EP2795130B1 - Pompe volumétrique rotative et méthode de régulation de son débit volumétrique - Google Patents

Pompe volumétrique rotative et méthode de régulation de son débit volumétrique Download PDF

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Publication number
EP2795130B1
EP2795130B1 EP12815823.5A EP12815823A EP2795130B1 EP 2795130 B1 EP2795130 B1 EP 2795130B1 EP 12815823 A EP12815823 A EP 12815823A EP 2795130 B1 EP2795130 B1 EP 2795130B1
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EP
European Patent Office
Prior art keywords
pump
stator ring
chamber
ring
displacement
Prior art date
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Not-in-force
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EP12815823.5A
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German (de)
English (en)
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EP2795130A1 (fr
Inventor
Matteo Cortesi
Luca Stagnoli
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VHIT SpA
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VHIT SpA
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/30Rotary-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
    • F04C2/32Rotary-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
    • F04C2/321Rotary-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 inner member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22Control 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
    • F04C14/223Control 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001Pumps for particular liquids
    • F04C13/002Pumps for particular liquids for homogeneous viscous liquids
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008Prime movers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088Lubrication
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/30Rotary-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
    • F04C2/34Rotary-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
    • F04C2/344Rotary-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
    • F04C2/3441Rotary-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
    • F04C2/3442Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00Geometry
    • F04C2250/30Geometry of the stator
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00Control; Monitoring or safety arrangements
    • F04C2270/18Pressure

