EP0679808B1 - Flügelzellenpumpe - Google Patents

Flügelzellenpumpe Download PDF

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Publication number
EP0679808B1
EP0679808B1 EP95106067A EP95106067A EP0679808B1 EP 0679808 B1 EP0679808 B1 EP 0679808B1 EP 95106067 A EP95106067 A EP 95106067A EP 95106067 A EP95106067 A EP 95106067A EP 0679808 B1 EP0679808 B1 EP 0679808B1
Authority
EP
European Patent Office
Prior art keywords
area
pump
vane
separating
suction
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
EP95106067A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0679808A2 (de
EP0679808A3 (de
Inventor
T. Dipl. Ing. Nied-Menninger
Bernd Dipl. Ing. Denfeld
Randolf Dipl. Ing. Körtge
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.)
LuK Fahrzeug Hydraulik GmbH and Co KG
Original Assignee
LuK Fahrzeug Hydraulik GmbH and Co KG
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 DE19504773A external-priority patent/DE19504773A1/de
Application filed by LuK Fahrzeug Hydraulik GmbH and Co KG filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Publication of EP0679808A2 publication Critical patent/EP0679808A2/de
Publication of EP0679808A3 publication Critical patent/EP0679808A3/de
Application granted granted Critical
Publication of EP0679808B1 publication Critical patent/EP0679808B1/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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface

