WO2009019095A1 - Pompe cellulaire à aubes à pression réduite sur les aubes - Google Patents

Pompe cellulaire à aubes à pression réduite sur les aubes Download PDF

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Publication number
WO2009019095A1
WO2009019095A1 PCT/EP2008/058756 EP2008058756W WO2009019095A1 WO 2009019095 A1 WO2009019095 A1 WO 2009019095A1 EP 2008058756 W EP2008058756 W EP 2008058756W WO 2009019095 A1 WO2009019095 A1 WO 2009019095A1
Authority
WO
WIPO (PCT)
Prior art keywords
wing
vane
vane pump
rotor
pump according
Prior art date
Application number
PCT/EP2008/058756
Other languages
German (de)
English (en)
Inventor
René Constantin SCHEERER
Stefan Merz
Gordon Ulrich Mohn
Martin Josef Zug
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
Publication of WO2009019095A1 publication Critical patent/WO2009019095A1/fr

Links

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
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C2/3441—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 one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—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 one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution

Definitions

  • the invention relates to a vane pump with a rotor, are formed in the wing slots for receiving in the radial direction therein movable wings, wherein the vane slots extend in the radial direction to an outer peripheral surface of the rotor.
  • a vane pump with adjustable delivery volume is known.
  • a cam ring is mounted so pivotable that an eccentricity of the cam ring with respect to a rotor is adjustable.
  • the rotor is arranged in the lifting ring and has a plurality of wing slots.
  • the vane slots extend in the radial direction up to an outer circumference of the rotor.
  • wings are arranged radially displaceable, abut the head ends on a trained on the inside of the cam raceway.
  • a control kidney is formed in a housing receiving the rotor and the cam ring.
  • the housing is closed by a lid.
  • the vane slots are introduced in the form of grooves in the rotor, wherein the vane slots in the circumferential direction bounding on both sides
  • Wing slot surfaces are formed parallel to each other. During operation of the pump and an associated force acting on a wing, the wings attach themselves to the wing slot surfaces.
  • the conveyor-side control kidneys is provided in the vane pump closing lid a relief kidney.
  • a hydraulic force is generated on a side face of the wing, but also on the opposite side. A one-sided axially acting hydraulic force on the wing is thus prevented.
  • the vane pump according to the invention has a rotor, in which vane slots are formed for receiving in the radial direction movable therein wings.
  • the vane slots extend in the radial direction to an outer circumferential surface of the rotor.
  • the vane slot circumferentially defining vane slot surfaces of the rotor extend so as to widen the slots toward the outer circumference of the rotor.
  • the course of the wing slot defining wing slot surfaces has the advantage that the
  • the wing slot surfaces are curved and in particular that the curvature of the wing slot surface corresponds to a bending line of a wing.
  • the curvature of the wing slot surface corresponds to the bending line of the wing at maximum pump pressure of the vane pump.
  • Oil pocket is formed.
  • the hydrodynamic relief of the radially displacing in the wing slot wing is improved upon rotation of the rotor.
  • the oil pockets are connected to a pressure medium supply line, via which the pressure medium supplied to the oil pocket is respectively tracked.
  • a hydrostatic force is built up on the wing, which further improves the hydrodynamic relief.
  • There is a leakage of pressure fluid generated from the wing slot which not only the hydrodynamic relief is improved, but also enters a flushing effect. This rinsing effect is particularly advantageous when contaminated pressure medium is conveyed through the vane pump.
  • the formation of an oil pocket connected to a pressure medium feed line is particularly advantageous, If the vane pump is integrated into a pump unit and the pressure medium supply line is supplied with a delivery-side pressure of a main pump.
  • the vane pump integrated into a pump unit is an auxiliary or charge pump of the pump, so that the delivery-side pressure of the vane pump is below the pressure provided by the main pump. This can be ensured by the connection of the oil pockets to the pressure side of the main pump that even at maximum pump pressure of the vane pump leakage from
  • a front and a rear lubricating wedge are formed between the wing and the raceway.
  • the front grease wedge is larger than the rear grease wedge.
  • the head end is preferably rounded.
  • the rounding of the head end corresponds in a cross section through a wing in particular a circular arc section.
