EP3377765B1 - Pompe à lubrifiant à cylindrée variable - Google Patents

Pompe à lubrifiant à cylindrée variable Download PDF

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Publication number
EP3377765B1
EP3377765B1 EP15797106.0A EP15797106A EP3377765B1 EP 3377765 B1 EP3377765 B1 EP 3377765B1 EP 15797106 A EP15797106 A EP 15797106A EP 3377765 B1 EP3377765 B1 EP 3377765B1
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EP
European Patent Office
Prior art keywords
pressure
control
chamber
variable displacement
pump
Prior art date
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Active
Application number
EP15797106.0A
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German (de)
English (en)
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EP3377765A1 (fr
Inventor
Carmine Cuneo
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.)
Pierburg Pump Technology GmbH
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Pierburg Pump Technology GmbH
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Publication of EP3377765A1 publication Critical patent/EP3377765A1/fr
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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
    • 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
    • F04C2/34—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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • F04C2240/80—Other components
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring

Definitions

  • the present invention refers to a variable displacement lubricant pump for providing pressurized lubricant for an internal combustion engine.
  • the mechanical lubricant pump is mechanically driven by the engine and comprises a pump rotor with radially slidable vanes rotating in a radially shiftable control ring, whereby the control ring is pushed by a pressure control chamber into high pumping volume direction.
  • the pump is provided with a pressure control system for controlling the discharge pressure of the pressurized liquid lubricant at the pump outlet port.
  • the pump is provided with a pressure conduit for connecting an actual pressure pickup with the pressure control chamber, and the pump is also provided with a pressure control valve and a control valve, which control the pressure in the pressure control chamber.
  • WO 2012/113437 discloses a variable lubricant pump, which provides two levels of nominal pressure of the pressurized lubricant leaving the pump.
  • the lubricant pump comprises a pump rotor with radially slidable vanes rotating inside a shiftable control ring which is radially shiftable or pivotable with respect to the rotor axis between a high pumping volume position and a low pumping volume position.
  • the pump comprises a pressure control system for controlling the discharge pressure of the pressurized lubricant at the pump outlet.
  • the pressure control system comprises a fluidic pressure control chamber for pushing the shiftable control ring into high pumping volume direction.
  • the pressure control system also comprises a fluidic pilot chamber for pushing the control ring into a low pumping volume direction against the forces generated by the pressure control chamber.
  • the pressure control chamber is an antagonist of the pilot chamber.
  • the pilot chamber as well as the pressure control chamber are directly fluidically charged with the discharge pressure.
  • WO2015/074700 , WO2013/093711 and WO2010/006705 disclose variable displacement lubricant pumps and the associated processes for controlling the pumps' displacement of the background art.
  • the object of the present invention is to provide a variable displacement lubricant pump with a simple control system which provides three different levels of nominal pressure of the pressurized lubricant leaving the pump.
  • variable-displacement lubricant vane pump having the features of claim 1.
  • variable displacement lubricant pump is provided with a pump rotor with radially slidable vanes rotating in a shiftable control ring.
  • the pump is provided with a pressure control chamber for pushing the control ring into a high pumping volume direction.
  • the pressure control chamber is connected to an actual pickup pressure source by a pressure conduit.
  • an actual pickup pressure source is the source from which the pressure for controlling the control chamber is used. Examples for the actual pickup pressure source are the pump outlet port or an engine main gallery.
