EP2938881B1 - Pompe à palettes à déplacement variable et procédé de régulation du déplacement de cette dernière - Google Patents

Pompe à palettes à déplacement variable et procédé de régulation du déplacement de cette dernière Download PDF

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Publication number
EP2938881B1
EP2938881B1 EP13824386.0A EP13824386A EP2938881B1 EP 2938881 B1 EP2938881 B1 EP 2938881B1 EP 13824386 A EP13824386 A EP 13824386A EP 2938881 B1 EP2938881 B1 EP 2938881B1
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EP
European Patent Office
Prior art keywords
pump
rolling elements
regulation
regulation ring
displacement
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.)
Not-in-force
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EP13824386.0A
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German (de)
English (en)
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EP2938881A1 (fr
Inventor
Matteo Calderoni
Leonardo Cadeddu
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VHIT SpA
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VHIT SpA
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Publication of EP2938881A1 publication Critical patent/EP2938881A1/fr
Application granted granted Critical
Publication of EP2938881B1 publication Critical patent/EP2938881B1/fr
Not-in-force legal-status Critical Current
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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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F04C14/223—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 using a movable cam
    • 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
    • F04C15/0088—Lubrication
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings

Definitions

  • the present invention relates to variable displacement rotary pumps, and more particularly it concerns a pump of a kind in which displacement regulation is obtained thanks to the variation of the relative eccentricity between a regulation ring and the pump rotor, obtained by varying the relative position of the ring and the rotor depending on the pump operating conditions.
  • the invention also concerns a method of regulating the displacement of such a pump.
  • the present invention is applied in a pump for the lubrication oil of a motor vehicle engine.
  • the regulation movement is a rotation
  • the portion of the region of engagement between the surfaces is configured as a sector of a rolling bearing of which said surfaces form sectors of the inner race and the outer race, respectively, and the rolling elements are arranged within a seat formed in the external surface of the regulation ring.
  • the rolling elements are rollers or needles mounted in a supporting and guiding cage arranged to move in said seat against the action of an opposing resilient member, which is arranged between one end of the cage and one end of the seat and is preloaded so as to keep the cage in contact with the opposite end of the seat in a maximum displacement or rest condition of the pump.
  • the invention also provides a method of regulating the displacement of a pump of the above kind, comprising the steps of:
  • a pump 1 of the above kind comprises a body 10 having a suitably shaped cavity 40 in which stator 11 is mounted so as to be freely rotatable along an arc of circumference, in the illustrated example in clockwise direction, as indicated by arrow A.
  • Reference character B denotes the axis of rotation of stator 11.
  • Stator 11 has a chamber 12 where vane rotor 13 is housed. The rotor is keyed on a shaft 14 arranged off-axis relative to centre C of chamber 12. Also rotor 13 is rotatable in clockwise direction.
  • Reference numerals 41 and 42 denote the ends of the suction and delivery ducts, when rotor 13 rotates in clockwise direction.
  • stator 11 has a pair of radial appendages 17, 18, which project into respective chambers 15, 16 formed by recesses of cavity 40, and which slide in fluid-tight manner on the bases of chambers 15, 16.
  • One of the chambers, for instance chamber 15, is permanently connected to the delivery side of the pump or to the units utilising the pumped fluid (in particular, in the preferred application, to a point of the engine lubrication circuit located downstream the oil filter), through a first regulation duct, not shown in these Figures.
  • the other chamber can in turn be put in communication with the delivery side or with the units utilising the pumped fluid through a valve operated by the electronic control unit of the vehicle and a second regulation duct (not shown). In this manner, appendage 17 is, or both appendages 17, 18 are, exposed to the pressure conditions of the pumped fluid.
  • An end wall of one of the chambers, e.g. chamber 15, may be shaped so as to form an abutment 19 for appendage 17 in the maximum displacement condition.
  • Chamber 16 houses a member 20 opposing the rotation of stator 11. That member, in the example illustrated, comprises two opposite mushroom-shaped elements 21, 22, connected for instance in telescopic manner and biased in opposite directions by a spring 23 arranged between heads 21A, 21B of both elements.
  • Spring 23 is preloaded so as to oppose the rotation of stator 11, and hence to keep it in the position shown in Fig. 1 , as long as the pressure applied to appendage 17 (or the overall pressure applied to appendages 17, 18) is lower than a predetermined threshold, and to subsequently keep the pump displacement at the value corresponding to the pressure threshold.
  • Such a condition is attained when an equilibrium is established between the torques generated by the pressure acting on appendages 17, 18 and the antagonist torque generated by spring 23.
  • Heads 21A, 21B for instance substantially shaped as half cylinders, engage recesses 22A, 22B of complementary shape formed in the opposite surface of appendage 18 with respect to the surface acted upon by the regulating pressure and in a wall of chamber 16, respectively.