  • the center of the circular arc section lies on a line which divides the thickness of the wing in a ratio of 2/3 to 1/3.
  • Such a division of the thickness of the wing 2/3 to 1/3 has the particular advantage that on the one hand, the front lubricating wedge large is enough to ensure a rapid floating of the wing and on the other hand, the point of contact between the wing and the track but far enough away from the rear edge of the wing.
  • the thus formed rear lubricating wedge improves the
  • the vane cell pump has a relief groove opposite this control opening in addition to a delivery-side control opening arranged on one side of the rotor.
  • this relief groove of the delivery-side pressure of the vane pump acts not only on the side of the control port, but also in the opposite direction on the side of the relief groove. Therefore, the forces acting on the wing in the axial direction compensate each other and the wing is not in the axial direction against the
  • FIG. 1 shows a cross section through a pump unit consisting of a main pump and a vane cell pump integrated in a connection plate;
  • Figure 2 is a side view of a rotor of the vane pump according to the invention with widening wing slots. 3 shows a cross section through the rotor of FIG. 2 for clarification of the oil pockets arranged in the vane slot surfaces;
  • Figure 4 is an enlarged view of a wing and a part of a cam ring to illustrate the geometry of the head end of the wing.
  • Fig. 5 is a view of a lid of the vane pump in the axial direction with a discharge opening.
  • a pump unit 1 is shown, which is arranged in a housing consisting of a cup-shaped first housing part 2 and a second housing part.
  • the second housing part is designed as a connection plate 3 and closes the cup-shaped housing part. 2
  • a main pump 4 is arranged in the cup-shaped housing part 2.
  • the main pump 4 is shown in the
  • Embodiment an axial piston machine.
  • a charge pump in the form of a vane pump 5 is formed.
  • the main pump 4 and the vane pump 5 are driven by a common drive shaft 6.
  • the drive shaft 6 penetrates the bottom of the cup-shaped housing part 2.
  • a toothing 7 is formed. The toothing 7 makes it possible to connect the drive shaft 6 with a torque-generating device.
  • the main pump 4 has a cylinder drum 8 in which cylinder bores are arranged in the longitudinal direction.
  • the plurality of cylinder bores is arranged distributed over a circumferential circle in the cylinder drum.
  • a piston is longitudinal slidably arranged in each of these cylinder bores.
  • the pistons 7 protrude out of the cylinder drum 8 at one end and are articulated there, each with a sliding shoe 10.
  • the sliding blocks 10 are supported on a swash plate 11. Depending on the angle of inclination between the
  • Swash plate 11 and the drive shaft 6 perform at a rotation of the drive shaft 6, the piston 9 in the cylinder bores and the cylinder drum 8 from a lifting movement.
  • connection plate 3 an inlet channel 12 and an outlet channel 13 are formed. Via the inlet channel 12 4 pressure medium is sucked by the main pump. During one revolution of the cylinder drum 8, the cylinder bores on the side facing the connection plate 3 are in contact with the inlet channel 12. As a result, pressure medium is sucked into the cylinder bore and displaced into the outlet channel 13 during a pressure stroke by the piston 9 arranged in the cylinder bores.
  • the pump unit 1 shown is a unit of the charge pump, which is formed by the vane pump 5, and the main pump 4.
  • the vane pump 5 is arranged in a recess 14 in the connection plate 3, which thus forms part of a housing of the vane pump 5, and is also driven by the drive shaft 6.
  • the drive shaft 6 protrudes into the recess 14 with a free shaft end 16.
  • the rotor 15 is disposed on the free shaft end 16 and rotatably connected to the free end of the shaft 16.
  • the recess 14 is introduced from the side facing away from the main pump 4 side in the connection plate 3.
  • the recess 14 takes the rotor 15 of the vane pump. 5 and a cam ring 19.
  • the cam ring 19 surrounds the rotor 15 and is arranged eccentrically to this.
  • a pressure chamber between the recess 14 and the cam ring 19 is formed in the illustrated embodiment.
  • This pressure chamber is connected to the inlet channel 12 via a control pressure line 20.
  • In the pressure chamber thus acts a hydraulic force that tries to adjust the cam ring 19 in Fig. 1 down as a restoring force.
  • Fig. 1 In the opposite direction acts in Fig. 1 not recognizable return device on the cam ring 19th
  • a plurality of grooves formed in the radial direction are arranged as vane slots 17.
  • a wing 18 is guided.
  • the wing 18 is displaceable in the radial direction in the
  • Wing slot 17 arranged and acts sealingly with a
  • connection plate 3 The recess 14 of the connection plate 3 is replaced by a
