EP2642073A2 - Pompe à palettes pendulaires - Google Patents

Pompe à palettes pendulaires Download PDF

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Publication number
EP2642073A2
EP2642073A2 EP13155506.2A EP13155506A EP2642073A2 EP 2642073 A2 EP2642073 A2 EP 2642073A2 EP 13155506 A EP13155506 A EP 13155506A EP 2642073 A2 EP2642073 A2 EP 2642073A2
Authority
EP
European Patent Office
Prior art keywords
groove
pendulum
curvature
radius
inner rotor
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.)
Withdrawn
Application number
EP13155506.2A
Other languages
German (de)
English (en)
Other versions
EP2642073A3 (fr
Inventor
André MAEDER
Eike Stitterich
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.)
Mahle International GmbH
Original Assignee
Mahle International 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 Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2642073A2 publication Critical patent/EP2642073A2/fr
Publication of EP2642073A3 publication Critical patent/EP2642073A3/fr
Withdrawn legal-status Critical Current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
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • 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
    • F04C2/32—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • F04C2/332—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • 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
    • F04C2/348—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 vanes positively engaging, with circumferential play, an outer rotatable member
    • 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
    • F04C2/32—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • F04C2/324—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the inner member and reciprocating with respect to the outer member
    • 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
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor

Definitions

  • the present invention relates to a pendulum slider pump with a rotatably mounted inner rotor, which is connected by pendulum with an outer rotor, according to the preamble of claim 1.
  • the invention also relates to a use of such pendulum slide pump in a motor vehicle, and an inner rotor for such pendulum slide pump.
  • volume-controlled pendulum slide pumps in internal combustion engines has long been state of the art, for example, to be able to easily adapt a flow rate and pressure of a fluid to be conveyed to the needs of the internal combustion engine.
  • a disadvantage of the known pendulum slide pumps is in particular the high load of the inner rotor at particularly sensitive points, namely at a transition from a groove wall to a groove base or in the groove base itself.
  • the pendulum are articulated mounted on the outer rotor and guided radially in the previously described grooves in the inner rotor.
  • the present invention therefore deals with the problem of providing an improved embodiment for a pendulum vane pump of the generic type, which is improved in particular by an improved Design and characterized an increased life and increased resilience.
  • the present invention is based on the general idea of a groove geometry, that is to modify a geometry of the radial guidance of a pendulum in an inner rotor or an outer rotor such that compared to previous groove geometries the load, especially in a transition from a groove bottom in the lateral groove walls / Groove edges, that is in the rounding area, can be significantly reduced.
  • the pendulum slide pump according to the invention has for this purpose a rotating inner rotor, which is connected via said pendulum with an outer rotor.
  • the pendulums are articulated mounted on the outer rotor and guided radially in an associated groove in the inner rotor or vice versa, in which case the grooves would be arranged in the outer rotor.
  • the grooves each have two groove walls or groove flanks, which pass over a respective rounding area into a common groove base.
  • the rounding area has variable groove radii and thus passes into the groove base and the groove walls with no or at least reduced curvature jump.
  • Variable groove radii means that these groove radii are larger in the transition to the groove walls and the groove bottom than in between. That is, the groove wall passes over a large Nutenradius and thus a small curvature in the rounding area. Subsequently, the groove radius decreases towards the center of the rounding area, so that there the curvature increases.
  • the production of the modified Nutengeometrie is manufacturing technology simple, for example, by means of a modified sintering implement feasible, with changes to the feet of the individual pendulum are not required, so that they can be taken over unchanged. Also, a depth of the respective groove can remain unchanged compared to previous groove depths, so that the inventive advantage of the significantly increased wear resistance can be achieved by a simple replacement of the inner rotor / outer rotor.
  • the increased wear resistance are particularly the increase in fatigue strength and thus the life and the increase in the performance of the composite between a drive shaft and the respective inner rotor and thus the transmittable torque.
  • the transition from groove bottom over the rounding area in the associated groove wall is formed without change of direction of curvature.
  • a uniform direction of curvature both in the region of the groove bottom and in the area given the transition to the rounding area or to the groove wall whereby the load can be further reduced and thus the life and wear resistance can be extended.
  • the groove base has an elliptical shape, wherein a first radius of the elliptical groove base corresponds to approximately half of the groove width and a second radius to approximately 3/8 of the first radius. This also makes it possible to achieve significant increases in dynamic safety and durability.