  • a pair of articulated joints is formed allowing keeping the ends of spring 23 mutually parallel during the rotation of stator 11, thereby ensuring a good lateral stability of the spring itself.
  • the circumferential extension and the radial size of chambers 15, 16 will be determined depending on the operation characteristics required of the pump.
  • a rotation of stator 11 of the order of about 20° is typical for the preferred application and has been shown in the drawings.
  • the radial size it may be constant over the whole circumferential extension, so that appendages 17, 18 have a constant thrust area and hence generate a constant torque, proportional to the actuation pressure, over the whole arc of rotation.
  • the radial size of one chamber or both chambers may change along the circumferential extension, and appendages 17, 18 have a variable thrust area, so as to generate a variable torque over the arc of rotation of stator 11.
  • Such a solution allows taking into account the fact that the resistant torques encountered during displacement regulation may be variable, for instance because the resistance opposed by opposing spring 20 and/or the rotational frictions vary.
  • Figs. 1 and 2 also show the different forces acting on the components of pump 1 during operation and the reactions caused by such forces. It is to be appreciated that Figs. 1 and 2 only are intended to give a representation of the zones where the different forces act and of the directions of the forces, whereas their magnitudes are not considered. More particularly:
  • Figs. 3 and 4 show the vectors representing forces F P1 - F C mentioned above and their partial and overall resultants in the extreme operating conditions shown in Figs. 1 and 2 .
  • the origin of the axes coincides with centre of rotation B of stator 11.
  • resultants SV1 and SV2, respectively, of the above forces have such orientations that they act in correspondence of a zone S of the mutually engaging surfaces in stator 11 and cavity 40.
  • the fluid under pressure present in chamber 12 creates a hydraulic support bearing.
  • the reaction provided by such a bearing is force R V mentioned above, which has the same magnitude as and opposite direction to the above resultants.
  • a plurality of rolling elements 25, in the illustrated example rollers or needles are arranged between external surface 11A of stator 11 and internal surface 40A of cavity 40, over a portion including zone S where the hydraulic support bearing is created and where resultants SV1, SV2 of the various forces act.
  • rollers 25 are fitted, for instance snap fitted, in respective seats 27 in a supporting cage 26, preferably made of plastic material, which in conventional manner acts as a guide and a spacer for rollers 25.
  • Cage 26 with rollers 25 is housed in a recess of external surface 11A of stator 11, which recess axially extends over the whole axial depth of stator 11 and chamber 40.
  • Recess 28, cage 26 and rollers 25 have such a radial size that the contact between surfaces 11A and 40A is ensured by rollers 25.
  • Typical diameters for the rollers, in the preferred application, are of the order of a few millimetres, for instance 2 - 4 mm.
  • rollers 25 have an axial size (length) slightly shorter than that of cage 26. This gives a labyrinth configuration to the assembly of cage 26 and rollers 25, which configuration allows maintaining the hydraulic support bearing.
  • Cage 26 has an angular extension smaller than the angular extension of recess 28, so that it can move within the recess during the rotation performed by stator 11 for the displacement regulation, and the angular extension of the displacement of cage 26 is smaller than the angular extension of the rotation performed by stator 11 for passing from the maximum displacement position to the minimum displacement position.
  • Recess 28 is defined by two steps or abutments 29A, 29B.
  • One end of cage 26 abuts against one of such abutments, for instance abutment 29A, in the rest condition (maximum displacement) of the pump, shown in Fig. 5 .
  • a resilient member 30 opposing the cage movement e.g. a suitably preloaded leaf spring, is instead arranged between cage 26 and the other abutment 29B and it keeps cage 26 in contact with abutment 29A in the maximum displacement condition.
  • Fig. 5 and 6 clearly show the behaviour of cage 26 with rollers 25 during displacement regulation.
  • three reference points belonging to body 10, stator 11 and cage 26, respectively, have been shown by segments X, Y and Z.
  • the three points are chosen so that their positions coincide in the maximum displacement condition ( Fig. 5 ).
  • point X At the end of the rotation bringing stator 11 to the minimum displacement position ( Fig. 6 ), point X of course has remained stationary, whereas point Z has displaced in clockwise direction and has described an arc that, in the example illustrated, is of about 20°.
  • point Y has performed a rotation in clockwise direction, yet over an arc shorter than that described by point Z. Due to the shorter rotation of cage 26 with respect to stator 11, cage 26 is no longer in contact with abutment 29A at the end of the rotation and spring 30 is more compressed.
  • the invention can be applied also to pumps where the rotation of the stator is achieved in different manner (for instance, through a gear engaging a toothed sector of the external surface of the stator, like in US 5,863,189 ) or to pumps where the regulation movement is different from the rotation of the stator disclosed here ("pendulum" pumps, pumps with oscillating stator, pumps with a translation of the stator ring, and so on).
  • cage 26 will be a linear cage.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Rotary Pumps (AREA)