  • For sealing is in a groove of
  • Lid 21 arranged an O-ring.
  • the integration of the vane pump 5 according to the invention into the pump unit 1 of FIG. 1 merely represents a preferred application of the vane pump 5 according to the invention. It should be noted that the following explanations regarding the design of the vane pump 5 according to the invention can also be applied to a separate vane pump. While in the embodiment of FIG. 1 on the one hand by the connection plate 3 and on the other hand by the cover 21, the two adjacent to the rotor 15 components can be formed, therefore, two housing parts of a separate vane pump can form these components.
  • one or more control plates are arranged between the housing parts or the connection plate and the rotor (so-called sandwich construction), in which the control openings for connecting the chambers to a suction line and a delivery line of the vane pump 5 are formed.
  • the rotor 15 of the vane pump is in one
  • the rotor 15 has a total of four vane slots 17.1 to 17.4.
  • the vane slots 17.1 to 17.4 extend in the axial direction from one side surface of the rotor 15 to the opposite side surface of the rotor 15, so that in the axial direction a wing 18.1 or 18.2 arranged in the vane slots 17.1 to 17.4 can be displaced therein.
  • the vane slots 17 are open to an outer peripheral surface 21 of the rotor 15 and the wings 18.1 and 18.2 can perform therein a movement in the radial direction. Due to this radial movement, a head end of the wings 18 is in contact with a raceway of the cam ring 19, as will be explained below with reference to FIG. 4.
  • the vane slots 17 extend from a first diameter di defining the minimum spacing of the vane slots 17 from the axis of rotation of the rotor 15 to an outer peripheral surface 21 of the rotor 15. Towards the outer peripheral surface 21 of the rotor 15, the vane widens Wing slot 17 each on. This will be clarified with reference to the third wing slot 17.3.
  • the direction of rotation of the rotor 15 at a winningdung of pressure medium is by means of an arrow
  • the vane slot 17.3 is bounded circumferentially by a rear vane slot surface 23 and a front vane slot surface 24 in the circumferential direction.
  • both the rear wing slot surface 23 and the front are
  • Wing slot surface 24 partially curved.
  • the illustrated embodiment shows a subdivision of the vane slot 17.3 in a first area 17 'and a second area 17' '.
  • the rear wing slot area extend in the first area 17 'oriented towards the rotation axis
  • the width of the vane slot 17.3 corresponds approximately to a thickness t of the wing 18 arranged therein.
  • the wing slot 17.3 widens. This is achieved in the illustrated embodiment by a curved design of both the rear wing slot surface 23 and the front wing slot surface 24.
  • the curvature is symmetrical to a centerline of the wing slot 17.3.
  • the symmetrical curvature of the front and rear wing slot surfaces 23 and 24 has the consequence that an orientation during assembly of the rotor 15 need not be considered.
  • a symmetrical design of the vane slots 17 the change of direction of force during rotation of the rotor 15 is taken into account.
  • the curvature of the rear wing slot surface 23 and the front wing slot surface 24 corresponds to a bending line of the wing slot 17.3 arranged in the wing 18.
  • the arranged in the wing slot 17.3 wing under load, as it arises during operation of the vane pump 5 by the delivery-side pressure, to the wing slot surface 23 or 24 in the region of the second portion 17 '' create.
  • An increased load on the wing slot surfaces 23, 24 in the region near the outer periphery 21 is thus prevented.
  • Wing slot made 17.3. However, it is apparent from Fig. 2 that all vane slots 17.1, 17.2 and 17.4 of the rotor are formed in the same way.
  • the proportions of the first portion 17 'and the second portion 17' 'on the total extension of the vane slot 17 in the radial direction depends on the maximum ingestible position of the wing 18 arranged in the vane slot 18 due to the eccentricity of the cam ring 19 and in the cam ring 19 trained career.
  • oil pockets 25 and 26 are also introduced.
  • the reference numerals are given only in the first vane slot 17.1 in FIG. 2, in order not to impair the clarity of the representation. It can be seen that the oil pockets 25 and 26 are arranged opposite to each other.
  • the oil pockets 25 and 26 are equipped with a pressure medium connected to the inflow line, which is formed in the rotor 15.
  • a hydraulic force is generated on the wing 18, which minimizes the friction between the blade 18 and the rotor 15.
  • the efficiency of the vane pump 5 is thus improved.
  • the effective in the direction of rotation of the rotor 15 surface of the rear oil bag 25 may be greater than that of the front oil bag 26.
