • a scroll type fluid compressor unit including a compressor housing having a fluid inlet port and a fluid outlet port, a fixed scroll member fixedly disposed within said compressor housing and having first end plate means to which first wrap means are affixed, and an orbiting scroll member orbitally disposed within said compressor housing and having second end plate means to which second wrap means are affixed, said first and second wrap means interfitting, being at a predetermined angular relationship, and having a plurality of line contacts so as to define at least one sealed off fluid pocket which moves with reduction in volume thereof upon orbital motion of said orbiting scroll member, thereby to compress the fluid in the pocket, wherein said fixed and orbiting scroll members are each formed of aluminium or an aluminium alloy, and at least one of the fixed and orbiting members has at least the surface of its wrap means and the end surface of its end plate means on which said wrap means are affixed formed of a material having anti-wearing properties.
  • One embodiment of the invention is an improved compressor unit of the scroll type which has excellent sealing and anti-wearing properties.
  • the dimensional accuracy of the scroll members is readily secured. Friction between the scroll members is reduced.
  • One embodiment of the invention is a scroll type fluid compressor unit which includes a compressor housing having a fluid inlet port and a fluid outlet port.
  • a fixed scroll member fixedly disposed which comprises first plate means to which first wrap means are affixed.
  • An orbiting scroll member is orbitally disposed within the housing and comprises second end plate means to which second wrap means are affixed.
  • the first and second wrap means interfit at a predetermined angular relationship to make a plurality of line contacts to define at least one sealed off fluid pocket.
  • the fluid pocket moves with reduction of volume thereof by the orbital motion of the orbiting scroll member.
  • the fluid in the pocket is thereby compressed.
  • the first and second scroll members are made of aluminium or an aluminium alloy.
  • One of the scroll members is treated by surface hardening the entire surface of its wrap means and the end surface of its end plate means on which the wrap means are affixed.
  • copper plating In order to effect the surface hardening, copper plating, anodic oxidation coating or hard chromium plating may be employed.
  • At least one -of scroll members is made of a high silicon aluminium alloy.
  • the entire surface of the scroll member has an anti-wearing property because many silicon crystals are dispersed in the surface. Therefore, a surface hardening treatment is not necessary.
  • one of scroll members is coated with a polytetrafluoroethylene coating.
  • the other scroll member is treated by the surface hardening, as above described.
  • the other scroll member is made of a high silicon aluminium alloy, such a surface hardening treatment is not necessary.
  • a refrigerant compressor unit 10 of an embodiment shown includes a compressor housing comprising a front end plate 11, a rear end plate 12 and a cylindrical body 13 connecting between those end plates.
  • Rear end plate 12 is shown formed integral with the cylindrical body and is provided with a fluid inlet port 14 and a fluid outlet port 15 formed therethrough.
  • a drive shaft 17 is rotatably supported by a radial needle bearing 16 in front end plate 11.
  • Front end plate 11 has a sleeve portion 18 projecting on the front surface thereof and surrounding drive shaft 17 to define a shaft seal cavity 181. Within the shaft seal cavity, a shaft seal assembly 19 is assembled on drive shaft 17.
  • a pulley 20 is rotatably mounted on sleeve portion 18 and is connected with drive shaft 17 to transmit an external drive power source (not shovm) to drive shaft 17 through belt means (not shown) wound around pulley 20.
  • a disk rotor 21 is fixedly mounted on an inner end of drive shaft 17 and is born on the inner surface of front end plate 11 through a thrust needle bearing 22 which is disposed concentric with drive shaft 17.
  • Disk rotor 21 is provided with a drive pin 23 projecting on the rear surface thereof. Drive pin 23 is radially offset from drive shaft 17 by a predetermined length.
  • Reference numerals 24 and 25 represent a pair of interfitting orbiting and fixed scroll members.
  • Orbiting scroll member 24 includes an end circular plate 241 and a wrap means or spiral element 242 affixed onto one end surface of the end plate.
  • End plate 241 is provided with a boss 243 projecting on the other end surface thereof.
  • Drive pin 23 is fitted into boss 243 with a radial needle bearing 26 therebetween, so that orbiting scroll member 24 is rotatably supported on drive pin 23.
  • a hollow member 27 having a radial flange 271 is fitted onto boss 243 non-rotatably by means of key and keyway connection.
  • Radial flange 271 is supported on the rear end surface of disk rotor 21 by a thrust needle bearing 28 which is disposed concentric with drive pin 23.