Claims (10)

  1. Pompe rotative à palettes à déplacement variable pour des fluides, comprenant :
    - un rotor (13) agencé pour tourner de manière excentrique à l'intérieur d'une couronne de régulation (11) avec une excentricité relative qui varie en fonction des conditions de fonctionnement de la pompe (1) ;
    - des moyens (17, 18) pour déplacer la couronne de régulation (11) dans une chambre (40) formée dans un corps de pompe (10) afin de faire varier ladite excentricité relative, et donc le déplacement de la pompe, lorsque lesdites conditions de fonctionnement varient ; et
    - une pluralité d'éléments roulants (25) intercalés entre une surface externe (11A) de la couronne de régulation (11) et une surface interne (40A) de la chambre (40) ;
    caractérisée en ce que :
    - les éléments roulants (25) sont montés dans une cage de support (26) et sont apportés uniquement sur une portion d'une région d'engagement entre la surface externe (11A) de la couronne de régulation (11) et la surface interne (40A) de la chambre (40), ladite portion comportant une zone (S) où agit une résultante (SV1, SV2) de forces mécaniques et fluidiques générées dans la pompe pendant la régulation ; et
    - les éléments roulants (25) et ladite cage de support (26) sont agencés, dans ladite portion de la région d'engagement entre lesdites surfaces (11A, 40A), de manière à bouger comme un corps d'un seul tenant le long desdites surfaces (11A, 40A) pendant le mouvement de la couronne de régulation (11), le mouvement des éléments roulants (25) et de la cage de support (26) ayant une amplitude plus petite qu'un mouvement réalisé par la couronne de régulation (11) afin de faire passer la pompe d'un déplacement maximal à un déplacement minimal.
  2. Pompe selon la revendication 1, dans laquelle le mouvement de régulation est une rotation de la couronne de régulation (11) et dans laquelle :
    - dans ladite portion de la région d'engagement, la surface externe (11A) de la couronne de régulation (11) et la surface interne (40A) de la chambre (40) forment, conjointement avec les éléments roulants (25), un secteur d'un roulement dont lesdites surfaces forment des secteurs d'un chemin de roulement intérieur et d'un chemin de roulement extérieur, respectivement ; et
    - les éléments roulants (25) sont agencés à l'intérieur d'un logement (28) formé dans la surface (11A) de la couronne de régulation (11) et ayant un prolongement plus grand que la cage de support (26) dans laquelle les éléments roulants (25) sont montés.
  3. Pompe selon la revendication 1 ou 2, dans laquelle la cage de support (26) est agencée pour bouger dans ledit logement, déplaçant ainsi les éléments roulants (25), contre l'action d'un organe résilient d'opposition (30), qui est agencé entre une extrémité de la cage (26) et une extrémité (29B) du logement (28) et est capable de conserver ou d'amener à nouveau la cage (26) en contact avec une extrémité opposée (29A) du logement (28) dans la condition de déplacement maximal de la pompe.
  4. Pompe selon l'une quelconque des revendications 1 à 3, dans laquelle les éléments roulants (25) sont montés dans la cage de support (26) de façon à lui donner une configuration en forme de labyrinthe agencée pour maintenir un palier support fluidique généré dans ladite zone (S) en réaction à l'action de la résultante (SV1, SV2) desdites forces.
  5. Pompe selon la revendication 4, dans laquelle les éléments roulants (25) sont des galets ou des aiguilles, et dans laquelle la cage de support (26) a une profondeur axiale correspondant sensiblement à une profondeur axiale de la couronne de régulation (11) et les galets ou aiguilles (25) ont une longueur plus courte que la profondeur axiale de la cage (26).