  • the pressure control valve for controlling the pressure in the pressure control chamber comprises a control plunger, an input pressure plunger and a control spring. Dependent on the position the control plunger a first control port or a second control port is opened, alternatively. Both ports are provided in a cylinder wall of the pressure control valve and are both connected with an outlet port of the pressure control chamber. In an opened state of the first- or second control port a fluidic connection is established to a first- or second discharge port provided in a cylinder wall of the pressure control valve. The first discharge port is connected to a set value control valve, which in an opened state establishes a fluidic connection from the discharge port to the lubricant tank having atmospheric pressure.
  • the second discharge port has preferably a direct fluidic connection to the lubricant tank.
  • the input pressure plunger is directly mechanically connected with the control plunger so that a high pressure in the input pressure chamber forces the control plunger into a closed position with respect to the first control port.
  • a control spring is provided, which preloads the control plunger against the pressure in the input pressure chamber. The spring force of the control spring and the pressure in the input pressure chamber acting on the input pressure plunger, force the control plunger into an equilibrium position.
  • the pressure in the input pressure chamber is dependent on a discharge pressure of the pump, which is applied to the input pressure chamber.
  • the pressure in the input pressure chamber further is dependent on a lubricant outflow rate of the lubricant flowing from the input pressure chamber to the lubricant tank.
  • the lubricant outflow either is enabled or disabled by opening or closing the set value control valve.
  • the lubricant pump When the internal combustion engine is off the lubricant pump is not rotating and the control plunger is in an idle position. Further, the set value control valve is in an opened state. By starting the combustion engine the lubricant pump starts pumping lubricant. The lubricant pressure thereby increases to a low discharge pressure level.
  • the set value control valve When, at a low discharge pressure level, the set value control valve is closed the discharge pressure level changes to an intermediate pressure level. In a closed state of the set value control valve a lubricant flow from the input pressure chamber to the lubricant tank is disabled. Further, also a lubricant flow from the first discharge port to the lubricant tank is disabled. Thus, the pressure in the input pressure chamber and the pressure control chamber increases. The pressure in the input pressure chamber moves the control plunger in the direction towards the spring.
  • the pressure in the pressure control chamber pushes the control ring to a higher pumping volume direction. Thereby also the discharge pressure of the pump will be increased. The discharge pressure will be increased until an intermediate discharge pressure level is achieved. The intermediate discharge pressure level is achieved when the control plunger closes the first control port and opens the second control port. By opening the second control port a fluidic connection between the pressure control chamber and the lubricant tank is established.
  • the set value control valve When, at an intermediate discharge pressure level, the set value control valve is opened the discharge pressure level changes to a high pressure level.
  • a lubricant flow from the input pressure chamber to the lubricant tank is enabled.
  • the control plunger thereby is temporarily forced by the spring in the direction toward the input pressure chamber.
  • the second control port will be further narrowed so that the fluid rate of the fluid leaving the pressure control chamber decreases and thus the pressure in the pressure control chamber increases.
  • the pressure in the pressure control chamber pushes the control ring to the high pumping volume direction. Thereby, also the discharge pressure will be increased. This leads to a movement of the control plunger in the direction to the spring.
  • the discharge pressure will be increased until the high discharge pressure level is achieved.
  • the discharge pressure level changes to an intermediate pressure level.
  • a lubricant flow from the input pressure chamber to the lubricant tank is disabled.
  • the pressure in the input pressure chamber increases.
  • the pressure in the input pressure chamber thereby temporarily moves the control plunger in the direction to the spring.
  • An orifice of the second control valve will be fully opened so that the lubricant flow from the pressure control chamber to the lubricant tank is increased and the pressure in the pressure control chamber decreases.
  • the control ring thereby moves to a low pumping volume direction.