  • the axial length of hollow member 27 is equal to, or more than, the axial length of boss 243, so that the thrust load from orbiting scroll member 24 is supported on front end plate 11 through disk rotor 21. Therefore, the rotation of drive shaft 17 effects the orbital motion of orbiting scroll member 24 together with hollow member 27. Namely, orbiting scroll member 24 moves along a circle of a radius of the length between drive shaft 17 and drive pin 23.
  • Means 29 for preventing orbiting scroll member 24 from rotating during the orbital motion is disposed between end plate 241 of orbiting scroll member 24 and radial flange 271 of hollow member 27.
  • hollow member 27 comprises a cylindrical portion 272 having. a rectangular outer contour, on which a rectangular slider member 291 is fitted slidable in a radial direction.
  • Rectangular slider member 291 has a rectangular hole with one pair of parallel sides equal to one pair of parallel sides of the outer rectangle of cylindrical portion 272 and with the other pair of parallel sides longer than the other pair of sides of rectangular cylindrical portion 272 by at least twice length between drive shaft 27 and drive pin 23. Accordingly, slider member 291 is slidable on hollow member 27 in a radial direction along the longer parallel sides of the rectangular hole.
  • Slider member 291 is also fitted into a ring like member 292 which is non-rotatably fixed on the inner surface of cylindrical body 13 of the compressor housing by key and keyway connection (shown at 293 in Fig. 2).
  • the central hole of ring like member 292 is a rectangular hole with one pair of parallel sides equal to one pair of parallel sides of the outer rectangle of slider member 291 and with the other pair of parallel sides longer than the other parallel sides of the same outer rectangle by at least twice length between drive shaft 17 and drive pin 23, so that slider member 291 may be slidable within ring like member 292 in a radial direction perpendicular to the slide direction of it on hollow member 27.
  • hollow member 27 is permitted to move in two radial directions perpendicular to one another and, therefore, moves along a circle as a result of movement in the two radial directions but is prevented fr,om rotation. Therefore, the eccentric movement of drive pin 23 by the rotation of drive shaft 17 effects the orbital motion of orbiting scroll member 24 together with hollow member 27 without rotation.
  • the ring like member has a central hole permitting hollow member to axially pass therethrough and is formed with a depression in an end surface for receiving and slidably guide slider member 291.
  • This construction of the ring like member permits the ring like member itself to be thin.
  • the other fixed scroll member 25 also comprises an end circular plate 251 and a wrap means or spiral element 252 affixed on one end surface of the end plate.
  • End plate 251 is provided with a hole or a discharge port 253 formed at a position corresponding to the center of the spiral elements, and with an annular projection 254 on the rear end surface around discharge port 253.
  • Rear end plate 12 is provided with an annular projection 121 on the inner surface thereof around outlet port 15.
  • the outer radius of annular projection 121 is selected slightly shorter than the inner radius of annular projection 254.
  • Annular projection 121 is cut away along the outer edge of the projecting end to define an annular recess 122.
  • An annular elastic material for example, a rubber ring 30 is fitted into annular recess 122 and is compressedly held between interfitted annular projections 121 and 254, so that fixed scroll member 25 is elastically supported on annular projection 121 of the rear end plate.
  • Rubber ring 30 serves as a seal for sealing off a chamber 31 defined by annular projections 121 and 254 from the interior space 131 of the compressor housing. Chamber 31 connects between outlet port 15 and discharge port of fixed scroll member 25.
  • End plate 251 of fixed scroll member 25 is formed with a plurality of cut away portions 255 at its rear peripheral edge.
  • a plurality of projections 132 are formed on the inner surface of cylindrical body 13 of the compressor housing and are mated i 4 to ' cut away portions 255, so that fixed scroll member 25 is non-rotatably disposed within the compressor housing. Gaps 32 is maintained between the inner wall of cylindrical body 13 and the peripheral end of fixed scroll member 25, and, therefore, a chamber portion 33 surrounding annular projections 121 and 254 does not form a sealed off chamber within interior space 131 of the compressor housing. Chamber portion 33 communicates with inlet port 14.
  • the introduced fluid is taken into fluid pockets 1 and 2 (which are shown at dotted regions) which are defined by line contacts between orbiting spiral element 242 and fixed spiral element 252, as shown in Fig. 3a.
  • the line contacts shift by the orbital motion of orbiting spiral element 242 and, therefore, fluid pockets 1 and 2 angularly and radially move toward the center of spiral elements and decrease their volume, as shown in.Figs. 3b-3d. Therefore, the fluid in each pocket is compressed.
  • fluid is again taken into new formed fluid pockets 1 and 2, while old pockets connected together to form a reduced pocket and the already taken and compressed fluid is discharged from the pocket through discharge port 253.