  6. Pompe selon l'une quelconque des revendications 1 à 5, dans laquelle la rotation de la couronne de régulation (11) est commandée directement par la pression du fluide pompé.
  7. Pompe selon l'une quelconque des revendications précédentes, dans laquelle la pompe est une pompe pour le circuit de lubrification d'un moteur de véhicule motorisé.
  8. Procédé de régulation du déplacement d'une pompe rotative à déplacement variable pour fluides, d'une sorte comprenant un rotor (13) agencé pour tourner de manière excentrique au sein d'une couronne de régulation (11) avec une excentricité relative qui est variable en fonction des conditions de fonctionnement de la pompe (1), le procédé comprenant les étapes consistant à :
    - fournir, entre une surface externe (11A) de la couronne de régulation (11) et une surface interne (40A) d'une chambre (40) logeant la couronne (11), une pluralité d'éléments roulants (25) montés dans une position relative fixe ; et
    - amener la couronne de régulation (11) à bouger dans la chambre (40) afin de faire varier ladite excentricité relative, et donc le déplacement de la pompe, lorsque lesdites conditions de fonctionnement varient ;
    et étant caractérisé en ce que l'étape consistant à fournir des éléments roulants (25) dans la chambre (40) comprend les étapes consistant à :
    - fournir les éléments roulants (25) montés dans une cage de support (26) uniquement sur une portion d'une région d'engagement entre la surface externe (11A) de la couronne de régulation (11) et la surface interne (40A) de la chambre (40), ladite portion incluant une zone (S) où agit une résultante (SV1, SV2) de forces mécaniques et fluidiques générées dans la pompe pendant la régulation ; et
    - pendant la régulation, amener les éléments roulants (25) et la cage de support (26) à bouger comme un corps d'un seul tenant dans ladite portion de la région d'engagement entre lesdites surfaces (11A, 40A), le mouvement des éléments roulants (25) et de la cage de support (26) ayant une amplitude plus petite qu'un mouvement de la couronne de régulation (11) amenant la pompe à passer d'un déplacement maximal à un déplacement minimal.
  9. Procédé selon la revendication 8, dans lequel le mouvement de régulation est une rotation de la couronne de régulation (11) et l'étape consistant à fournir les éléments roulants (25) et la cage de support (26) uniquement sur une portion de la région d'engagement entre lesdites surfaces (11A, 40A) comprend l'étape consistant à configurer les éléments roulants (25) et la cage de support (26), la surface externe (11A) de la couronne de régulation (11) et la surface interne (40A) de la chambre (40) comme un secteur d'un roulement, dont lesdites surfaces forment des secteurs circulaires d'un chemin de roulement intérieur et d'un chemin de roulement extérieur, respectivement.
  10. Procédé selon la revendication 8 ou 9, dans lequel l'étape consistant à amener les éléments roulants (25) et la cage de support (26) à bouger comme un corps d'un seul tenant comprend le mouvement des éléments de roulement (25) et de la cage de support (26) dans un logement (28) formé dans la surface (11A) de la couronne de régulation (11) et ayant un prolongement plus grand qu'un prolongement global desdits éléments roulants (25) et de ladite cage de support (26).
EP13824386.0A 2012-12-27 2013-12-13 Pompe à palettes à déplacement variable et procédé de régulation du déplacement de cette dernière Not-in-force EP2938881B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT001149A ITTO20121149A1 (it) 2012-12-27 2012-12-27 Pompa a palette a cilindrata regolabile e metodo per la regolazione della cilindrata di tale pompa.
PCT/IB2013/060918 WO2014102652A1 (fr) 2012-12-27 2013-12-13 Pompe à palettes à déplacement variable et procédé de régulation du déplacement de cette dernière

