WO2001059302A1 - Pompe a palettes - Google Patents

Pompe a palettes Download PDF

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Publication number
WO2001059302A1
WO2001059302A1 PCT/US2001/004396 US0104396W WO0159302A1 WO 2001059302 A1 WO2001059302 A1 WO 2001059302A1 US 0104396 W US0104396 W US 0104396W WO 0159302 A1 WO0159302 A1 WO 0159302A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
thrust
vane pump
chamber
thrust plate
Prior art date
Application number
PCT/US2001/004396
Other languages
English (en)
Inventor
Albert Cheuk-Yin Wong
Tom Wong
Johnny M. Paris
Gary Ray Minnis
Original Assignee
Delphi Technologies, Inc.
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 Delphi Technologies, Inc. filed Critical Delphi Technologies, Inc.
Publication of WO2001059302A1 publication Critical patent/WO2001059302A1/fr

Links

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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid

Definitions

  • a vane pump typically includes a cylindrical rotor supported for rotation inside of an oval-shaped rotor chamber defined by a cam ring surrounding the rotor.
  • the cam ring and the rotor define crescent-shaped cavities therebetween which are divided in to a plurality of pump chambers by a corresponding plurality of flat vanes carried in radial vane slots of the rotor.
  • the pump chambers expand into an inlet sector of the crescent-shaped cavities and collapse in a discharge sector of the cavities as the rotor rotates.
  • a thrust plate and a pressure plate are disposed on opposite sides of the cam ring and are squeezed together under spring tension to cover the rotor chamber. An opposite thrust face of the thrust plate is pinned between the cam ring and end wall of the housing.
  • a cam ring is disposed in the cavity between the thrust plate and pressure plate and has a circumferentially extending inner cam wall defining a rotor chamber of the cavity.
  • a rotor is supported in the rotor chamber for rotation about the longitudinal axis of the housing relative to the inner cam wall of the cam ring.
  • a plurality of vanes are slideably supported by the rotor for radial reciprocation in communication with the inner cam wall of the cam ring to define a plurality of dynamically expanding and diminishing volume sectors of the rotor chamber and which are operative to draw hydraulic fluid into the rotor chamber under low pressure and expel the hydraulic fluid under elevated pressure from the rotor chamber.
  • a resilient gasket is disposed between the first thrust face of the thrust plate and the end wall of the housing to define a sealed balance chamber therebetween.
  • Figure 3 is a sectional view taken generally along lines 3-3 of Figure i;
  • Figure 6 is a fragmentary sectional view taken generally along lines 6-6 of Figure 5;
  • a vane pump 10 constructed according to the invention includes a pump housing 12 having therein a drive shaft bore 14 open tlirough a first end 16 of the housing 12 and intersecting a flat bottom or end wall 18 of a large counter bore or cavity 20 in a second end 22 of the housing 12.
  • a control valve bore 24 in the housing 12 communicates with the counter bore 20 through a schematically represented internal passage 26 in the housing 12.
  • An inlet passage 28 in the housing 12 communicates with a reservoir of fluid (e.g., hydraulic fluid), not shown, and with the internal passage 26 tlirough an aperture 30.
  • a "rotating group" 32 of the vane pump 10 is captured in the cavity 20 between the end wall and a disc-shaped cover 34 closing the open end of the cavity 20.
  • An annular chamber 36 is defined between a cylindrical side wall 38 of the cavity 20 and the rotating group 32.
  • a seal ring 40 suppresses fluid linkage between the housing 12 and the cover 34.
  • the rotating group 32 is stationary relative to the pump housing 12 and includes a thrust plate 42 seated on the flat end wall 18 of the cavity 20, a pressure plate 44 spaced axially from the thrust plate 42, and a cam ring 46 disposed in the cavity 20 between the thrust plate 42 and the pressure plate 44.
  • a plurality of dowel pins 48 traverse the thrust plate 42, pressure plate 44, cam ring 46, and the housing 12 and prevent relative rotational movement therebetween about a longitudinal center line or axis 50 of the pump housing 12.
  • the outer surface 80 of the rotor 78 cooperates with the inner wall 52 of the cam ring 46 in defining a pair of crescent-shaped cavities 84A, 84B of the rotor chamber 66 on radially opposite sides of the rotor 78, as best illustrated in Figure 3.
  • the rotor 78 is formed with a plurality of radial vane slots 86 which intersect the outer surface 80 and each of the end walls 82 A, 82B.
  • a corresponding plurality of flat vanes 88 are supported in respective ones of vane slots 86 for sliding radial reciprocation relative to the rotor 78.
  • Each flat vane 88 has an outboard lateral edge 90 (Figure 1) bearing against the oval-shaped inner wall 52 of the cam ring 46, and a pair of radial edges 92 (Figure 5) separated from the planar side 66 of the pressure plate 46 and the planar side 57 of the thrust plate 44 by clearance dimensions Di, D , respectfully ( Figure 6).
  • the vanes 88 divide the crescent-shaped cavities 84A, 84B into a plurality of pump chambers 93 ( Figure 3) which expand in each of a pair of diagonally opposite inlet sectors of the crescent- shaped cavities, and collapse in each of a pair of diagonally opposite discharge sectors of the crescent-shaped cavities in conventional fashion concurrent with the direction of rotation R of the rotor 78.
  • the thrust plate 42 has a pair or diametrically opposed notches 94A,
  • the thrust plate 42 has a pair of diametrically opposed tlirough ports 98A, 98B extending through the plate 42 from in the second thrust face 57 thereof to the first thrust face 56.