  • the discharge pressure will be decreased leading to a movement of the control plunger in the direction to the input pressure chamber and the control ring to a low pumping volume direction.
  • the discharge pressure will be decreased until an intermediate discharge pressure level is achieved.
  • variable displacement lubricant pump therefore can provide three different discharge pressure levels.
  • the discharge pressure can be changed to the intermediate pressure level and to the high pressure level by simply switching a set value control valve.
  • the low pressure level is available after starting the engine. After the pressure has been increased to an intermediate level the low pressure level can be set after restarting the engine or if the engine pressure is below the low pressure level.
  • the set value control valve is a solenoid valve.
  • a solenoid valve has the advantage that a fast switching of the valve is possible.
  • a throttle valve is provided in flow direction before the input pressure chamber.
  • a throttle valve according to the invention is a calibrated orifice, which reduces the flow cross section in an unchangeable manner so that a defined pressure loss is generated. Therefore it is possible to adjust the pressure in flow direction behind the throttle valve.
  • a respective throttle valve is preferably also provided in flow direction behind the input pressure chamber.
  • a pilot chamber is provided, which is connected to the pump outlet port and is pushing the control ring into the low pumping volume direction.
  • control ring is pretensioned by a spring into the high pumping volume direction.
  • the spring is an antagonist of the pilot chamber.
  • the second discharge port is directly connected to the lubricant tank.
  • an electronic control device is connected to a lubricant temperature sensor and controlling the outlet valve.
  • the lubricant temperature sensor detects the temperature of the lubricant in the engine.
  • the electronic control device decides whether to open or to close the set value control valve in order to change the discharge pressure level of the pump.
  • the electronic control device is connected to a speed sensor and controlling the outlet valve.
  • the speed sensor detects the speed of an e.g. vehicle.
  • the electronic control device decides whether to open or to close the set value control valve in order to change the discharge pressure level of the pump.
  • an engine load sensor is provided. Dependent on a detected engine load value the electronic control device decides whether to open or to close the set value control valve in order to change the discharge pressure level of the pump.
  • a pressure sensor is provided. Dependent on a detected pressure value the electronic control device decides whether to open or to close the set value control valve in order to change the discharge pressure level of the pump.
  • FIG. 1 shows a schematic representation of a variable displacement lubricant pump 10 for supplying an internal combustion engine 12 with pressurized lubricant.
  • the pump 10 comprises a pumping unit 14, which is mechanically driven by the engine 12.
  • the pumping unit 14 comprises a housing 40 having a cavity 41 in which a control ring 42 translates, which encircles a pump rotor 44.
  • the pump rotor 44 is provided with numerous radially slidable vanes 46, whereby the vanes 46 are rotating inside the control ring 42.
  • the control ring 42 is radially shiftable so that the eccentricity of the control ring 42 with respect to a rotation axis 47 of the pump rotor 44 can be set to thereby shift the control ring between a low pumping volume at low eccentricity position and a high pumping volume position at high eccentricity.
  • the housing 40 is closed by two side walls 48 of which one is not shown in the drawing.
  • the side walls 48, the vanes 46, the pump rotor 44 and the control ring 42 define five rotating pump chambers 50.
  • the control ring 42 is provided with a first control ring plunger 52 housed in a pressure control chamber 54 and is provided with a second control ring plunger 55 housed in a pilot chamber 56.
  • the pilot chamber 56 is provided opposite to the pressure control chamber 54.
  • the control ring 42 and the plungers 52, 55 are one single integral part.
  • the pressure control chamber 54 is defined by the housing 40.
  • the housing 40 also comprises a inlet port 58 for sucking the lubricant from a lubricant tank 60 and a outlet port 62 for feeding lubricant with a discharge pressure to the engine 12.
  • An engine supply conduit 64 extends from the outlet port 62 to the engine 12 to supply the engine 12 with pressurized lubricant.
