EP0674105A1 - Flügelzellenpumpe - Google Patents

Flügelzellenpumpe Download PDF

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Publication number
EP0674105A1
EP0674105A1 EP95200457A EP95200457A EP0674105A1 EP 0674105 A1 EP0674105 A1 EP 0674105A1 EP 95200457 A EP95200457 A EP 95200457A EP 95200457 A EP95200457 A EP 95200457A EP 0674105 A1 EP0674105 A1 EP 0674105A1
Authority
EP
European Patent Office
Prior art keywords
fluid
stator
rotor
vane pump
rotary vane
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
EP95200457A
Other languages
English (en)
French (fr)
Other versions
EP0674105B1 (de
Inventor
Jean Joseph Botti
Jerry Myron Roethlisberger
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.)
Delphi Automotive Systems France
Motors Liquidation Co
Original Assignee
Delphi Automotive Systems France
Motors Liquidation Co
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 Automotive Systems France, Motors Liquidation Co filed Critical Delphi Automotive Systems France
Publication of EP0674105A1 publication Critical patent/EP0674105A1/de
Application granted granted Critical
Publication of EP0674105B1 publication Critical patent/EP0674105B1/de
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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/05—Speed
    • F04C2270/054—Speed linear

Definitions

  • This invention relates to a rotary vane pump, and in particular to a rotary vane pump which is usable in a power steering system of a motor vehicle.
  • Designs of rotary vane pump are well known. These well known designs typically comprise a stator which has a cylindrical bore, and a rotor having a longitudinal axis about which the rotor rotates in the bore. Either the longitudinal axis of the bore is offset from the longitudinal axis of the rotor, or the bore has a contoured inner surface.
  • the rotor has a number of circumferentially spaced, radially extending, slots therein.
  • a vane is positioned in, and slidable in, each slot, with each vane being biased outwardly to engage the inner surface of the bore in the stator.
  • a fluid inlet and a fluid outlet open into the bore.
  • the arrangement is such that rotation of the rotor within the bore causes the vanes to reciprocate in their respective slots, and drives fluid from the inlet to the outlet.
  • These designs have a limitation in that they are continually driving fluid from the inlet to the outlet, which above certain vehicle speeds is unnecessary, and consequently wastes energy.
  • a rotary vane pump in accordance with the present invention comprises a stator having a cylindrical surface; a rotor which is positioned relative to the stator to define a fluid chamber between the rotor and the stator, the rotor being rotatable about a longitudinal axis and having a number of radially extending slots therein; a vane slidably mounted in each slot and biased towards the fluid chamber and into engagement with the surface of the stator, the vanes reciprocating in their respective slots as the rotor rotates relative to the stator; a first fluid passage providing fluid at a first pressure from a fluid inlet to the fluid chamber; a second fluid passage taking fluid at a second pressure higher than the first pressure from the fluid chamber to a fluid outlet; and a electrically operated valve positioned adjacent the fluid chamber and fluidly connecting the first and second fluid passages on detection of a predetermined condition.
  • the predetermined condition is preferably a predetermined level of vehicle speed, with the first and second fluid passage being fluidly connected when the vehicle speed is above a predetermined level.
  • the rotary vane pump is preferably as described and claimed in our patent application no. (MJD/G-9795), filed the same day as the present application.
  • the rotary vane pump may be of the previously known designs in which the stator surrounds the rotor, but with the addition of the electrically operated valve.
  • the rotary vane pump comprises a housing 1 preferably of cast metallic material; a substantially annular rotor 2 positioned within the housing; a stator 10 formed on a pressure plate 3 and positioned within the rotor; and sixteen vanes 11 mounted in corresponding slots 12 in the rotor.
  • the housing 1 is substantially cylindrical and defines a through bore 17 of stepped diameter.
  • the larger open end 18 of the through bore 17 in the housing 1 is closed by a cover plate 6 which is secured to the housing by screws 19.
  • An O-ring seal 16 forms a substantially fluid-tight seal between the housing 1 and the cover plate 6.
  • a solenoid operated valve 15 is secured in the cover plate 6 and projects into the pressure plate 3.