  • An inventive pendulum slide pump 1 has a rotatably mounted inner rotor 2, which is connected via pendulum 3 with an outer rotor 4 in connection.
  • the drawn pendulum 3 is articulated mounted on the outer rotor 4 and guided in the radial direction in an associated groove 5 in the inner rotor 2.
  • the pendulum 3 consists of a pendulum head 6 and a pendulum foot 7, wherein the pendulum head 6 is rotatably mounted on the outer rotor 4 and the pendulum foot 7 is mounted translationally adjustable in the groove 5 on the inner rotor 2.
  • the pendulum head 6 of the pendulum 3 is rotatably mounted on the inner rotor 2 and the pendulum foot 7 can be translationally adjusted in a groove arranged on the outer rotor 4.
  • the inner rotor 2 is produced as a part, in particular in one piece, for example in a sintering process.
  • the in the Fig. 1 shown two colors has no meaning.
  • the inner rotor 2 could also be constructed of several materials in layers.
  • the pendulum slide pump 1 can be used, for example, to supply an internal combustion engine, not shown, with lubricant, for example oil, but alternatively it is also conceivable that it be used for other liquids to be conveyed, such as, for example, refrigerant, coolant or water.
  • the groove 5 has two Nutenrow / Nutenflanken 8, which pass over rounding areas 9 in a common groove bottom 10. In a transition region groove wall 8, rounding area 9 and groove bottom 10, a locally existing curvature is shown as a striped plot. This goes from point A via B and C to point D. In the Fig. 2-5 are different Rotornutengeometrien and the respective curvature shown.
  • the curvature is the derivative of the rolling curve, which results when the groove radii s and the groove bottom 10 as a curve.
  • Derivation is the mathematical derivation of the rolling curve. This derivative corresponds to the curvature of the rolling curve. If the curvature is constant, as is the case for a circle with a fixed radius, the graph shows a constant long line s with envelope g, see Fig. 2b ). In points B and C according to the FIG. 2 the curvature jumps from a negative value to a positive one (or vice versa). Here, a curvature direction change 11 and a curvature jump 12 are present. The length of the stroke s indicates the size of the curve. at Fig.
  • the envelope g at these two points B and C has a discontinuity in the form of a curvature jump 12. That is, the rolling curve is not curvature-continuous over the entire course of A over B and C to D. But in the subareas A to B, B to C and C to D, but not in the points B and C. At these points, Point B and C, the mechanical load of the inner rotor 2 is the largest during continuous operation, so that it can come here most likely to stress-induced fractures of the inner rotor 2. This represents the known state of the inner rotor 2.
  • the local curvature can be measured by mechanical or optical measuring methods on each inner rotor 2 and can also be determined in most design programs. Complex calculations can be used to calculate possible load limits for different rolling curves. The findings gained lead to it Internal rotors 2 with new inventive geometry, which can expect a longer life of the pendulum slide pumps 1.
  • the curvature direction change 11 has a negative effect, but the curvature jump 12, as the envelope g shows significantly smaller .
  • the length of the stroke s 1 is significantly less than in Fig. 2b .
  • the size s and thus the radius and the curvature here vary along the rolling curve, g is the envelope to it. It is noticeable that the region with the reverse curvature is significantly narrower and significantly smaller than in the Fig. 2 ,
  • the rounding area 9 has variable Nutenradien s and these Nutenradien s in transition to the Nutencaren 8 and the Groove base 10 are larger than in between in the rounding region 9, this goes on without or with at least reduced curvature jump 12 in the groove base 10 and the groove walls 8 on.
  • a first radius r 1 of the elliptical groove base 10 corresponds to approximately half of a groove width b (see FIG. Fig. 4 above), whereas a second radius r 2 corresponds to approximately half of the first radius r 1 .
  • the first radius r 1 corresponds to approximately half of the groove width b and the second radius r 2 corresponds approximately to 3/8 of the first radius r 1 . This gives the elliptical shape a much flatter shape.
  • the rounding areas 9 and the groove base 10 are formed curvature-continuous, such as in the embodiment in the Fig. 2 and 3 ,
  • the rounding region 9 has variable groove radii s and is designed such that it merges into the groove base 10 and / or the groove walls 8 without or with at least a reduced curvature jump 12 and that the groove radii s in the transition to the groove walls 8 and the Groove bottom 10 are larger than in between.
  • the groove base 10 also has an elliptical shape, that is also a curvature continuous contour, which in turn no change of direction of curvature 11 in the groove base 10 is present.
  • no curvature jump 12 in the points B and C at the junction of the rounding 9 to the groove base 10 is present.
  • the range of transition of the groove walls 8 to the rounding areas 9, that is, in the points A and D was not optimized with respect to the curvature continuity, but this is also possible there and possibly useful. In practice, not so high loads have occurred in points A and D, so that there is virtually no risk of breakage of the inner rotor 2 there. For these transitions, it is completely sufficient if the groove walls 8 pass so smoothly into the rounding areas 9 that the pendulums 3 of the pendulum slide pump 1 can slide over them almost without friction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP13155506.2A 2012-03-21 2013-02-15 Pompe à palettes pendulaires Withdrawn EP2642073A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012204500A DE102012204500A1 (de) 2012-03-21 2012-03-21 Pendelschieberpumpe