Publications (2)

Publication Number Publication Date
EP2938881A1 EP2938881A1 (fr) 2015-11-04
EP2938881B1 true EP2938881B1 (fr) 2017-03-08

Family

ID=47749969

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13824386.0A Not-in-force EP2938881B1 (fr) 2012-12-27 2013-12-13 Pompe à palettes à déplacement variable et procédé de régulation du déplacement de cette dernière

Country Status (5)

Country Link
US (1) US20150322944A1 (fr)
EP (1) EP2938881B1 (fr)
CN (1) CN104903582A (fr)
IT (1) ITTO20121149A1 (fr)
WO (1) WO2014102652A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762615A (zh) * 2017-02-16 2017-05-31 陕西法士特齿轮有限责任公司 一种单作用式变量叶片泵
CN106969249A (zh) * 2017-04-26 2017-07-21 奇瑞汽车股份有限公司 一种叶片式机油泵
IT201800003344A1 (it) * 2018-03-07 2019-09-07 O M P Officine Mazzocco Pagnoni S R L Pompa rotativa a palette a cilindrata variabile
CN114294354A (zh) * 2021-12-30 2022-04-08 綦江齿轮传动有限公司 一种缓速器油量调节装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1988213A (en) * 1931-02-12 1935-01-15 Racine Tool & Machine Company Multiple rotary pump
US2348428A (en) * 1939-12-22 1944-05-09 Hydraulic Dev Corp Inc Variable delivery vane pump
DE3542776A1 (de) * 1985-12-04 1987-07-23 Kurt G Dipl Ing Fickelscher Roll-ring-maschine zum verdichten und foerdern von fluiden
US5863189A (en) 1995-07-10 1999-01-26 Coltec Industries Inc Variable displacement vane pump adjustable by low actuation loads
CN100465444C (zh) * 2004-05-07 2009-03-04 特斯玛国际公司 用管线压力直接调节排量的叶轮泵
WO2007128106A1 (fr) * 2006-05-05 2007-11-15 Magna Powertrain Inc. Pompe à palettes à cylindrée variable en continu et système correspondant
EP2150702A1 (fr) * 2007-04-10 2010-02-10 BorgWarner Inc. Pompe à double aube à déplacement variable

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
US20150322944A1 (en) 2015-11-12
ITTO20121149A1 (it) 2014-06-28
WO2014102652A1 (fr) 2014-07-03
EP2938881A1 (fr) 2015-11-04
CN104903582A (zh) 2015-09-09

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