  • the rotor 2 is integrally formed with a back plate 20 and a drive shaft 21 which extends out of the smaller open end 22 of the through bore 17 in the housing 1.
  • the drive shaft 21 is rotatably mounted in the through bore 17 by a bearing 4.
  • a high pressure seal 5 acts between the through bore 17 and the drive shaft 21 to form a substantially fluid-tight seal at the smaller open end of the through bore.
  • the rotor 2 is rotatably mounted in the through bore 17 by needle bearing 13 or a suitable bushing (such as a Babbitt bushing).
  • Drive means (not shown) rotates the rotor 2 about its longitudinal axis L.
  • the pressure plate 3 is located in a predetermined position relative to the cover plate 6 by locating pins 14 which locate the pressure plate within the housing 1 with the stator 10 positioned inside the rotor 2.
  • a fluid chamber 24 is defined between the rotor 2 and the stator 10.
  • the stator 10 has an outer surface 23 (Figure 2) which is contoured to form a cam surface, and a longitudinal axis which is aligned with the longitudinal axis L of the rotor 2.
  • the slots 12 extend radially through the rotor 2.
  • a circumferentially extending groove 25 is formed in the rotor 2 at the outer radial ends of the slots 12.
  • Each vane 11 is slidably mounted in its respective slot and is capable of reciprocating movement therein.
  • Each vane 11 protrudes out of its respective slot 12 and is biased by a garter spring 7 positioned in the groove 25 into engagement with the outer surface 23 of the stator 10.
  • the positioning of the vanes 11 is symmetrical about the longitudinal axis L of the rotor 2, although the vanes are unequally spaced apart.
  • the cover plate 6 comprises a fluid inlet 26 which is connected to a fluid reservoir (not shown) and a fluid outlet 27.
  • a flow control valve (not shown) may be positioned in the fluid outlet 27.
  • a supercharge fluid passage 28 may interconnect the inlet 26 and outlet 27.
  • annular groove 30 which fluidly connects the inlet 26 to two low pressure depressed areas 31 in the inner surface, and a central depressed area 32 fluidly connected by channels 33 to two high pressure depressed areas 34 and the outlet 27.
  • the central depressed area 32 is also connected with a through bore 46 within which the solenoid operated valve 15 is secured.
  • the outer surface 35 of the pressure plate 3 has two low pressure through bores 36 and two high pressure through bores 37 which align with the corresponding depressed areas 31,34 in the inner surface 29 of the cover plate 6 on assembly of the rotary vane pump.
  • the low pressure through bores 36 and depressed areas 31 define a first fluid passage
  • the high pressure through bores 37 and depressed areas 34 defined a second fluid passage.
  • the outer surface 35 has a centrally positioned stepped through bore 38 which aligns with the central depressed area 32 in the cover plate 6, and which is fluidly connected with the high pressure through bores 37 by a channel 39 in the outer surface 35.
  • the solenoid operated valve 15 extends into the stepped bore 38.
  • the inner surface 40 of the pressure plate 3 has the stator 10 integrally formed thereon, a channel 41 therein for fluidly connecting the low pressure through bores 36, and an annular channel 42 therein adjacent the outer edge 43 for the passage of high pressure fluid between the slots 12 in the rotor 2 adjacent the outer radial end of the slots.
  • the high pressure fluid acts on the vanes 11 (along with the garter spring 7) to bias the vanes into engagement with the outer surface 23 of the stator 10.
  • a bore 47 extends though the stator 10 from adjacent each low pressure through bore 36 to the stepped bore 38.
  • the speed bore 38 also has an opening 48 through the stator 10 which is directed towards the back plate 20 on assembly of the rotary vane pump.
  • the rotor 2 is shown with the back plate 20 and the drive shaft 21, radially extending slots 12, and circumferential groove 25.
  • a pair of bores 44 extend through the back plate 20 and fluidly connect with radially extending channels 45 in the back plate to provide an additional passage for high pressure fluid from the fluid chamber 24 to the outer radial end of each slot 12 to provide bias on the vanes 11 and a hydraulic balance of the rotor 2 relative to the cover plate 6.
  • a longitudinally extending bore 49 passes through the back plate 20 into the drive shaft 21, and a radially extending bore 50 extends from the bore 49 to the outer surface 51 of the drive shaft.
  • the bore 49 aligns with the opening 48 in the stator 10 and is closed at the other end by a ball 52 or something similar, and the bore 50 opens adjacent the bearing 4. This arrangement allows fluid at low pressure to flow to the bearing 4 to lubricate the bearing.