  • the pressure plate 44 has a pair of diametrically opposed shallow recesses or grooves 100 A, 100B in the planar side 60 thereof which are angularly aligned with the ports 98 A, 98b, respectively, and with the discharge sectors of the crescent-shaped cavities 84A, 84B, respectively.
  • the end wall 82 A of the rotor defines an annular outer land 108 between the annular groove and the cylindrical outer surface 80 of the rotor.
  • the annular outer land 108 is interrupted by each of the radial vane slots and rums toward the longitudinal centerline 50 on opposite sides of each vane slot to define a plurality of pairs of radial lands 110 integral with the outer land.
  • Radially inboard of the annular groove 106, the end wall 82A of the rotor defines an annular inner land 112 between the annular groove 106 and the splined bore 76 in the rotor.
  • the surface area of the annular groove 106 between the outer land 108 and the inner land 112 constitutes a reaction portion of the planar end wall 82 A of the rotor having a surface area of at least 30% of the surface area of the planar end wall 82 A.
  • the groove 106 cooperates with the planar side 60 of the pressure plate in defining an annular first longitudinal balance chamber 116.
  • the groove 114 cooperates with the planar side 56 of the thrust plate in defining an annular second longitudinal balance chamber 118.
  • the first longitudinal balance chamber communicates with the discharge chamber 70 through a schematically represented passage 120 in the pressure plate.
  • the second longitudinal balance chamber communicates with the first balance chamber 116 through the vane slots 86 under the vanes 88 therein.
  • the annular inner and outer lands 112, 108 cooperate with the planar side 60 of the pressure plate in defining fluid seals on opposite sides of the annular groove 106 even though separated by the clearance dimension Di.
  • the inner and the outer lands on opposite sides of the annular groove 114 in the end wall 82B of the rotor cooperate with the planar side 56 of the thrust plate in defining fluid seals on opposite sides of the annular groove 114 even though separated from the planar side 56 by the clearance dimension D 2 .
  • the close fit between the vanes 88 and the vane slots 86 suppresses fluid leakage from the balance chambers through the vane slots.
  • the outer lands also separate the first and the second balance chambers from the aforesaid inlet and discharge ports of the vane pump.
  • a resilient gasket or seal 122 fabricated of a suitable rubber or synthetic plastic material resistant to hydraulic fluid is disposed between the first thrust face 56 of the thrust plate 42 and the facing end wall 18 of the housing 12.
  • the gasket 106 is compressed between the thrust plate 42 and housing end wall 18 and defines at least one and preferably at least two bounded, sealed balance chambers 124A, 124B which are isolated by the gasket 106 from the chamber 36 and the drive shaft bore 14 of the housing 12.
  • the thrust plate 42 preferably is formed with grooves 126 in the first thrust face 56 which outline the balance chamber regions 124A, 124B.
  • the size and shape of the balance chambers 124A, 124B are selected to capture within the balance chambers 124 A, 124B a volume of the high pressure hydraulic fluid under the discharge pressure which is distributed evenly across the area of the first thrust face surface 56 confined by the balance chambers 124A, 125B and exerts an axial hydraulic balancing force F 3 ( Figures 1 and 8) in the axial direction against the first thrust face 56 which is preferably equal to and counteracts the hydraulic fluid force F 4 exerted on the second thrust face 57 from the rotor chamber 66, so as to balance the thrust plate 42 in hydraulic equilibrium in the direction of the axis 50, as will be explained in greater detail below.
  • fluid at substantially atmospheric pressure is delivered to the annular chamber 36 around the rotating group through the inlet passage 28, the aperture 30, and the internal passage 26 in the pump housing 12.
  • the expanding pump chamber 93 in the inlet sectors of the crescent-shaped cavities 84A, 84B are filled with hydraulic fluid through the inlet ports defined by the notches 94 A, 96B and 94 A, 96B.
  • the fluid in the pump chambers is transported by the rotor 78 to the discharge sectors of the crescent- shaped cavities 84A, 84B and expelled through the discharge ports 98A, 98B of the thrust plate 42 and the recesses 100A, 100B of the pressure plate 44 into the discharge chamber 70.
  • the fluid in the discharge chamber induces a net pressure force on the pressure plate 44 represented by a schematic force vector Fi, Figure 1, which reacts evenly across the exposed area of the pressure plate.
  • the net pressure force represented by the schematic vector Fj thrusts the rotating group toward the flat bottom 18 of the counterbore 20 for enhanced suppression of fluid leakage from between the planar side of the thrust plate and the end 58 of the cam ring and between the planar side of the pressure plate and the end 61 of the cam ring.
  • the fluid in the discharge sectors exerts a hydraulic pressure force F 3 on the second thrust face 57 of thrust plate 41 which urges the thrust plate 42 axially away from the rotor 78 and cam ring 46 toward the end wall 18 of the housing 12.
  • the hydraulically balanced thrust plate 42 has been surprisingly shown to perform best when used in combination with the hydraulically balanced rotor 78.
  • the balanced thrust plate 42 has shown to improve volumetric efficiency of a vane pump- by about 20% when used with a conventional non-hydraulically balanced rotor. A gain in volumetric efficiency of about 58% was shown when the hydraulically balanced thrust plate 42 was used together with the hydraulically balanced rotor 78.