  • disk rotor 21 fixedly mounted on drive shaft 17 is supported through thrust bearing 22 on front end plate 11, drive shaft 17 is securely and non-vibratingly supported by the use of a single needle bearing as a radial bearing.
  • annular elastic material 30, fixed and orbiting scroll members 25 and 24, rotation preventing means 29, hollow member 27, bearings 26 and 28, and a pre- assembly of drive pin 23, disk rotor 21, bearings 16 and 22, drive shaft 17 and front end plate 11, are inserted in this order into cylindrical body 13 having rear end plate 12, and the compressor is completed by securing front end plate 11 onto cylindrical body 13 by bolt means 34.
  • the radial sealing force at each line contact between fixed and orbiting spiral elements 252 and 242 is determined by the radius of the orbital motion of orbiting scroll member 24 or the offset length between drive shaft 17 and drive pin 23, and the pitch and thickness of each of fixed and orbiting spiral elements 252 and 242.
  • the distance between drive shaft 17 and drive pin 23 is preferably selected slightly larger than the half of the dimensional difference between the pitch of each spiral element and the total dimension..of thickness of fixed and orbiting spiral elements.
  • both scroll members 24 and 25 are made of aluminum or aluminum alloy by forging, casting or die casting, to make the compressor unit light.
  • aluminum alloy of No. 6051 in JIS (Japanese Industrial Standards) H 4140, which comprises by weight 0.40-0.8 % Si, up to 0.7 % Fe, 0.15-0.40 % Cu, up to 0.15 % Mn, 0.8-1.2 % Mg, 0.04-0.35 % Cr, up to 0.25 % Zn, up to 0.15 % Ti, and the balance essentially A1, is preferably used.
  • JIS Japanese Industrial Standards
  • aluminum alloy of AC2A by JIS, H 5202 which comprises 3.5-4.5 % Cu, 4.0-5.0 % Si, up to 0.2 % Mg, up to 0.5 % Zn, up to 0.8 % Fe, up to 0.5 % Mn, up to 0.2 % Ti and the balance of Al, is preferably used.
  • aluminum alloy of ADC 10 in JIS H 5302 (which comprises 2.0-4.0 % Cu, 7.5-9.5 % Si, up to 0.3 % Mg, up to 1.0 % Zn, up to 1.3 % Fe, up to 0.5 % Mn, up to 0.5 % Ni, up to 0.3 % Sn and the balance of Al), or ADC 12 in JIS H 5302 (which comprises 1.5-3.5 % Cu, 9.6-12.0 % Si, up to 0.3 % Mg, up to 1.0 % Zn, up to 1.3 % Fe, up to 0.5 % Mn, up to 0.5 % Ni, up to 0.3 % Sn and the balance of Al) is preferably used.
  • At least one of scroll members of aluminum or aluminum alloy is treated by surface hardening at its at least surface area in slidingly contact with one another, in this invention.
  • orbiting scroll member 24 is treated by surface hardening as shown at 35.
  • hard chromium plating, copper plating, and anodic oxidation coating can be selectively used. Since these treatments are well known per se in the prior art of aluminum and aluminum alloy surface treating technique, the description as to the concrete processes for producing such surface hardened coatings on to aluminum or aluminum alloy scroll members is omitted for the purpose of simplification of the description.
  • surface hardened coating 35 such as plated hard chromium coating, plated copper coating, or anodic oxidation coating on orbiting scroll member 24, establishes a reduced friction at contact portions between both scroll members 24 and 25. Therefore, not only orbiting scroll member 24 but also fixed scroll member 25 are protected from wearing due to sliding contact therebetween, so that the sealing of fluid pockets is maintained during long use.
  • Such a surface hardening treatment may be performed onto not orbiting scroll member 24 but fixed scroll member 25.
  • the application onto both scroll members is also preferable.
  • scroll members is made of high silicon aluminum alloy or anti-wearing aluminum alloy including high silicon such as about 12-25 wt%, such surface hardening treatment is not necessary.
  • the dimensional accuracy is obtained by machining.
  • the machined surface is subjected by exposure of many silicon crystals, so that the surface has an anti-wearing property.
  • Anti-wearing aluminum alloy like this is known as disclosed in U.S. Patent No. 3,514,286.
  • a polytetrafluoro- ethylene coating may be used onto the scroll member as shown in Fig. 4.
  • fixed scroll member 25 is coated by a surface hardening coating 36 similar to the coating 35 in Fig. 1, and orbiting scroll member 24 is coated by a polytetrafluoroethylene coating 37.
  • the surface hardening coating is not necessary.
  • a scroll type compressor. unit is obtained according to this invention, which is light and wherein the sealing of fluid pockets between both scroll members is maintained for a long time use. Furthermore, since scroll members are made light, dynamic unbalance is reduced. Moreover, the dimensional accuracy of scroll members can be readily obtained so that the sealing of fluid pockets is further secured.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP79302900A 1978-12-15 1979-12-14 Améliorations à des compresseurs à fluide du type à volutes imbriquées Withdrawn EP0012615A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP15559078A JPS5581294A (en) 1978-12-15 1978-12-15 Positive-displacement fluid compressor
JP155591/78 1978-12-15
JP155590/78 1978-12-15
JP15559178A JPS5581295A (en) 1978-12-15 1978-12-15 Positive-displacement fluid compressor

