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US3852003A - Pressure-sealed compressor - Google Patents

Pressure-sealed compressor Download PDF

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Publication number
US3852003A
US3852003A US00359030A US35903073A US3852003A US 3852003 A US3852003 A US 3852003A US 00359030 A US00359030 A US 00359030A US 35903073 A US35903073 A US 35903073A US 3852003 A US3852003 A US 3852003A
Authority
US
United States
Prior art keywords
rotor
compressor
high pressure
actuator surface
vanes
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.)
Expired - Lifetime
Application number
US00359030A
Other languages
English (en)
Inventor
G Adalbert
J Hess
E Linder
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Application granted granted Critical
Publication of US3852003A publication Critical patent/US3852003A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S418/00—Rotary expansible chamber devices
    • Y10S418/01—Non-working fluid separation

Definitions

  • a vane compressor has a rotor with radial vanes mounted in a housing cavity bounded by an endless actuator surface engaged by the outer ends of the vanes, and laterally bounded by two end walls having confronting stationary faces slidingly engaged by the rotor end faces to form clearance gaps.
  • the end walls have conduits communicating with a high pressure container housing connected with the outlet of the housing, and opening in ports on the stationary housing faces, respectively, so as to fill and seal the gaps with high pressure fluid.
  • the ports are longer in circumferential than in radial direction, and are located in an imaginary axial plane in which the vanes, which are completely inward pushed by the actuator surface, are located.
  • Pressure ducts in the end walls are connected through an annular recess in the rotor shaft with an annular space in therotor whichis connected with the radially inner ends of the vane slots.
  • the present invention relates to rotary compressors, particularly vane compressors which have a rotor whose end faces form clearance gaps with lateral stationary faces.
  • the US. Pat. No. 2,654,532 discloses a rotary vane compressor in which high pressure oil from the output is used as sealing medium for the clearance gaps.
  • the oil is supplied from the high pressure outlet along the rotor shaft to the end faces of the rotor where it is required for sealing.
  • the actual amount of oil reaching the clearance gaps cannot be determined and may be irregular.
  • the arrangement of the prior art has the disadvantage that the oil used for sealing the clearance gaps of compressor is not used in the optimal manner, since oil is also supplied to parts of the compressor where the sealing is not necessary.
  • a comparatively large flow of oil along the rotor shaft is necessary in the prior art. It cannot be avoided that such large amounts of oil also flow in the expanding and contracting chambers formed by the vanes and by the actuator suface surrounding the same. The space in the contracting chambers is thus reduced, and a lesser amount ofoil is pressed into the outlet, which reduces the efficiency of the compressor.
  • the U.S. Pat. No. 1,776,921 discloses a rotary vane compressor in which oil, under the outlet pressure of the compressor, is used as a sealing and lubricating medium.
  • oil flows out of a'high pressure container through a central bore in the rotor shaft to the radial slots in which the vanes are mounted for radial movement.
  • the oil serves on the one hand for pressing the vanes against the endless actuator camming surface, and on the other hand seals and lubricates the vanes guided in the vane slots.
  • the disadvantages explained above are present also in this compressor.
  • Another object of the invention is to supply fluid from the high pressure outlet of the compressor, to the clearance gaps between the rotor end faces and lateral stationary faces of the housing.
  • the lateral end walls of the housing which have the stationary end faces are provided with conduits, having one end communicating with high pressure outlet means, and another end formed as a port in the respective stationary face.
  • ports in the lateral stationary faces are oblong and curved, and longer in circumferential direction than in radial direction.
  • the distance between the radially outer edge of each port, and a circle on the stationary face having the diameter 'of the rotor, is between 2 and It is particularly advantageous if two-thirds of the area of the port are located on the high pressure side,
  • one-third of the port is located on the low pressure side of an imaginary axial plane passing through the diametrically located rotor portions where the vanes assume their innermost position in the vane slots due to the action of the endless camming actuator surface on the outer ends of the vanes.
  • FIG. 1 is an axial sectional view taken on line I-I in FIG. 2;
  • FIG. 2 is a cross sectional view taken along line 11-11 in FIG. 1.