Definitions

  • the present invention relates to variable displacement pumps, and more particularly it concerns a rotary positive displacement pump in which the displacement variation is obtained by means of the translation of a stator ring inside which the pump rotor eccentrically rotates.
  • the present invention is employed in a pump for the lubrication oil of a motor vehicle engine.
  • the pump capacity in pumps for making lubricating oil under pressure circulate in motor vehicle engines, the pump capacity, and hence the oil delivery rate, depends on the rotation speed of the engine.
  • the pumps are designed so as to provide a sufficient delivery rate at low speeds, in order to ensure lubrication also under such conditions. If the pump has fixed geometry, at high rotation speed the delivery rate exceeds the necessary rate, giving rise to a high power absorption, and consequently to higher fuel consumption, and to a greater stress of the components due to the high pressures generated in the circuit.
  • WO2005068838A1 discloses a positive displacement pump with a vane rotor, in which the stator ring is made to slide in response to the pressure difference in two chambers located at opposite sides of the stator ring and connected to the delivery side of the pump, one chamber directly and the other one through a control valve. The translation is guided by the same members on which the pressure controlling translation acts.
  • the stator ring includes guiding means arranged to slide in a guiding chamber formed in the pump body and preferably communicating with a pressure zone of the pump in order to receive fluid under pressure therefrom, and in that the guiding means, during the translation of the stator ring, are arranged to be pushed by the fluid under pressure into sealing contact with a surface of the guiding chamber and, in a zone of contact with such a surface, they have a curvature with such a radius that a homogeneous contact pressure distribution is ensured as the operating conditions of the pump and, consequently, the position of the stator ring, vary.
  • the guiding means comprise a pair of fins, which extend substantially tangentially to the stator ring and in opposite directions from an outer surface of the ring, define a common push surface that is acted upon by the fluid under pressure and a pair of contact areas each having the radius of curvature ensuring the homogeneous contact pressure distribution, and have rounded free ends.
  • the translation may be mechanically controlled, by the action of the pressures in a circuit utilising the pumped fluid, or electronically controlled, by means of a motor controlled by an electronic control unit detecting the conditions of the same fluid in a utilisation circuit.
  • the invention also implements a method of regulating the displacement of a rotary positive displacement pump by means of the translation of a stator ring inside which the pump rotor eccentrically rotates.
  • a translation is guided by guiding means arranged to slide in contact with a surface of a guiding chamber, formed in the pump body, due to the action of a pressurised fluid preferably coming from the delivery side of the pump, and the guiding means are made to contact the surface of the guiding chamber at a zone of the surface of the guiding means having a curvature with such a radius that a homogeneous contact pressure distribution is ensured as the operating conditions of the pump and, consequently, the position of the stator ring, vary.
  • a lubrication system for a motor vehicle engine in which the adjustable displacement pump and the method of regulating the displacement set forth above are employed.
  • reference numeral 1 generally denotes a rotary positive displacement pump with adjustable displacement, in particular a pump for the lubrication oil of a motor vehicle engine, of a kind comprising a body 2 in which a chamber 3 housing a stator ring 4 is formed.
  • Ring 4 has an internal cavity 40 in which rotor 5 eccentrically rotates and it can be translated transversally to its axis in order to regulate the pump displacement.
  • Rotor 5 is for instance a vane rotor, vanes 6 of which are radially slidable in radial slots 7, and it is driven by a suitably shaped shaft (not shown), which is inserted in a cavity 10 of complementary shape.
  • a centring ring 11 is mounted at each of both axially opposite ends of rotor 5 in order to keep the vanes in contact with the internal surface of ring 4 at low temperature and/or low speed.
  • Chamber 3 is closed by a front cover 41 and a rear cover 42.
  • Suction channel 8 communicates, through a chamber 45 in rear cover 42, with suction chambers 43, 44 formed for instance in the lower part of chamber 3 and of internal cavity 40 of the stator ring 4, respectively. Chambers 43, 44 also communicate with each other through a chamber 46 formed in front cover 41.
  • Oil is sent in conventional manner from suction chamber 44 to a delivery chamber 47 formed in cavity 40 and communicating in turn with delivery channel 9.
  • Chamber 43 preferably allows collecting possible oil leaks inside pump 1, coming from delivery chamber 47 or generally from spaces under pressure, as it will be disclosed later on.
  • Chamber 43 if it is located at a lower level than channel 8, also prevents the pump from emptying at the start from a stationary condition, after a long stop.
  • the translation of ring 4 which, by way of example, is supposed to take place horizontally, is controlled by the oil pressure in the engine lubrication circuit, as it will be disclosed later on.
  • the translation of ring 4 is caused by a pair of substantially cylindrical push heads 13, 14, which act on two diametrically opposite areas of ring 4.
  • the contacting surfaces in heads 13, 14 and ring 4 are flat surfaces, as shown in Fig. 3 for head 14.
  • a flat contact surface does not demand special workings.
  • a projection 12 in the wall of chamber 3 acts as a stop for the maximum displacement stroke and it is arranged to maintain, in such a condition, a certain clearance between ring 4 and rotor 5, as it is better visible in Fig. 4 .
  • the position taken by ring 4 in the condition of maximum displacement of the pump is also the reference position for mounting the ring into seat 3.
  • Heads 13, 14 are mounted in body 2 so as to be slidable in respective chambers 15, 16, which are closed by plugs 17 and 18 and which receive pressurised oil from the lubrication circuit of the engine either directly (chamber 16) or through a regulation valve 19 (chamber 15), also controlled by the oil pressure in the lubrication circuit.
  • the first push head 13 is also biased by a spring 20 that is preloaded so that head 13 keeps ring 4 in a position of maximum displacement of the pump ( Figs. 2 , 5 ) under low oil pressure conditions, in particular at the motor start.
  • the flat surfaces of head 13 and ring 4 in their contacting zones allow a homogeneous distribution of the force generated by spring 20 on ring 4.
  • the second head 14 is actuated to displace ring 4 from the maximum displacement position towards the minimum displacement position when oil pressure in chamber 16 exceeds the preload of spring 20, and it is pushed backwards by ring 4 when the latter moves back to the maximum displacement position as oil pressure in chamber 16 decreases. Thanks to a spacer 21, which may also be integrally formed with head 14, the latter is always kept in contact with ring 4 and does not adhere to plug 18.
  • Regulation valve 19 may be made to slide parallel to the displacement direction of ring 4, in order to manage the regulation pressures, thanks to a pair of push surfaces 19a, 19b which are acted upon by the oil pressure.