  • the solenoid operated valve 15 comprises a valve member 53 having a frustoconical surface connected to a longitudinally extending stem 54, an electromagnetic coil 55, and a sleeve 56.
  • the stem 54 is reciprocally mounted in the electromagnetic coil 55 which is secured in the through bore 46 in the cover plate 6.
  • the stem 54 is also sealing mounted in the through bore 46 by an O-ring seal 57.
  • the sleeve 56 is mounted in the stepped bore 38 in the pressure plate 3 and extends into the centrally depressed area 32 in the cover plate 6.
  • the sleeve 56 has a through bore 58 comprising a large diameter portion 59, a small diameter portion 60, and a shoulder 61 therebetween.
  • the small diameter portion 60 is directed towards, and opens to, the opening 48 in the stator 10.
  • the valve member 53 is located within the large diameter portion 59 and the shoulder 61 defines a valve seat for the valve member.
  • a diametrically extending bore 62 opens into the small diameter portion 60 and aligns with the bores 47 in the stator 10 on assembly of the rotary vane pump.
  • a diametrically extending channel 63 opens into the large diameter portion 59 and aligns with the channels 39 in the pressure plate 3 and the channels 33 in the cover plate 6 on assembly of the rotary vane pump.
  • a coil spring 64 extends through the small diameter portion 60 and acts on the valve member 53 to bias the valve member to a normally open position.
  • the electromagnetic coil 55 is electrically connected to a control module 65 which monitors signals from a speed sensor 66 mounted in the motor vehicle. On detection of a vehicle speed below a predetermined level, the control module 65 energises the electromagnetic coil 55 to move the valve member 53 into engagement with the shoulder 61 to close the solenoid operated valve 15.
  • the rotor 2 is driven by the drive means (not shown) to rotate about its longitudinal axis L relative to the housing 1 and stator 10.
  • the vanes reciprocate within the slots 12, with the vanes being fully extended inwardly between the low pressure through bores 36 and the high pressure through bores 37 as the vanes move from the low pressure through bores 36 towards the high pressure through bores 37.
  • Fluid at low pressure enters the fluid chamber 24 from the fluid reservoir (not shown) by way of fluid inlet 26 and the low pressure through bores 36.
  • the vanes 11 drive the fluid towards and out through the high pressure through bores 37 to the fluid outlet 27, thereby increasing the pressure in the fluid.
  • the pressurised fluid is used in a power steering system (not shown) of a motor vehicle. Excess fluid flow passes through the supercharge fluid passage 28 to the inlet 26 to help to pressurise the fluid entering the fluid chamber 24.
  • the valve member 53 When the valve member 53 is in its open position, the low pressure through bores 36 and the high pressure through bore 37 in the pressure plate 3 are fluidly connected by way of bores 47 and 62, channels 39 and 63, and through bore 58. In this situation, with the vehicle speed above the predetermined level, the rotary vane pump is effectively disconnected and only a minimal amount of energy is being consumed by the rotary vane pump, thereby saving energy.
  • valve member 53 is moved to its closed position to separate the low and high pressure fluid passages so that the rotary vane pump operates as described above to provide pressurised fluid to the power steering system of the motor vehicle.
  • the slots in the rotor could be equidistantly spaced apart.
  • the stator could have a substantially circular crosssection, with the longitudinal axis of the stator offset from the longitudinal axis of the rotor to provide the required reciprocating movement of the vanes as the rotor rotates.
  • Other forms of electrically operated valve could be used besides a solenoid operated valve. In either case, the arrangement may be that the valve member is biased to a normally closed positioned, and is moved to an open position on detection of a vehicle speed above the predetermined level.
  • stator could have an annular configuration with the rotor positioned inside the stator as is known from previous designs of rotary vane pump.
  • the electrically operated valve would be positioned in or adjacent the stator and adjacent the fluid chamber.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP19950200457 1994-03-19 1995-02-23 Flügelzellenpumpe Expired - Lifetime EP0674105B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9405471A GB2287756B (en) 1994-03-19 1994-03-19 Rotary vane pump
GB9405471 1994-03-19

