WO2013093711A1 - 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
WO2013093711A1
WO2013093711A1 PCT/IB2012/057167 IB2012057167W WO2013093711A1 WO 2013093711 A1 WO2013093711 A1 WO 2013093711A1 IB 2012057167 W IB2012057167 W IB 2012057167W WO 2013093711 A1 WO2013093711 A1 WO 2013093711A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
stator ring
chamber
displacement
ring
Prior art date
Application number
PCT/IB2012/057167
Other languages
English (en)
Inventor
Matteo Cortesi
Luca Stagnoli
Original Assignee
Vhit S.P.A.
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 Vhit S.P.A. filed Critical Vhit S.P.A.
Priority to EP12815823.5A priority Critical patent/EP2795130B1/fr
Priority to US14/367,710 priority patent/US20150292502A1/en
Publication of WO2013093711A1 publication Critical patent/WO2013093711A1/fr

Links

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
    • 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
    • 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
    • F04C2/321—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 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • F04C13/002—Pumps for particular liquids for homogeneous viscous liquids
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • 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
    • 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
    • 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
    • F04C2250/30—Geometry of the stator
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure

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.
  • This prior art pump has a number of problems that mainly affect just the ring and concern in particular:
  • the pressure controlling the displacement of the stator ring is the pressure at the delivery side, and this entails that the system is considerably sensitive to the pressure fluctuations, typical of positive displacement pumps, present at the pump delivery side;
  • 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 there from, 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.
  • FIG. 1 is an axial sectional view of a pump according to the invention
  • FIG. 2 is a front view of the pump, without the front cover, showing the stator ring in the maximum displacement position;
  • FIG. 3 is enlarged views of details A and B of Fig. 2;
  • FIG. 5 and 6 are cross-sectional views of the pump, showing the stator ring in the maximum displacement and minimum displacement positions, respectively;
  • Figs. 7 and 8 are enlarged views of details of the guiding fins of the stator ring.
  • Figs. 9 to 11 are diagrams of a lubrication circuit of a motor vehicle engine using the pump according to the invention, in different operating conditions.
  • 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
  • heads 13, 14 and ring 4 are flat surfaces, as shown in Fig. 3 for head
  • 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.

Abstract

L'invention concerne une pompe volumétrique rotative pour des fluides, en particulier pour l'huile de lubrification d'un moteur de véhicule motorisé (30), dont le débit volumétrique peut être régulé grâce à la translation d'une bague de stator (4) entourant le rotor (5) de la pompe (1) avec une excentration dépendant de la position de ladite bague suite à la translation. La translation est guidée par des ailettes de guidage (25) coulissant en contact avec une surface d'une chambre de guidage (26), en communication avec le côté refoulement de la pompe (1), grâce à l'action du fluide sous pression introduit dans ladite chambre et agissant sur les ailettes (25). La zone de contact (28) est telle qu'une distribution homogène de pression de contact est assurée au fur et à mesure de la variation des conditions d'exploitation de la pompe (1) et par conséquent de la position de la bague de stator (4). L'invention concerne aussi une méthode de régulation du débit volumétrique de la pompe (1) et un système de lubrification pour un moteur de véhicule motorisé dans lequel on utilise la pompe (1).
PCT/IB2012/057167 2011-12-22 2012-12-11 Pompe volumétrique rotative et méthode de régulation de son débit volumétrique WO2013093711A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP12815823.5A EP2795130B1 (fr) 2011-12-22 2012-12-11 Pompe volumétrique rotative et méthode de régulation de son débit volumétrique
US14/367,710 US20150292502A1 (en) 2011-12-22 2012-12-11 Rotary positive displacement pump and method of regulating its displacement

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
ITTO2011A001188 2011-12-22

Publications (1)

Publication Number Publication Date
WO2013093711A1 true WO2013093711A1 (fr) 2013-06-27

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ID=45541021

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2012/057167 WO2013093711A1 (fr) 2011-12-22 2012-12-11 Pompe volumétrique rotative et méthode de régulation de son débit volumétrique

Country Status (4)

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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017084710A1 (fr) * 2015-11-19 2017-05-26 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

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Citations (5)

* 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
US20040247643A1 (en) 2001-06-29 2004-12-09 Martinod Serge R Sustained release delivey system
WO2005068838A1 (fr) 2004-01-09 2005-07-28 Pierburg S.P.A. Systeme de pompage
EP1600637A2 (fr) 2004-05-28 2005-11-30 DaimlerChrysler AG Pompe à huile à capacité variable
US20080038117A1 (en) 2003-09-12 2008-02-14 Giacomo Armenio Pumping System Employing a Variable-Displacement Vane Pump

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2381272C (fr) * 2000-06-29 2011-04-26 Tesma International Inc. Pompe volumetrique a palettes a debit variable a flux constant

Patent Citations (5)

* 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
US20040247643A1 (en) 2001-06-29 2004-12-09 Martinod Serge R Sustained release delivey system
US20080038117A1 (en) 2003-09-12 2008-02-14 Giacomo Armenio Pumping System Employing a Variable-Displacement Vane Pump
WO2005068838A1 (fr) 2004-01-09 2005-07-28 Pierburg S.P.A. Systeme de pompage
EP1600637A2 (fr) 2004-05-28 2005-11-30 DaimlerChrysler AG Pompe à huile à capacité variable

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017084710A1 (fr) * 2015-11-19 2017-05-26 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

Also Published As

Publication number Publication date
EP2795130B1 (fr) 2016-03-16
EP2795130A1 (fr) 2014-10-29
US20150292502A1 (en) 2015-10-15
ITTO20111188A1 (it) 2013-06-23

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