Definitions

  • the invention relates to a vane pump a rotor that has radially movable blades, the one on the inside contour in a pump housing arranged lifting ring are movable along, wherein the stroke ring has a diametrically symmetrical double stroke contour has and two diametrically opposite Pump room trains.
  • Vane pumps of the type mentioned are known. When the rotor rotates, the blades become by the centrifugal force that occurs and additionally by one under the wings, one pumped Medium outgoing pressure is guided along the ring contour. This leads to the well-known Function of sucking and pumping away any Medium.
  • the known double-stroke vane pumps has the inner contour of the cam ring for each of the two diametrically opposite pump rooms a suction area and a pressure area, each separated by a separation area are. Between the suction areas of each a pump room and the pressure ranges of each another pump room is another separation area educated. The latter separation areas are formed by a so-called small circle, while the separation areas between the suction and pressure areas a pump room by a so-called Great circle.
  • the wings of the Vane pump on the inner contour of the cam ring are movable along, they are dependent a certain speed or acceleration behavior of their stroke in the radial direction.
  • the wings are radial Experience acceleration jumps that are too radial Can cause jumps in the wing movement.
  • this leads to an increased Leakage and on the other hand to increased noise by taking off and then The wings reappear on the ring contour.
  • a vane pump is known from EP 0 151 983, which have a cam ring with diametrically opposite Pump rooms and a rotor with eight Has wings.
  • the pump rooms each have an entry curve area that is in a constant Velocity curve area, an acceleration curve area and a speed deceleration curve area is divided.
  • the entry curve area which in each case the separation areas between the print area of the one pump room and the suction area of the other Pump room connects, the occurrence of a Leakage can be reduced.
  • the selected inner contour of the cam ring a wing pitch of 45 ° is required and thus provided a total of eight blades on the rotor have to be.
  • a vane pump is known from US 33 40 816 which has a rotor with six radially movable Has wings that on the inner contour of a arranged in a pump housing along the stroke ring are movable. Because of the diametrically symmetrical double stroke contour become two diametrical opposite pump rooms formed. The inner contour is in each case in the area of the pump rooms divided into three sections, each a suction and pressure area and a between this lying separation area are formed. Of the Suction, pressure and separation areas are different large. Due to the design of the inner contour and the arrangement of those assigned to the pump chamber Intake and exhaust opening is at one turn of the rotor towards the outlet opening of the pump chamber that is formed between two wings Pump chamber shifted and at the same time reduced in size.
  • the invention has for its object a vane pump of the generic type to create which is simple and made up of a few parts and leakage between the pump rooms is minimized.
  • the vane pump is characterized by the fact that the suction, Pressure and separation area are the same size and that the wings in the separation area in their radial maximum remain extended position. The wings remain when driving through the entire separation area fully extended and remain in this Position. This ensures that the radial Velocity and radial acceleration the wing in the separation area is zero.
  • the suction, pressure and separation areas are preferred each an angular range of 60 °. Which advantages resulting from this configuration the vane pump are considered when considering Current position of the circumference of the rotor distributed wings clearly in one of the wings just the suction area of the pump room completely has passed through.
  • the pump rooms without erratic Change in the radial speed curve of the movement influenced by the inner contour Merge wings and preferably the Inner contour in the separation area between the printing area of the first pump room and the suction area of the second pump chamber and the pressure range of the second pump chamber and the suction area of the first Pump room does not have its own circular area, is advantageously achieved that for the wing independent dynamic radial behavior only for these areas there is no wing no sudden change in their radial speed and because of one about one small angular range of constantly changing stroke one continuous radial speed change exhibit.
  • acceleration is the first derivative which forms speed according to time the occurrence of radial jumps in acceleration avoided in the separation areas. This will prevents the wings from lifting off the inner contour can, so that leakage between the pump rooms is minimized.
  • there is a reduction in noise because by not lifting the wings also not noise-intensive again on the inner contour can open.
  • a vane pump 10 is shown in FIG.
  • the Vane pump 10 has a pump housing 12, in a cam ring 16 is arranged in a recess 14 is. Within the cam ring 16 is one on one Drive shaft 18 attached rotor 20 arranged. Of the Rotor 20 is centered on the recess 14 or the Hubring 16 arranged.
  • the rotor 20 has radially extending Slots 22 in which are radially movable Wing 24 are guided.
  • the rotor 20 has a total six slots 22 with a degree of division 60 ° arranged around the circumference of the rotor 20 are.
  • the cam ring 16 has an inner contour 26, the two diametrically opposite pump chambers 28 'and 28 " trains.
  • Opposite is the separation area 34 between the Pressure range 32 'of the first pump chamber 28' and the Suction area 30 "of the second pump chamber 28" is formed.
  • the inner contour 26 points in the area of the pump rooms 28 each have a separation area 36 between the Suction area 30 and the pressure area 32 of each pump room 28 on.
  • Section 40 is the suction area 30, in section 42 the separation area 36 and in section 44 the printing area 32 educated.
  • the inner contour 26 has in the separation regions 34 no own contour area, especially none Circular area so that the inner contour of the areas the pressure areas 32 seamlessly into the inner contour merges into the areas of the suction areas 30.
  • the Separation area 34 is thus directly at an angle from 0 ° or opposite at 180 ° only by a thickness of the wings 24 with a corresponding Position of the rotor 20 determined.
  • Figure 1 is one running through the angular position 0 ° or 180 ° Radials 38 shown.
  • the point A is with 0 ° and point B with 180 °, the Rotor 20 is movable counterclockwise.
  • the vane pump 10 shown in Figure 1 does the following Function off:
  • the rotor 20 via the drive shaft 18 in rotation offset so that the vanes 24 by centrifugal force and additionally by pressure under the wings in the Slits 22 pressed outwards and so on the inner contour 26 are moved along.
  • the inner contour 26 are the wings 24 in the suction areas 30 and in the printing areas 32 off or retracted.
  • the Wing 24 thus a certain radial stroke, one certain radial speed and a certain radial acceleration ( Figures 2 to 4).
  • the pump chambers fall into this Now together with sections 40, 42 and 44.
  • the separation between the pressure areas 32 and suction areas 30 of the two opposite pump rooms 28 is carried out by at least one wing 24.
  • the inner contour 26 is designed such that the wings 24 in the separation areas 34 do not have their own Range of motion, that is, exclusively on have the separating area 34 designed radial stroke.
  • FIGS 24 The dynamics of the wings are shown in FIGS 24 assuming a constant rotor speed 20 clarifies.
  • the radial is in FIG Stroke of a wing 24 shown over the angle. From the course of the curve it is clear that the radial stroke of the vanes 24 only at 0 ° and 180 °, the positions designated by A and B in Figure 1 correspond, has a minimum.
  • the hub leaves the falling branch in the tree without an abrupt change Area of pressure areas 32 in the ascending branch in the area of the suction areas 30. A pause of the stroke at its minimum value over an angular range of several degrees is not given, so that the stroke only in the angular position of 0 ° or 180 ° has its minimum.
  • the radial speed is one Wing 24 applied over the angle.
  • the course of the curve shows that the wings 24 in the separation area between the pressure areas 32 and the suction areas 30 a constantly changing radial speed have exactly at positions A or B, that is, at 0 ° or 180 °, have the value zero.
  • the wings 24 remain on a certain one Speed level in the separation areas 34 is avoided by the selected inner contour 26.
  • the radial speed goes from a maximum negative value in the area of the pressure areas 32, the that is, the vanes 24 are radially into the rotor 20 inserted, continuously into a maximum positive Value in the area of the suction areas 30, that is, the vanes 24 are radially out of the rotor 20 moved beyond.
  • the radial speed in the separation area 34 as shown in FIG. 4, in this area Avoid jumps in acceleration. Because of the constant stroke in the separation areas 36 has the radial Speed of the wing 24 there the value Assumed zero.
  • FIG 4 is the radial acceleration of the wing 24 shown above the angle.
  • the acceleration has in the separation areas 34 and 36 in essentially approximately constant course, since the acceleration is derived from the speed results after time.
  • In the separation areas 36 has the radial acceleration constant value from zero to.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP95106067A 1994-04-26 1995-04-24 Flügelzellenpumpe Expired - Lifetime EP0679808B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4415214 1994-04-26
DE4415214 1994-04-26
DE19504773A DE19504773A1 (de) 1994-04-26 1995-02-14 Flügelzellenpumpe
DE19504773 1995-02-14