  • the illustrated compressor has housing means which substantially include five parts, namely a left end wall 1 covered by a cover 17, an annular central housing part 3 having an inner ellipsoid camming actuator face 3c, a right end wall 2, and a container 23 secured to cover 17 by screws 17a and enveloping the end wall 2 and the central housing part 3.
  • Rotor means which include a rotor 5 having end faces 5a and 5b, and a rotor drive shaft 6'which is secured to the bottom portion 50 of rotor 5 at one end, and has another end projecting out of the housing for being driven by a suitable motor.
  • the outer cylindrical surface 5 of rotor 5 has a diameter which matches the length of the smaller axis of the ellipsoid inner endless actuator surface 3c so that a diametrical axial plane 29 is located between two crescentshaped portions of the cavity 4 located between the rotor surface 5' and the inner endless actuator surface 36.
  • the end wall 1 is integral with, or secured to, atubular pintle 9 which projects inward into the cavity 4, and more particularly into a cylindrical bore in rotor 5;
  • Rotor shaft 6 passes through the interior of tubular pintle 9 and has two journal portions 6b and 6c located in bearings 8 and 7 provided in the interior of the tubular pintle 9.
  • Bearing 8 is located in a portion of the pintle 9 which projects outward from end wall 1.
  • the shaft portion between journal portions 6b and-6c has an annular recess 6a communicating at one end through a bore and throttle 32 in the wall of pintle 9, with an annular space 31 communicating with the inner ends of the radial slots 12 in which vanes 13 are mounted for radial movement.
  • the other end of recess is connected by a duct 30 with liquid 27 in the lower portion of container 23.
  • A'thrust bearing 11 preferably a needle bearing, is mounted between the inner free end of pintle 9 and a corresponding shoulder of the bottom portion'5c of sure of the fluid supplied through the duct means 30, 6a, 32, 31 to the inner ends of the vanes 13.
  • the two crescent-shaped spaces between the rotor and the inner endless actuator surface 3c are divided by diametrically disposed vanes 13 into expanding suction chambers 14b, and contracting pressure chambers 19c.
  • Suction chambers communicate through radial inlet passages 14, and axially extending bores 14a, with the inlet means 15 through an annular channel 16 in cover 17.
  • Cover 17 has a tubular portion through which shaft 6 passes, sealed by sealing means 18.
  • the high pressure chambers 19c communicate through outlets 19 and leaf spring check valves 20 with axial pressure passages 21 provided with filter outlets 22 opening into the interior of the container 23 which has an outlet 25, protected by a baffle 24, and contains liquid 27 under high pressure.
  • both end walls 1 and 2 are provided with conduits 26 whose lower ends communicate with the interior of high pressure container 23, and receive liquid therefrom.
  • the lower portion of conduit 26 is covered in FIG. 1 by the duct 30, but the extension of conduit 26 in end wall 1 is the same as in end wall 2.
  • a portion of conduit 26 is omitted in end wall 2 for the sake of clarity, and it will be understood that conduit 26 passes around the recess 20 in end wall 2, and passes around the inner bore of the tubular pintle 9 in end wall 1.
  • each port 28 is arcuate and oblong in circumferential direction, so that the circumferential extension of each port 18 is greater than its radial dimension.
  • the radially outer edge or boundary 28' of each port 28 and the outer rotor surface 5' is between 2 and 5 mm., and preferably 4 mm.
  • the aforementioned circumferential extension ofeach port 28 is equivalent to 10", but it may rise to l7.
  • Two-thirds of the area of each port 28 are located on the high pressure side of an imaginary diametrical axial plane 29, and one-third on the low pressure side of plane 29 which passes through the rotor axis, and through the generatrix of the cylindrical outer rotor surface 5 where the vanes 13 are in the innermost positions in slots 12.
  • two-thirds of the area of port 28 is located on the side of plane 29 facing the outlets 19, and one-third of the area of port 28 is located on the side of plane 29 facing the inlets 14.
  • vanes 13 slide along the endless elipsoid inner camming actuator surface 30 so that chambers 14b expand and suck the fluid to be compressed from the inlet openings 14, axial conduits 14a, annular space 16 and inlet 15.
  • the spaces 19c contract so that the compressed fluid is discharged through the leaf spring check valves 20 into the outlet passages 21 and through the filters 22 into the high pressure container 23 from where the fluid is discharged through outlet 25.
  • the stored oil 27 is pressed into the conduits 26 in the end walls 1 and 2 and into the duct 30 in end wall 1. Liquid under pressure flows out of the ports 28 in the confronting stationary faces 1a and 2a of the end walls 1 and 2, and is pressed into the clearance gaps between stationary faces la and 2a and rotating rotor end faces 5a and 5b.