  • the lubricant discharge pressure at the outlet port 62 is transmitted to the pressure control chamber 54 via a conduit 66, 68 and through a pressure throttle valve 70 in which a calibrated pressure drop occurs as the lubricant flows through.
  • the lubricant discharge pressure is also transmitted to the pilot chamber 56 via a pilot chamber conduit 71.
  • the outlet port 62 is also connected via a conduit 66, 72 and through a pressure throttle valve 74 to an input pressure port 76 of a pressure control valve 78.
  • the pressure control valve 78 keeps the outlet pressure at the outlet port 62 at a constant nominal pressure value independently of the rotational speed of the engine 12 by regulating the radial position of the control ring 42.
  • the radial position of the control ring 42 is controlled by controlling the pressure in the pressure control chamber 54.
  • the pressure in the pressure control chamber 54 is regulated by controlling a lubricant discharge of an outlet port 79 of the pressure control chamber 54 via conduit 80, 81 by closing and opening a first control port 82 and a second control port 83 in a cylinder wall 84 of a pressure control valve housing 85.
  • the first or the second control port 82, 83 is open and the other port 83, 82 is closed.
  • the position of the control plunger 86 is dependent on a pressure in an input pressure chamber 88, which pressure thereby is charged to an input pressure plunger 90 and on a preload applied to the control plunger 86 by a control spring 92.
  • the control spring 92 acts against the pressure in the input pressure chamber 88.
  • the input pressure plunger 90 is mechanically directly connected with the control plunger 86 so that a high pressure in the input pressure chamber 88 forces the control plunger 86 in a closed position with respect to the first control port 82.
  • Figure 1 shows a position of the control plunger 86 in which the first control port 82 is open, while the second control port 83 is closed.
  • the first control port 82 thereby is fluidically connected through a first discharge port 94 in the cylinder wall 84 of the pressure control valve 78 to a solenoid valve as a set value control valve 96.
  • the solenoid valve is controlled by an electronic control device 97, which is connected to a lubricant temperature sensor 98.
  • the lubricant temperature sensor 98 measures the temperature of the lubricant in the engine 12.
  • the solenoid valve is in an open state so that the pressure control chamber 54 is fluidically connected by the open first control port 82 to the lubricant tank 60.
  • the input pressure chamber 88 is connected via a conduit 99 and through a pressure throttle valve 100 to the solenoid valve. If the solenoid valve in figure 1 is in an open state, the input pressure chamber 88 is fluidically connected to the lubricant tank 60.
  • the input pressure chamber 88 and the first control port 82 are fluidically disconnected from the lubricant tank 60.
  • the pressure in the input pressure chamber 88 and in the pressure control chamber 54 increases.
  • the pressure in the input pressure chamber 88 moves the control plunger 86 in the direction to the control spring 92.
  • the pressure in the pressure control chamber 54 pushes the control ring 42 to a high pumping volume direction.
  • the discharge pressure of the pumping unit 14 increases leading to a further movement of the control plunger 86.
  • the discharge pressure will be increased until a new equilibrium plunger position is achieved.
  • the new equilibrium position is achieved when the control plunger 86 closes the first control port 80 and opens the second control port 83.
  • the input pressure chamber 88 By opening the solenoid valve in a state of an intermediate pressure the input pressure chamber 88 is again fluidically connected to the lubricant tank 60. Thereby the pressure in the input pressure chamber 88 decreases. The control plunger 86 thereby is temporarily forced by the control spring 92 in the direction to the input pressure chamber 88. The second control port 82 further will be narrowed so that less fluid leaves the pressure control chamber 54 and the discharge pressure increases. The pressure in the pressure control chamber 54 pushes the control ring 42 to a high pumping volume direction. Thereby also the discharge pressure will be increased leading to a movement of the control plunger 86 in the direction to the control spring 92 and of the control ring 42 to a high pumping volume direction. The discharge pressure will be increased until an equilibrium situation is achieved. In figure 3 a respective equilibrium situation is achieved. In this state the pump discharges a high discharge pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (12)