  • a spring 24 tends to maintain valve 19 in the position required in order ring 4 remains in the maximum displacement position.
  • Valve 19 may be integrated into pump body 2, in a seat 22 closed by a plug 23, as shown in Figs. 5 , 6 , or in the engine block, depending on the particular engine. In any case, body 2 will be provided with seat 22 independently of the actual presence of the valve, so that a same pump body can always be utilised.
  • Ring 4 is so shaped as to have a guiding member, advantageously consisting of a pair of fins 25 formed for instance in the top portion of ring 4.
  • the fins extend substantially tangentially to the ring in opposite directions and they are housed in a guiding chamber 26 formed in body 2 and communicating with delivery channel 9.
  • fins 25 slide in contact with the walls of chamber 2 and the contact is ensured by the pressure of oil picked up from delivery channel 9 and acting on top faces 27 of fins 25, defining a common push surface.
  • the communication between delivery channel 9 and chamber 26 is obtained through a duct (not visible in the drawing) formed by means of a suitable working of rear cover 41 and/or body 2.
  • each fin 25 and body 2 The shape of contact area 29 between each fin 25 and body 2 is such as to counterbalance the pressure forces generated inside the pump during operation and to maintain the contact with body 2 in a limited area in any operating condition. In this manner, there is no need for sealing elements.
  • fins 25 contact body 2 according to a curved surface having a curvature with relatively wide radius R designed so as:
  • the free ends of fins 25 have a rounded shape, designed so as to avoid that, due to the forces exerted by the moving fins or by internal overpressures (which could bring the fins in contact with the upper surface of chamber 26, Fig. 8 ), ring 4 is blocked in case of an unbalance due to an overpressure surge within the pump.
  • lubrication circuit 100 of a motor vehicle engine 30 using pump 1 is shown.
  • Reference numerals 31 and 32 denote the oil sump and the oil filter, connected in conventional manner to the suction and delivery channels 8 and 9 ( Fig. 1 ), through ducts also denoted by reference numerals 8 and 9.
  • Reference numeral 33 denotes the outlet duct of filter 12, conveying oil to engine 30.
  • a branch 9a of delivery channel 9 conveys oil into chamber 26 in order to push fins 25 into contact with the base of chamber 26.
  • a branch actually is a duct formed internally of the pump body.
  • a first branch 33a of duct 33 forms a first regulation duct conveying pressurised oil to chamber 16.
  • a second and a third branch 33b, 33c of the same duct convey oil to a first and a second inlet 49a, 49b of valve 19.
  • Oil fed to the first inlet 49a preferably acts on the first push surface 19a in order to control the possible displacement of valve 19, whereas oil fed to the second inlet 49b may be transferred either to a second regulation duct 35, communicating with chamber 15, or to exhaust 37.
  • the second branch 33b conveys oil also to a distribution valve 36, for instance an electromagnetic valve. Depending on the position of this valve, oil leaving filter 32 may be conveyed, through a duct 34, to a third inlet 49c of valve 19, where oil acts on a second push surface 19b, or oil present in valve 19 in correspondence of inlet 49c may be sent back to oil sump 31 (duct 38).
  • a distribution valve 36 for instance an electromagnetic valve.
  • oil leaving filter 32 may be conveyed, through a duct 34, to a third inlet 49c of valve 19, where oil acts on a second push surface 19b, or oil present in valve 19 in correspondence of inlet 49c may be sent back to oil sump 31 (duct 38).
  • oil fed to the first inlet 49a and to the third inlet 49c may act in reversed manner, for instance so that the first inlet 49a and the third inlet 49c act on the second push surface 19b and the first push surface 19a, respectively.
  • the regulation pressures could be taken from delivery channel 9 instead of being taken from outlet duct 33 of the filter.
  • the illustrated solution is the solution ensuring the greatest stability in the regulation pressure since, as known, due the nature of the positive displacement pumps, the delivery pressure has surges that are smoothed by filter 32.
  • valve 19 is located in pump body 2, ducts 33a, 33b, 34 35 will be formed, at least in part, in body 2 by means of a suitable working, in similar manner to what has been stated for the duct putting delivery channel 9 in communication with chamber 26.
  • pump 1 The operation of pump 1 is as follows.
  • valve 19 During the operation of pump 1, the pressure at outlet 33 from filter 32 (and hence at inlet 49a of valve 19) increases and, once it has exceeded a given threshold, it overcomes the preload of spring 24, thereby making valve 19 displace to the right.
  • the displacement of valve 19 progressively closes inlet 49b and puts chamber 15 in communication with exhaust 37. In this manner, the pressure in chamber 15 decreases and the pressure in chamber 16 can overcome the preload of spring 21 and displace ring 4 proportionally to the pressure drop in chamber 15.
  • the displacement of ring 4 ends when the minimum displacement position is reached ( Fig. 10 ).
  • valve 36 If an intervention of valve 19 at a pressure level different from the high pressure level described above is desired, electromagnetic valve 36 will be actuated so as to apply the pressure existing at outlet 33 of filter 32 also to inlet 49c of valve 19 ( Fig. 11 ). The push is now exerted on both push surfaces 19a, 19b and hence the preload of spring 20 can be overcome by a pressure lower than the previous one. It is clear for the skilled in the art that valve 36 also allows obtaining also multiple actuation levels different from the high pressure level for regulation valve 19.
  • the mechanical and/or geometrical tolerances and the surface conditions suitable for ensuring the proper sliding of ring 4 only concern the small contact zone between ring 4 and body 2 (that is, between fins 25 and guide 26), whereas the whole remaining surface of the fins may remain raw. Also a special working of the ring surface zones in contact with push heads 13, 14 is not required. This allows reducing the manufacturing costs.
  • the wide radius R in zone 28 allows reducing the contact pressure and, as the pressure acting on ring 4 varies during operation, it allows displacing the contact point while keeping the shape of the contact pressure distribution constant. This prevents sticking and wear of the parts in relative movement, always possible in the prior art. Also the rounded shapes of the ends of fins 25 contribute to avoiding sticking during the normal sliding of ring 4 or during possible unbalances of same due to overpressure surges inside the pump.
  • the constant contact between fins 25 and body 2 eliminates the need for sealing elements in order to avoid excessive oil leaks, thereby contributing to the constructional simplicity and hence to the limitation of the manufacturing costs.
  • the lack of sealing elements moreover assists in having a faster system response to the displacement variation signal.
  • an electronic control is also possible, through a small electric motor (brushless, three-phase synchronous or step-by-step motor) directly connected to ring 4 through a lever system, a mechanical coupling or another linkage arranged to convert the rotary movement of the motor into a translatory movement.
  • the motor will be electronically controlled by the electronic control unit of the motor vehicle, thereby ensuring a greater accuracy and a greater readiness in the intervention.