  • Oil is also pressed out of pressure container 23 into the duct 30 from where it flows through the recess 6a in rotor 6, the throttle 32, and annular connecting space 31 into the inner ends of the vane slots 12 so that the vanes 13 are pressed radially outward into engagement of their outer ends with the endless inner camming actuator surface 3c, sealing the expanding suction chambers 14b from the contracting pressure chambers 19b.
  • the oil in shaft recess 6a lubricates the bearings 7 and 8 of the rotor shaft 6.
  • the elipsoid shape of the actuator surface 3c of the central housing wall 3 which exerts a cam action on the vanes 13, is geometrically designed so that the radial stroke of two diametrically arranged vanes 13 in outward and inward direction, corresponds in every position of rotor 5 to an exactly equal length of the strokes in inward and outward directions of the two vanes 13 which are angularly displaced in relation to the first two vanes 13. This has the result that the volume of liquid in the common annular space 31 is constant in every position of rotor S with vanes 13.
  • the ellipsoid inner actuator surface 3c which is suitable for a two-flow compressor, may be replaced with a circular inner actuator surface having an axis eccentric to the rotor axis so that the compressor is a singleflow compressor.
  • the ellipsoid endless inner actuator surface 30 with a circular portion parallel to the outer cylindrical surface of the rotor so that the sealing between the rotor 5 and the respective portions of the inner endless actuator surface 3c is improved.
  • the imaginary plane 29, which determines the position of the ports 28, passes through the rotor axis and the generatrix of the outer rotor surface, which is located in the center of the regions where the outer surface of the rotor and the circular portions of the inner surface3c are parallel.
  • Pressure-sealed compressor comprising housing means including a central housing part having a cylindrical cavity surrounded by an endless inner actuator surface, a pair of end walls closing the ends of said cavity and having confronting stationary faces, a tubular pintle on one of said end walls, and inlet and outlet means for a fluid, said housing means further including a container for high pressure fluid communicating with said outlet means and having an outlet for high pressure fluid; rotor means mounted on said housing means for rotation about an axis, and including a rotor having rotor end faces slidingly engaging said stationary faces and forming clearing gaps therewith, a drive shaft portion mounted in said tubular pintle for rotation and including a thin shaft portion formed with an annular recess, and a plurality of vanes respectively mounted in radial slots of said rotor and having outer ends slidingly engaging said actuator surface for forming expanding and contracting chambers between said rotor and said actuator surface, said inlet and outlet means communieating with said chambers, said rotor being formed with an annular space surrounding said pin
  • Pressure-sealed compressor comprising housing means including a central housing part forming a cylindrical cavity surrounded by an endless inner actuator surface, a pair of end walls-closing the ends of said cavity and having confronting stationary faces, and inlet means and outlet means for a fluid; rotor means mounted in said housing means for rotation about an axis, and including a rotor having rotor end faces slidingly engaging said stationary faces and forming clearance gaps therewith, and at least one vane mounted in a radial slot of said rotor and having an outer end slidingly engaging said actuator surface for forming expanding and contracting chambers between said rotor and said actuator surface, said inlet means and outlet means on said housing means communicating with said expanding and contracting chambers, respectively; and each of said end walls being formed with a conduit having one end connected with said outlet means and the other end formed as a port in the respective stationary face of the respective end wall opening into the respective gap between the respective stationary face and rotor end face so that fluid is pressed into both gaps for sealing the same against leakage,
  • said rotor means include four vanes forming in said cavity between said rotor and said actuator surface two expanding suction chambers and two contracting pressure chambers alternating with said suction chambers; wherein said actuator surface places diametrically disposed vanes simultaneously in innermost positions when passing through an imaginary axial plane whereby on one side of said imaginary plane high pressure, and on the other side of said plane low pressure prevails in said cavity; and wherein said ports are located in said imaginary axial plane and have port portions located on opposite sides of said imaginary axial plane.
  • dial outer boundary of said port is spaced from the outer surface of said rotor a radial distance between 2 and 5 millimeters.