Abstract

L'invention concerne une pompe à palettes (10) comprenant un rotor cylindrique (78) tournant à l'intérieur d'une chambre de rotor (66) de forme ovale définie par un anneau excentrique (46) autour du rotor (78). Une plaque de poussée (42) et une plaque de pression (44) couvrent la chambre du rotor (66) sur les côtés opposés de l'anneau excentrique (46), et sont comprimées ensemble par une force de pression due au fluide dans une chambre de décharge (70) de la pompe à palettes (10) à une pression de décharge correspondante. Une première face de poussée (56) de la plaque de poussée (42) est pressée contre une paroi d'extrémité (18) d'une cavité (20) d'un logement de pompe (12) dans laquelle les composants sont installés. Le fluide, sous pression de décharge, est admis dans une ou plusieurs chambres d'équilibre (124A, 124B) entre la plaque de poussée (42) et la paroi d'extrémité (18) du logement (12). Les chambres d'équilibre (124A, 124B) sont définies par un joint (122) s'encastrant dans une rainure (126) de la première face de poussée (56). Le fluide, sous pression de décharge dans les chambres d'équilibre (124A, 124B), permet de compenser une fraction de la force de pression sur la plaque de poussée (42) sur une seconde face de poussée (57) opposée en raison d'une arrivée de fluide de la chambre de rotor (66) dans laquelle le rotor (78) tourne, de manière à placer la plaque de poussée (42) en équilibre axial statique.
PCT/US2001/004396 2000-02-11 2001-02-08 Pompe a palettes WO2001059302A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US18181700P 2000-02-11 2000-02-11
US60/181,817 2000-02-11

Publications (1)

Publication Number Publication Date
WO2001059302A1 true WO2001059302A1 (fr) 2001-08-16

Family

ID=22665931

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2001/004396 WO2001059302A1 (fr) 2000-02-11 2001-02-08 Pompe a palettes

Country Status (1)

Country Link
WO (1) WO2001059302A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103075338A (zh) * 2011-10-25 2013-05-01 丹佛斯公司 叶片单元机
CN105822543A (zh) * 2016-06-02 2016-08-03 李钢 一种转子径向力平衡的叶片泵

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3664776A (en) * 1970-08-17 1972-05-23 Continental Machines Variable volume vane pump
US5266018A (en) * 1992-07-27 1993-11-30 Vickers, Incorporated Hydraulic vane pump with enhanced axial pressure balance and flow characteristics
DE4326627A1 (de) * 1993-08-07 1995-02-09 Zahnradfabrik Friedrichshafen Flügelzellenpumpe
EP0959249A2 (fr) * 1998-05-18 1999-11-24 Delphi Technologies, Inc. Pompe à palettes

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3664776A (en) * 1970-08-17 1972-05-23 Continental Machines Variable volume vane pump
US5266018A (en) * 1992-07-27 1993-11-30 Vickers, Incorporated Hydraulic vane pump with enhanced axial pressure balance and flow characteristics
DE4326627A1 (de) * 1993-08-07 1995-02-09 Zahnradfabrik Friedrichshafen Flügelzellenpumpe
EP0959249A2 (fr) * 1998-05-18 1999-11-24 Delphi Technologies, Inc. Pompe à palettes
US6050796A (en) 1998-05-18 2000-04-18 General Motors Corporation Vane pump

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103075338A (zh) * 2011-10-25 2013-05-01 丹佛斯公司 叶片单元机
US9279424B2 (en) 2011-10-25 2016-03-08 Danfoss A/S Vane cell machine having plates containing axial moving inserts bearing against the rotor
CN103075338B (zh) * 2011-10-25 2016-12-28 丹佛斯公司 叶片单元机
CN105822543A (zh) * 2016-06-02 2016-08-03 李钢 一种转子径向力平衡的叶片泵

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