  • the pressures acting in the oil pockets pressures can be set differently. This can be done either by supplying different pressures to the oil pockets 25, 26 or dynamically during operation of the vane pump 5.
  • the vane slot 17 is designed so that the vane 18 upon application to, for example, the rear vane slot surface 23, in which the rear Oil bag 25 is formed on the side of the front oil bag 26 increases the leakage gap. This reduces the force acting on the wing 18 on the side of the front oil pocket 26. The result is a resulting hydraulic force that hydrostatically relieves the wing 18.
  • the surface area of the vane slot surfaces 23 and 24 is reduced by the oil pockets 25 and 26 introduced as a groove in the vane slot surfaces 23 and 24. This in turn reduces the viscous friction between the vane 18 and vane slot 17.
  • Fig. 3 shows a section along the line III-III of Fig. 2. It can be seen that the grooves of the
  • Oil pockets 25 and 26 is made substantially rectangular. Alternative geometries are also possible. Furthermore, in the Fig. 3 are Ausmünditch 27 and 28 of the pressure fluid supply line, not shown.
  • the pressure medium supply line is preferably with the
  • Dirt particles between the wing 18 and wing slot surface 23 and 24 is reduced. Dirt particles that are present in the oil are rinsed out and can then be filtered out via a filter that may be present.
  • FIG. 4 shows an enlarged view of a cam ring 19 and a wing 18, the head end 30 rests against the raceway 29 of the cam ring 19.
  • the head end 30 touches the track 29 in a touch point B.
  • the contact point B is determined by the contour of the wing 18 on
  • Head 30 determined as it can be seen in a section through the wing 18.
  • the head end 30 is formed in section as a circular arc section.
  • This circular arc section has a radius r.
  • the center of the circular arc portion is located on a line 33 that the thickness t of the blade 18 in relation to a first portion of a second fraction ti t 2 divides.
  • the ratio ti / t 2 is preferably 2/1.
  • Due to the curved course of the head end 30 of the wing 18, a first lubricating wedge 31 is formed on a front side of the wing 18 with respect to the direction of rotation 22, and a second lubricating wedge 32 is formed on a rear side of the wing 18. As can be seen clearly in FIG.
  • the front lubricating wedge 31 is larger than the rear lubricating wedge 32.
  • the lubricating wedge 31, 32 is in each case the region formed between the end face at the top end of the wing 18 and the raceway 29.
  • larger lubricating wedge 31 a floating of the wing 18 is promoted in a rotation of the rotor 15 and thus a movement of the blade 18 along the track 29.
  • This improved floating on an oil film occurs especially at the start of the vane pump 5 but also at low speeds and at low-viscosity pressure means for improved lubrication between the head end 30 and the raceway 29 in the region of the contact point B, whereby the mechanical wear of the vane pump 5 is reduced.
  • a relief groove 34 is opposite to a delivery-side control kidney of the vane pump 5.
  • This hydraulic force is compensated by the relief groove 34 arranged opposite and preferably provided with the same geometry as the control opening.
  • the relief groove 34 communicates with the delivery chambers of the vane pump 5, so that the delivery-side pressure also prevails in it.
  • the relief groove 34 is also not connected to the hydraulic circuit and has only the purpose to compensate for the force generated by the delivery-side control opening on the first side surface of the wing 18 force on the second side surface of the wing 18.
  • the relief groove 34 may be formed as a second control kidney, which is connected to the delivery side of the vane pump 5. Due to the thus enlarged flow cross-section of the dynamic pressure is reduced at the output side of the vane pump 5.
  • the invention is not limited to the illustrated embodiment. Rather, individual features of the embodiment to reduce wear in an advantageous manner can be combined.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne une pompe cellulaire à aubes qui présente un rotor (15) dans lequel des fentes (17) pour aubes sont formées pour y recevoir des aubes aptes à coulisser dans la direction radiale. Les fentes (17) pour aubes s'étendent dans la direction radiale jusqu'à une surface périphérique extérieure du rotor (15). Les surfaces (23, 24) du rotor qui délimitent la fente (17) pour aubes dans sa direction périphérique s'étendent de telle sorte que la fente s'évase en direction de la surface périphérique extérieure du rotor (15).
PCT/EP2008/058756 2007-08-09 2008-07-07 Pompe cellulaire à aubes à pression réduite sur les aubes WO2009019095A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710037666 DE102007037666A1 (de) 2007-08-09 2007-08-09 Flügelzellenpumpe mit verringerter Flächenpressung der Flügel
DE102007037666.0 2007-08-09