Publications (1)

Publication Number Publication Date
EP0012615A1 true EP0012615A1 (fr) 1980-06-25

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EP79302900A Withdrawn EP0012615A1 (fr) 1978-12-15 1979-12-14 Améliorations à des compresseurs à fluide du type à volutes imbriquées

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EP (1) EP0012615A1 (fr)
AU (1) AU5375079A (fr)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0065426A2 (fr) * 1981-05-20 1982-11-24 Sanden Corporation Outil à fabriquer des éléments en forme de volute
EP0066426A2 (fr) * 1981-05-20 1982-12-08 Sanden Corporation Outil à fabriquer des éléments en forme de volute
EP0075053A1 (fr) * 1981-09-22 1983-03-30 Sanden Corporation Moyens anti-corrosion pour appareil de déplacement de fluide à volutes imbriquées
EP0122067A1 (fr) * 1983-03-15 1984-10-17 Sanden Corporation Appareil à volutes pour transport de fluide ayant une volute à surface traitée
EP0122722A1 (fr) * 1983-03-15 1984-10-24 Sanden Corporation Dispositif d'étanchéité axiale pour un appareil à volutes de déplacement de fluide
DE3402548A1 (de) * 1984-01-26 1985-08-01 Leybold-Heraeus GmbH, 5000 Köln Verdraengermaschine
GB2167131A (en) * 1984-11-19 1986-05-21 Sanden Corp Scroll-type rotary fluid-machine
US4645436A (en) * 1984-11-19 1987-02-24 Sanden Corporation Scroll type fluid displacement apparatus with improved anti-wear device
EP0267559A1 (fr) * 1986-11-08 1988-05-18 Wankel GmbH Soufflante à piston rotatif
EP0286341A2 (fr) * 1987-04-04 1988-10-12 Sanden Corporation Compresseur à volute
EP0350790A2 (fr) * 1988-07-08 1990-01-17 Sanden Corporation Compresseur du type à spirales
EP0467492A1 (fr) * 1990-07-16 1992-01-22 Mitsubishi Jukogyo Kabushiki Kaisha Compresseur
DE4404054A1 (de) * 1993-02-09 1994-08-11 Toyoda Automatic Loom Works Kältemittel-Spiralkompressor mit Gehäuseschutzeinrichtungen
BE1010426A3 (nl) * 1996-07-16 1998-07-07 Atlas Copco Airpower Nv Werkwijze voor het vervaardigen van een spiraalcompressor.
US5791886A (en) * 1995-10-20 1998-08-11 Sanden Corporation Scroll type fluid displacement apparatus with an axial seal plate
US6033194A (en) * 1996-06-24 2000-03-07 Sanden Corporation Scroll-type fluid displacement apparatus with anti-wear plate mechanism
GB2548607A (en) * 2016-03-23 2017-09-27 Edwards Ltd Scroll pump tip sealing
US11359628B2 (en) * 2017-04-28 2022-06-14 Shanghai Highly New Energy Technology Co., Ltd. Scroll compressor including retaining wall housing electrical machinery mechanism

Citations (6)