  1. Pompe à lubrifiant à cylindrée variable (10) reliée fluidiquement à et entraînée mécaniquement par un moteur à combustion interne (12) pour pomper du lubrifiant sous pression vers le moteur (12), comprenant:
    - un rotor de pompe (44) à aubes (46) aptes à coulisser radialement dans une bague de commande déplaçable (42) pouvant se déplacer ou pivoter radialement par rapport à l'axe du rotor (47) entre une position de volume de pompage haut et une position de volume de pompage bas,
    - un système de commande de pression pour contrôler la pression de refoulement du lubrifiant sous pression, le système de commande comprenant:
    - une chambre de régulation de pression (54) pour pousser la bague de commande (42) dans la direction d'un volume de pompage haut,
    - un conduit de pression (66, 68) pour relier une source de pression de prélèvement actuelle à la chambre de régulation de pression (54), et
    - une soupape de réglage de pression (78) contrôlant la pression dans la chambre de réglage de pression (54), la soupape de réglage de pression (78) comprenant:
    - un plongeur de réglage (86), qui peut être déplacé entre une première position, dans laquelle un premier orifice de commande (82) dans une paroi de cylindre (84) de la soupape de commande de pression (78) est relié à un premier orifice de décharge (94) dans la paroi de cylindre (84) et un deuxième orifice de commande (83) dans la paroi du cylindre (84) est fermée, et une seconde position, dans laquelle le premier orifice de commande (82) est fermé et le deuxième orifice de commande (83) est relié à un deuxième orifice de décharge (102) dans la paroi du cylindre (84), les premier et deuxième orifices de commande (82, 83) étant reliés à un orifice de sortie (79) de la chambre de régulation de pression (54),
    - un plongeur de pression d'entrée (90) étant chargé avec une pression dans une chambre de pression d'entrée (88) alimentée par un orifice de sortie de pompe (62), dans lequel le plongeur de pression d'entrée (90) est relié mécaniquement au plongeur de commande (86), et
    - un ressort de commande (92) qui précontraint le plongeur de commande (86) dans la première position contre le pression dans la chambre de pression d'entrée (88),
    - une soupape de réglage de la valeur de consigne (96) qui peut être commutée entre un état ouvert et un état fermé, ou, à l'état ouvert, la soupape de réglage de la valeur de consigne (96) relie de manière fluidique le premier orifice de décharge (94) ainsi que la chambre de pression d'entrée (88) à un réservoir de lubrifiant (60).
  2. Pompe à lubrifiant à cylindrée variable (10) selon la revendication 1, caractérisée en ce que la soupape de réglage de valeur de consigne (96) est une électrovanne.
  3. Pompe à lubrifiant à cylindrée variable (10) selon l'une des revendications précédentes, caractérisée en ce qu'un papillon (74) est prévu dans la direction de l'écoulement en amont de la chambre de pression d'entrée (88).
  4. Pompe à lubrifiant à cylindrée variable (10) selon l'une des revendications précédentes, caractérisée en ce qu'un papillon (100) est prévu dans la direction de l'écoulement en aval de la chambre de pression d'entrée (88).
  5. Pompe à lubrifiant à cylindrée variable (10) selon l'une des revendications précédentes, caractérisée par une chambre de pilotage (56) reliée à l'orifice de sortie de la pompe (62) et poussant la bague de commande (42) dans la direction du volume de pompage bas.
  6. Pompe à lubrifiant à cylindrée variable (10) selon l'une des revendications précédentes, caractérisée en ce que la bague de commande (42) est précontrainte par un ressort (57) dans la direction du volume de pompage haut.
  7. Pompe à lubrifiant à cylindrée variable (10) selon l'une des revendications précédentes, caractérisée en ce que le deuxième orifice de décharge (102) est directement relié au réservoir de lubrifiant (60).
  8. Pompe à lubrifiant à cylindrée variable (10) selon l'une des revendications précédentes, caractérisée en ce qu'un papillon (70) est prévu dans la direction de l'écoulement en amont de la chambre de commande (54).
  9. Pompe à lubrifiant à cylindrée variable (10) selon l'une des revendications précédentes, caractérisée par un dispositif de commande électronique (97) relié à un capteur de température de lubrifiant (98) et commandant la soupape de réglage de valeur de consigne (96).
  10. Pompe à lubrifiant à cylindrée variable (10) selon les revendications 1 à 8, caractérisée par un dispositif de commande électronique (97) relié à un capteur de vitesse et commandant la soupape de réglage de valeur de consigne (96).
  11. Pompe à lubrifiant à cylindrée variable (10) selon les revendications 1 à 8, caractérisée par un dispositif de commande électronique (97) relié à un capteur de charge du moteur et commandant la soupape de réglage de valeur de consigne (96).
  12. Pompe à lubrifiant à cylindrée variable (10) selon les revendications 1 à 8, caractérisée par un dispositif de commande électronique (97) relié à un capteur de pression et commandant la soupape de réglage de valeur de consigne (96).
EP15797106.0A 2015-11-19 2015-11-19 Pompe à lubrifiant à cylindrée variable Active EP3377765B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2015/077085 WO2017084710A1 (fr) 2015-11-19 2015-11-19 Pompe à lubrifiant à cylindrée variable

Publications (2)

Publication Number Publication Date
EP3377765A1 EP3377765A1 (fr) 2018-09-26
EP3377765B1 true EP3377765B1 (fr) 2020-01-01

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EP15797106.0A Active EP3377765B1 (fr) 2015-11-19 2015-11-19 Pompe à lubrifiant à cylindrée variable

Country Status (2)

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EP (1) EP3377765B1 (fr)
WO (1) WO2017084710A1 (fr)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2307726B1 (fr) * 2008-07-15 2016-01-27 Magna Powertrain Bad Homburg GmbH Pompe à cylindrée variable
ITTO20111188A1 (it) * 2011-12-22 2013-06-23 Vhit Spa Pompa a cilindrata variabile e metodo di regolazione della sua cilindrata
CN105960531B (zh) * 2013-11-21 2018-01-02 皮尔伯格泵技术有限责任公司 可变排量润滑剂泵

Non-Patent Citations (1)

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

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WO2017084710A1 (fr) 2017-05-26
EP3377765A1 (fr) 2018-09-26

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