Publications (2)

Publication Number Publication Date
EP0674105A1 true EP0674105A1 (de) 1995-09-27
EP0674105B1 EP0674105B1 (de) 1998-05-20

Family

ID=10752189

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19950200457 Expired - Lifetime EP0674105B1 (de) 1994-03-19 1995-02-23 Flügelzellenpumpe

Country Status (4)

Country Link
EP (1) EP0674105B1 (de)
DE (1) DE69502529T2 (de)
ES (1) ES2116671T3 (de)
GB (1) GB2287756B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10229809A1 (de) * 2002-07-03 2004-01-15 Zf Lenksysteme Gmbh Flügelzellenpumpe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1091333A (en) * 1964-01-24 1967-11-15 Heinz Teves Improvements in or relating to rotary hydraulic machines
GB1213360A (en) * 1967-12-05 1970-11-25 Rafael Gil Alcolea Improvements in or relating to rotary sliding vane compressors
GB1369680A (en) * 1971-06-30 1974-10-09 Fraser Co Ltd Andrew Rotary fluid pumps and motors
DE2362810A1 (de) * 1973-12-18 1975-06-19 Josef Bertrams Rotorfluegelzellenpumpe mit besonders hohem mech. wirkungsgrad
US5026263A (en) * 1988-12-02 1991-06-25 Jidosha Kiki Co., Ltd. Rotary vane pump with valve to control vane biassing

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60191873A (ja) * 1984-03-13 1985-09-30 Jidosha Kiki Co Ltd 動力舵取装置
DE3788228T2 (de) * 1986-09-25 1994-03-10 Diesel Kiki Co Anlage zur Steuerung eines Verdichters variabler Fördermenge.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1091333A (en) * 1964-01-24 1967-11-15 Heinz Teves Improvements in or relating to rotary hydraulic machines
GB1213360A (en) * 1967-12-05 1970-11-25 Rafael Gil Alcolea Improvements in or relating to rotary sliding vane compressors
GB1369680A (en) * 1971-06-30 1974-10-09 Fraser Co Ltd Andrew Rotary fluid pumps and motors
DE2362810A1 (de) * 1973-12-18 1975-06-19 Josef Bertrams Rotorfluegelzellenpumpe mit besonders hohem mech. wirkungsgrad
US5026263A (en) * 1988-12-02 1991-06-25 Jidosha Kiki Co., Ltd. Rotary vane pump with valve to control vane biassing

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 8, no. 143 (M - 306)<1580> 4 July 1984 (1984-07-04) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10229809A1 (de) * 2002-07-03 2004-01-15 Zf Lenksysteme Gmbh Flügelzellenpumpe

Also Published As

Publication number Publication date
EP0674105B1 (de) 1998-05-20
GB2287756A (en) 1995-09-27
ES2116671T3 (es) 1998-07-16
GB2287756B (en) 1998-04-08
GB9405471D0 (en) 1994-05-04
DE69502529T2 (de) 1998-09-10
DE69502529D1 (de) 1998-06-25

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