Publications (3)

Publication Number Publication Date
EP0679808A2 EP0679808A2 (de) 1995-11-02
EP0679808A3 EP0679808A3 (de) 1996-07-31
EP0679808B1 true EP0679808B1 (de) 1999-10-13

Family

ID=25936125

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95106067A Expired - Lifetime EP0679808B1 (de) 1994-04-26 1995-04-24 Flügelzellenpumpe

Country Status (3)

Country Link
US (1) US5702242A (ja)
EP (1) EP0679808B1 (ja)
JP (1) JP3865414B2 (ja)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1096570C (zh) * 1997-12-21 2002-12-18 徐浩冠 共轴多滑片波环转子机
CN101338747B (zh) * 2008-08-12 2010-06-02 胡东文 双油路叶片泵/马达
CA2679776A1 (en) * 2008-10-08 2010-04-08 Magna Powertrain Inc. Direct control variable displacement vane pump
RU2517641C2 (ru) 2008-11-07 2014-05-27 ЭсТиТи ТЕКНОЛОДЖИС ИНК., Э ДЖОЙНТ ВЕНЧЕР ОФ МАГНА ПАУЭРТРЕЙН ИНК. ЭНД СХВ ГМБХ Погружной электронасос
US8696326B2 (en) * 2009-05-14 2014-04-15 Magna Powertrain Inc. Integrated electrical auxiliary oil pump

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2330565A (en) * 1939-10-30 1943-09-28 Walter W Eckart Power transmission pump
US2791185A (en) * 1954-07-19 1957-05-07 Gen Motors Corp Hydraulic rotary transmission device
GB863162A (en) * 1956-09-21 1961-03-15 Scaife Company Rotary gas compressor pump
US3340816A (en) * 1965-10-11 1967-09-12 Weatherhead Co Vane pump or motor
FR2199339A5 (ja) * 1972-09-14 1974-04-05 Lucas Industries Ltd
JPS5882088A (ja) * 1981-10-07 1983-05-17 Hitachi Ltd ベ−ン形圧縮機
JPH0674790B2 (ja) * 1983-03-08 1994-09-21 株式会社豊田中央研究所 流体圧ベ−ンポンプ
EP0151983B1 (en) * 1984-02-01 1990-09-26 Toyoda Koki Kabushiki Kaisha Vane pump

Also Published As

Publication number Publication date
US5702242A (en) 1997-12-30
JPH0842463A (ja) 1996-02-13
JP3865414B2 (ja) 2007-01-10
EP0679808A2 (de) 1995-11-02
EP0679808A3 (de) 1996-07-31

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