* 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
FR2272277A1 (en) * 1974-05-24 1975-12-19 Unus Dei F Lli Rossato V Et S Rotary-piston air compressor - has sliders made from polyamide with spherical bronze powder charge and molybdenum disulphide
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

Patent Citations (6)

* 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
FR2272277A1 (en) * 1974-05-24 1975-12-19 Unus Dei F Lli Rossato V Et S Rotary-piston air compressor - has sliders made from polyamide with spherical bronze powder charge and molybdenum disulphide
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

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0065426A2 (fr) * 1981-05-20 1982-11-24 Sanden Corporation Outil à fabriquer des éléments en forme de volute
EP0066426A2 (fr) * 1981-05-20 1982-12-08 Sanden Corporation Outil à fabriquer des éléments en forme de volute
EP0065426A3 (en) * 1981-05-20 1983-08-17 Sanden Corporation Scroll manufacturing tool
EP0066426A3 (en) * 1981-05-20 1983-08-24 Sanden Corporation Scroll manufacturing tool
EP0075053A1 (fr) * 1981-09-22 1983-03-30 Sanden Corporation Moyens anti-corrosion pour appareil de déplacement de fluide à volutes imbriquées
EP0122722A1 (fr) * 1983-03-15 1984-10-24 Sanden Corporation Dispositif d'étanchéité axiale pour un appareil à volutes de déplacement de fluide
EP0122067A1 (fr) * 1983-03-15 1984-10-17 Sanden Corporation Appareil à volutes pour transport de fluide ayant une volute à surface traitée
US4540355A (en) * 1983-03-15 1985-09-10 Sanden Corporation Axial sealing device for a scroll-type fluid displacement apparatus
US4956058A (en) * 1983-03-15 1990-09-11 Sanden Corporation Scroll type fluid displacement apparatus with surface treated spiral element
DE3402548A1 (de) * 1984-01-26 1985-08-01 Leybold-Heraeus GmbH, 5000 Köln Verdraengermaschine
GB2167131A (en) * 1984-11-19 1986-05-21 Sanden Corp Scroll-type rotary fluid-machine
FR2574866A1 (fr) * 1984-11-19 1986-06-20 Sanden Corp Appareil de deplacement de fluide de type a spirale, muni d'un mecanisme de support d'arbre
US4645436A (en) * 1984-11-19 1987-02-24 Sanden Corporation Scroll type fluid displacement apparatus with improved anti-wear device
EP0267559A1 (fr) * 1986-11-08 1988-05-18 Wankel GmbH Soufflante à piston rotatif
EP0286341A3 (en) * 1987-04-04 1989-06-14 Sanden Corporation Scroll type compressor
EP0286341A2 (fr) * 1987-04-04 1988-10-12 Sanden Corporation Compresseur à volute
EP0350790A2 (fr) * 1988-07-08 1990-01-17 Sanden Corporation Compresseur du type à spirales
EP0350790A3 (en) * 1988-07-08 1990-05-16 Sanden Corporation Scroll type compressor
US5015163A (en) * 1988-07-08 1991-05-14 Sanden Corporation Scroll type compressor with radially outer support for fixed end plate
AU623413B2 (en) * 1988-07-08 1992-05-14 Sanden Corporation Scroll type compressor
EP0467492A1 (fr) * 1990-07-16 1992-01-22 Mitsubishi Jukogyo Kabushiki Kaisha Compresseur
DE4404054A1 (de) * 1993-02-09 1994-08-11 Toyoda Automatic Loom Works Kältemittel-Spiralkompressor mit Gehäuseschutzeinrichtungen
US5791886A (en) * 1995-10-20 1998-08-11 Sanden Corporation Scroll type fluid displacement apparatus with an axial seal plate
US6033194A (en) * 1996-06-24 2000-03-07 Sanden Corporation Scroll-type fluid displacement apparatus with anti-wear plate mechanism
BE1010426A3 (nl) * 1996-07-16 1998-07-07 Atlas Copco Airpower Nv Werkwijze voor het vervaardigen van een spiraalcompressor.
GB2548607A (en) * 2016-03-23 2017-09-27 Edwards Ltd Scroll pump tip sealing
GB2548607B (en) * 2016-03-23 2020-05-06 Edwards Ltd Scroll pump tip sealing
US11359628B2 (en) * 2017-04-28 2022-06-14 Shanghai Highly New Energy Technology Co., Ltd. Scroll compressor including retaining wall housing electrical machinery mechanism

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