Publications (2)

Publication Number Publication Date
EP2642073A2 true EP2642073A2 (fr) 2013-09-25
EP2642073A3 EP2642073A3 (fr) 2016-06-15

Family

ID=47710047

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13155506.2A Withdrawn EP2642073A3 (fr) 2012-03-21 2013-02-15 Pompe à palettes pendulaires

Country Status (4)

Country Link
US (1) US9217432B2 (fr)
EP (1) EP2642073A3 (fr)
CN (1) CN103321894B (fr)
DE (1) DE102012204500A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018153468A1 (fr) 2017-02-24 2018-08-30 Pierburg Pump Technology Gmbh Pompe à palettes à pendule liquide pour automobile

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010023068B4 (de) * 2010-06-08 2025-11-27 Mahle International Gmbh Flügelzellenpumpe
JP6295923B2 (ja) * 2014-11-12 2018-03-20 アイシン精機株式会社 オイルポンプ
JP2017048681A (ja) * 2015-08-31 2017-03-09 株式会社マーレ フィルターシステムズ ポンプ
DE102017210776A1 (de) * 2017-06-27 2018-12-27 Mahle International Gmbh Pendelschieberzellenpumpe

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19532703C1 (de) 1995-09-05 1996-11-21 Guenther Beez Pendelschiebermaschine
DE10334672B3 (de) * 2003-07-30 2005-01-13 Beez, Günther, Dipl.-Ing. Pendelschiebermaschine

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1941651A (en) * 1931-09-08 1934-01-02 John E Behlmer Fluid compressor
US2064635A (en) * 1936-01-13 1936-12-15 Benjamin B Stern Rotary type pump
FR980766A (fr) * 1943-02-26 1951-05-17 Pompe à alluchons oscillants
CH257830A (de) * 1944-05-23 1948-10-31 Scott Prendergast Charles Fluidummaschine, insbesondere für Kraftübertragungsanlagen und Pumpwerke.
US4125031A (en) * 1977-01-03 1978-11-14 Swain James C Coupler for two eccentrically rotating members
JP3014656B2 (ja) * 1997-03-11 2000-02-28 建治 三村 回転圧縮機
CN101328890B (zh) * 2008-07-22 2010-12-08 温岭市鑫磊空压机有限公司 平动式旋转压缩装置
DE102009006453A1 (de) * 2009-01-28 2010-07-29 Bayerische Motoren Werke Aktiengesellschaft Fluidpumpe
DE102010007255A1 (de) * 2010-02-09 2011-08-11 Bayerische Motoren Werke Aktiengesellschaft, 80809 Fluidpumpe
DE102010023068B4 (de) * 2010-06-08 2025-11-27 Mahle International Gmbh Flügelzellenpumpe

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19532703C1 (de) 1995-09-05 1996-11-21 Guenther Beez Pendelschiebermaschine
DE10334672B3 (de) * 2003-07-30 2005-01-13 Beez, Günther, Dipl.-Ing. Pendelschiebermaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018153468A1 (fr) 2017-02-24 2018-08-30 Pierburg Pump Technology Gmbh Pompe à palettes à pendule liquide pour automobile
US11193484B2 (en) 2017-02-24 2021-12-07 Pierburg Pump Technology Gmbh Automotive liquid pendulum vane pump

Also Published As

Publication number Publication date
CN103321894A (zh) 2013-09-25
DE102012204500A1 (de) 2013-09-26
US20130251580A1 (en) 2013-09-26
US9217432B2 (en) 2015-12-22
EP2642073A3 (fr) 2016-06-15
CN103321894B (zh) 2016-09-21

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