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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)
US00359030A 1972-05-12 1973-05-10 Pressure-sealed compressor Expired - Lifetime US3852003A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2223156A DE2223156C2 (de) 1972-05-12 1972-05-12 Flügelzellenverdichter

Publications (1)

Publication Number Publication Date
US3852003A true US3852003A (en) 1974-12-03

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ID=5844712

Family Applications (1)

Application Number Title Priority Date Filing Date
US00359030A Expired - Lifetime US3852003A (en) 1972-05-12 1973-05-10 Pressure-sealed compressor

Country Status (3)

Country Link
US (1) US3852003A (de)
JP (1) JPS5828434B2 (de)
DE (1) DE2223156C2 (de)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3989490A (en) * 1973-10-05 1976-11-02 Robert Bosch G.M.B.H. Oil separator, especially for a cooling medium compressor
US4248575A (en) * 1979-01-29 1981-02-03 Robert Bosch Gmbh Rotary fluid pressure biased vane compressor with pressure release means
US4260343A (en) * 1979-01-29 1981-04-07 Robert Bosch Gmbh Vane compressor
US4341506A (en) * 1979-08-14 1982-07-27 Gutehoffnungshutte Sterkrade A.G. Apparatus for the generation of compressed air
US4408969A (en) * 1980-05-31 1983-10-11 Diesel Kiki Co., Ltd. Vane compressor having improved rotor supporting means
US4470778A (en) * 1980-11-10 1984-09-11 Sanden Corporation Scroll type fluid displacement apparatus with oil separating mechanism
US4516918A (en) * 1982-05-25 1985-05-14 Trw Inc. Pump assembly
GB2156333A (en) * 1984-03-12 1985-10-09 Leon Kruss Brick
US4571164A (en) * 1982-06-18 1986-02-18 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
US4668172A (en) * 1983-02-12 1987-05-26 Diesel Kiki Co., Ltd. Compressor having discharge valve means adapted to enhance the coefficient of performance of the compressor
EP0264005A2 (de) * 1986-10-09 1988-04-20 Diesel Kiki Co., Ltd. Trennschieberkompressor
US4810177A (en) * 1982-06-18 1989-03-07 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
US5499515A (en) * 1993-06-23 1996-03-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Rotary vane-type compressor

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53126361A (en) * 1977-04-11 1978-11-04 Teijin Ltd Ombre tone fabric
GB2012626B (en) * 1977-12-29 1982-04-15 Seiko Instr & Electronics Oil separator
JPS57174887A (en) * 1981-04-20 1982-10-27 Matsushita Electric Ind Co Ltd Magnetron oscillator circuit
JPS6211355Y2 (de) * 1981-04-24 1987-03-17
JPS5818588A (ja) * 1981-07-24 1983-02-03 Toyoda Autom Loom Works Ltd スライドベ−ン型回転圧縮機
JPS5851292A (ja) * 1981-09-21 1983-03-25 Matsushita Electric Ind Co Ltd ロ−タリ−式流体機械
DE3840764A1 (de) * 1988-12-03 1990-06-07 Bosch Gmbh Robert Fluegelzellenverdichter
DE4035463C2 (de) * 1990-11-08 2000-05-11 Bosch Gmbh Robert Flügelzellenkompressor
JP2938203B2 (ja) * 1991-03-08 1999-08-23 株式会社東芝 流体圧縮機
SA94140669B1 (ar) * 1993-04-27 2006-03-01 كارير كوربوريشن ضاغط دوار مع حقن للزيت
JPH08296575A (ja) * 1995-04-25 1996-11-12 Smc Corp 回転ベーン形圧縮機及び真空ポンプ