Publications (1)

Publication Number Publication Date
WO2009019095A1 true WO2009019095A1 (fr) 2009-02-12

Family

ID=39816599

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/058756 WO2009019095A1 (fr) 2007-08-09 2008-07-07 Pompe cellulaire à aubes à pression réduite sur les aubes

Country Status (2)

Country Link
DE (1) DE102007037666A1 (fr)
WO (1) WO2009019095A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113027751A (zh) * 2021-03-25 2021-06-25 宁波圣龙智能汽车系统有限公司 一种单作用无困油叶片泵

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018513296A (ja) * 2015-03-30 2018-05-24 ハイコア テクノロジーズ インク．Ｈｉｃｏｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ，Ｉｎｃ． 液体噴射冷却機能を備えた圧縮機

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4274816A (en) * 1978-08-31 1981-06-23 Diesel Kiki Company, Ltd. Rotary vane compressor with chamfered vane slots
BE895811A (fr) * 1983-02-03 1983-08-03 Flamme Jean M Dispositif ameliorant le fonctionnement des machines a palettes
DE3333647A1 (de) * 1982-09-21 1984-05-24 Glyco-Antriebstechnik Gmbh, 6200 Wiesbaden Regelbare schmiermittelpumpe
US4599058A (en) * 1984-08-31 1986-07-08 Rineer Hydraulics, Inc. Vane slots for a fluid power converter
DE4332540A1 (de) * 1993-09-24 1995-03-30 Bosch Gmbh Robert Flügelzellenpumpe
DE10156254A1 (de) * 2000-11-11 2002-07-11 Luk Fahrzeug Hydraulik Flügelzellenmaschine
US20050019175A1 (en) * 2003-07-25 2005-01-27 Unisia Jkc Steering Systems Co., Ltd. Variable displacement pump

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4274816A (en) * 1978-08-31 1981-06-23 Diesel Kiki Company, Ltd. Rotary vane compressor with chamfered vane slots
DE3333647A1 (de) * 1982-09-21 1984-05-24 Glyco-Antriebstechnik Gmbh, 6200 Wiesbaden Regelbare schmiermittelpumpe
BE895811A (fr) * 1983-02-03 1983-08-03 Flamme Jean M Dispositif ameliorant le fonctionnement des machines a palettes
US4599058A (en) * 1984-08-31 1986-07-08 Rineer Hydraulics, Inc. Vane slots for a fluid power converter
DE4332540A1 (de) * 1993-09-24 1995-03-30 Bosch Gmbh Robert Flügelzellenpumpe
DE10156254A1 (de) * 2000-11-11 2002-07-11 Luk Fahrzeug Hydraulik Flügelzellenmaschine
US20050019175A1 (en) * 2003-07-25 2005-01-27 Unisia Jkc Steering Systems Co., Ltd. Variable displacement pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113027751A (zh) * 2021-03-25 2021-06-25 宁波圣龙智能汽车系统有限公司 一种单作用无困油叶片泵

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