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

Claims (11)

  1. Pompe volumétrique rotative destinée à des fluides, comportant un rotor (5) agencé pour tourner de façon excentrée dans une chambre (40) définie à l'intérieur d'une bague de stator (4), laquelle est placée dans une embase (3) formée dans un corps de pompe (2) et est raccordée à des moyens (13, 14, 15, 19) pour translater une telle bague par rapport au rotor (5), lorsque les conditions de fonctionnement de la pompe (1) varient, en vue de modifier le débit volumétrique de la pompe, dans laquelle la bague de stator (4) comporte des moyens de guidage (25) agencés pour coulisser dans une chambre de guidage (26) formée dans le corps de la pompe (2) et communiquant avec une zone de pression de la pompe (1) ou avec des dispositifs d'utilisation (100) d'un fluide pompé, afin de recevoir, à partir d'elle, du fluide sous pression, caractérisée en ce que les moyens de guidage (25), pendant la translation de la bague de stator (4), sont agencés pour être poussés par le fluide sous pression en vue d'établir un contact étanche avec une surface de la chambre de guidage (26) et, dans une zone (28) de contact avec cette surface, ils présentent une courbure dotée d'un rayon de courbure (R) tel qu'une distribution homogène de la pression de contact est assurée lorsque les conditions de fonctionnement de la pompe (1) et, en conséquence, la position de la bague de stator (4), varient.
  2. Pompe selon la revendication 1, dans laquelle les moyens de guidage (25) comprennent une paire d'ailettes orientées dans des directions opposées (35) s'étendant essentiellement, de façon tangentielle à la bague de stator (4) à partir d'une surface extérieure de la bague de stator (4) et définissant une surface de poussée commune (27) qui est activée par le fluide sous pression et une paire de zones de contact (28) présentant, chacune, ladite courbure dotée d'un rayon de courbure (R) tel que la distribution homogène de la pression de contact est assurée.
  3. Pompe selon la revendication 2, dans laquelle les ailettes (25) présentent des extrémités libres arrondies.
  4. Pompe selon l'une quelconque des revendications 1 à 3, dans laquelle la translation de la bague de rotor (4) est commandée par une première et une seconde têtes de poussée (13, 14), lesquelles agissent sur des surfaces diamétralement opposées de la bague et sont agencées pour coulisser, respectivement, dans une première et dans une seconde chambre de poussée (15 , 16), lesquelles chambres sont distinctes de la chambre de guidage (26) et communiquent avec la zone de pression de la pompe (1) ou, de préférence, avec les dispositifs d'utilisation (100) du fluide pompé, par l'intermédiaire d'une vanne de régulation (19) ou directement, respectivement.
  5. Pompe selon la revendication 4, dans laquelle la vanne de régulation (19) est intégrée dans la pompe (1).
  6. Pompe selon la revendication 4 ou 5, dans laquelle les têtes de poussée (13, 14) sont disposées pour séparer un environnement d'aspiration (43) de la pompe d'un environnement de pression élevée dans lequel les moyens de guidage (25) coulissent.
  7. Pompe selon l'une quelconque des revendications 1 à 3, dans laquelle la translation de la bague de stator (4) est commandée par un moteur électrique.
  8. Pompe selon l'une quelconque des revendications précédentes, dans laquelle la pompe (1) est une pompe destinée à un circuit de lubrification (100) du moteur d'un véhicule à moteur.
  9. Procédé de régulation du débit volumétrique d'une pompe volumétrique rotative (1) comportant les étapes comprenant le fait de :
    - translater, par rapport à un rotor (5) de la pompe (1) une bague de stator (4) à l'intérieur de laquelle le rotor (5) tourne de façon excentrée ;
    - guider la translation de la bague de stator (4) par l'intermédiaire de moyens de guidage (25) agencés pour coulisser dans une chambre de guidage (26) formée dans un corps de pompe (2) et communiquant avec une zone de pression de la pompe (1) ou avec des dispositifs d'utilisation (100) du fluide pompé ;
    le procédé étant caractérisé en ce qu'il comporte, de plus, les étapes comprenant de :
    - laisser le fluide pompé agir sur les moyens de guidage (25) afin de les maintenir en contact étanche avec une surface de la chambre de guidage (26) pendant la translation de la bague de stator (4) ; et
    - laisser les moyens de guidage (25) en contact avec la surface de la chambre de guidage (26) au niveau d'une zone de la surface des moyens de guidage (25) qui présente une courbure dotée d'un rayon de courbure (R) tel qu'une distribution homogène de pression de contact est assurée lorsque les conditions de fonctionnement de la pompe (1) et, en conséquence, la position de la bague de stator (4), varient.
  10. Procédé selon la revendication 9, permettant de réguler le débit volumétrique d'une pompe destinée à l'huile de lubrification pour le moteur (30) d'un véhicule à moteur.
  11. Système de lubrification destiné à un moteur (30) d'un véhicule à moteur, comportant une pompe (1) selon l'une quelconque des revendications 1 à 8.
EP12815823.5A 2011-12-22 2012-12-11 Pompe volumétrique rotative et méthode de régulation de son débit volumétrique Not-in-force EP2795130B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT001188A ITTO20111188A1 (it) 2011-12-22 2011-12-22 Pompa a cilindrata variabile e metodo di regolazione della sua cilindrata
PCT/IB2012/057167 WO2013093711A1 (fr) 2011-12-22 2012-12-11 Pompe volumétrique rotative et méthode de régulation de son débit volumétrique