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB415030A (en) * 1933-02-11 1934-08-13 John Arthur Improvements in or relating to rotary fluid motors, compressors and the like
US2522824A (en) * 1944-08-29 1950-09-19 Thomas L Hicks Rotary compressor
GB692690A (en) * 1952-03-04 1953-06-10 George Henry Thomas Williams Improvements in or relating to rotary elastic fluid operated motors
US2816702A (en) * 1953-01-16 1957-12-17 Nat Res Corp Pump
US3038414A (en) * 1958-06-05 1962-06-12 Vanton Pump & Equipment Corp Pump
US3191853A (en) * 1964-11-16 1965-06-29 Worthington Corp Rotary compressor
US3480204A (en) * 1968-03-26 1969-11-25 Borg Warner Lubrication system for rotary compressor

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2639855A (en) * 1948-02-06 1953-05-26 William T Daniels Variable vacuum and pressure rotary pump
GB653295A (en) * 1948-12-16 1951-05-09 Bird Mfg Co Ltd Improvements in and relating to rotary compressors and/or vacuum pumps and the like
US3295752A (en) * 1966-04-04 1967-01-03 Worthington Corp Rotary vane compressor
JPS4530767Y1 (de) * 1967-09-07 1970-11-25
US3434656A (en) * 1967-09-14 1969-03-25 Worthington Corp Lubrication system for rotary vane compressors
US3434655A (en) * 1967-10-23 1969-03-25 Worthington Corp Rotary compressor

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB415030A (en) * 1933-02-11 1934-08-13 John Arthur Improvements in or relating to rotary fluid motors, compressors and the like
US2522824A (en) * 1944-08-29 1950-09-19 Thomas L Hicks Rotary compressor
GB692690A (en) * 1952-03-04 1953-06-10 George Henry Thomas Williams Improvements in or relating to rotary elastic fluid operated motors
US2816702A (en) * 1953-01-16 1957-12-17 Nat Res Corp Pump
US3038414A (en) * 1958-06-05 1962-06-12 Vanton Pump & Equipment Corp Pump
US3191853A (en) * 1964-11-16 1965-06-29 Worthington Corp Rotary compressor
US3480204A (en) * 1968-03-26 1969-11-25 Borg Warner Lubrication system for rotary compressor

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3989490A (en) * 1973-10-05 1976-11-02 Robert Bosch G.M.B.H. Oil separator, especially for a cooling medium compressor
US4248575A (en) * 1979-01-29 1981-02-03 Robert Bosch Gmbh Rotary fluid pressure biased vane compressor with pressure release means
US4260343A (en) * 1979-01-29 1981-04-07 Robert Bosch Gmbh Vane compressor
US4341506A (en) * 1979-08-14 1982-07-27 Gutehoffnungshutte Sterkrade A.G. Apparatus for the generation of compressed air
US4408969A (en) * 1980-05-31 1983-10-11 Diesel Kiki Co., Ltd. Vane compressor having improved rotor supporting means
US4470778A (en) * 1980-11-10 1984-09-11 Sanden Corporation Scroll type fluid displacement apparatus with oil separating mechanism
US4516918A (en) * 1982-05-25 1985-05-14 Trw Inc. Pump assembly
US4571164A (en) * 1982-06-18 1986-02-18 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
US4717321A (en) * 1982-06-18 1988-01-05 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
US4810177A (en) * 1982-06-18 1989-03-07 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
US4668172A (en) * 1983-02-12 1987-05-26 Diesel Kiki Co., Ltd. Compressor having discharge valve means adapted to enhance the coefficient of performance of the compressor
GB2156333A (en) * 1984-03-12 1985-10-09 Leon Kruss Brick
EP0264005A2 (de) * 1986-10-09 1988-04-20 Diesel Kiki Co., Ltd. Trennschieberkompressor
EP0264005A3 (en) * 1986-10-09 1988-11-17 Diesel Kiki Co., Ltd. Sliding-vane rotary compressor
US5499515A (en) * 1993-06-23 1996-03-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Rotary vane-type compressor

Also Published As

Publication number Publication date
JPS5828434B2 (ja) 1983-06-15
DE2223156C2 (de) 1985-02-14
DE2223156A1 (de) 1973-11-29
JPS4949207A (de) 1974-05-13

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