Publications (2)

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EP2795130A1 EP2795130A1 (fr) 2014-10-29
EP2795130B1 true EP2795130B1 (fr) 2016-03-16

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US (1) US20150292502A1 (fr)
EP (1) EP2795130B1 (fr)
IT (1) ITTO20111188A1 (fr)
WO (1) WO2013093711A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3377765B1 (fr) * 2015-11-19 2020-01-01 Pierburg Pump Technology GmbH Pompe à lubrifiant à cylindrée variable
GB2552328A (en) * 2016-07-18 2018-01-24 Delphi Int Operations Luxembourg Sarl Transfer pump
CN110332446A (zh) * 2019-07-17 2019-10-15 湖南机油泵股份有限公司 一种可以降低反馈油压力波动的机油泵

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53148703A (en) * 1977-06-01 1978-12-25 Jidosha Kiki Co Ltd Variable volumetric pump
WO2002001073A1 (fr) * 2000-06-29 2002-01-03 Tesma International Inc. Pompe volumetrique a palettes a debit variable a flux constant
AUPR602401A0 (en) 2001-06-29 2001-07-26 Smart Drug Systems Inc Sustained release delivery system
ITBO20030528A1 (it) * 2003-09-12 2005-03-13 Pierburg Spa Impianto di pompaggio utilizzante una pompa a palette
ITBO20040008A1 (it) * 2004-01-09 2004-04-09 Pierburg Spa Impianto di pompaggio
DE102004026296A1 (de) 2004-05-28 2005-12-15 Daimlerchrysler Ag Ölpumpe

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US20150292502A1 (en) 2015-10-15
EP2795130A1 (fr) 2014-10-29
ITTO20111188A1 (it) 2013-06-23
WO2013093711A1 (fr) 2013-06-27

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