EP2751393A1 - Lubricant vane pump - Google Patents

Lubricant vane pump

Info

Publication number
EP2751393A1
EP2751393A1 EP11754860.2A EP11754860A EP2751393A1 EP 2751393 A1 EP2751393 A1 EP 2751393A1 EP 11754860 A EP11754860 A EP 11754860A EP 2751393 A1 EP2751393 A1 EP 2751393A1
Authority
EP
European Patent Office
Prior art keywords
sector
pumping chamber
stator ring
stator
outlet
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.)
Granted
Application number
EP11754860.2A
Other languages
German (de)
French (fr)
Other versions
EP2751393B1 (en
Inventor
Matteo Gasperini
Alessandro TESTA
Giacomo Armenio
Raffaele Squarcini
Nicola Novi
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
Original Assignee
Pierburg Pump Technology GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pierburg Pump Technology GmbH filed Critical Pierburg Pump Technology GmbH
Publication of EP2751393A1 publication Critical patent/EP2751393A1/en
Application granted granted Critical
Publication of EP2751393B1 publication Critical patent/EP2751393B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • 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
    • F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters
    • 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
    • F04C2270/13—Noise

Definitions

  • the invention refers to a lubricant vane pump for delivering the lubricant to an internal combustion engine.
  • a lubricant vane pump is a volumetric pump and is provided with a pump rotor including siidable vanes rotating in a circumferentiai stator ring.
  • the siidable vanes, the stator ring and two stator side walls define a plurality of rotating pumping chambers rotating in the pump cavity which is enclosed by the stator ring and the stator side walls.
  • the pump cavity is separated into an inlet sector with an inlet opening, an outlet sector with an outlet opening and an intermediate sector between the inlet sector and the outlet sector.
  • the intermediate sector is, seen in the rotating direction of, arranged between the inlet sector and the outlet sector and has an intermediate sector angle which is more or less equal to the pumping chamber angle which is defined by two neighbor vanes.
  • the lubricant pumped by the lubricant vane pump is incompressible oil with an unavoidable fraction of compressible air.
  • the content of the rotating pumping chamber is not considerably compressed so that the lubricant in the rotating pumping chamber is more or less under atmospheric pressure when the pumping chamber is connected to the pump outlet sector.
  • the pressurized lubricant of the outlet sector flows backwards into the pumping chamber so that oscillations of the lubricant mass occur until the pressure outside and inside the pumping chamber is equalized. This leads to so-called hydraulic noise which causes acoustic noise and increased wearing of the vane pump.
  • the hydrau!ic noise is reduced by pre-compressing the Iubricant-air-mixture in the pumping chamber passing the intermediate sector before the pumping chamber is connected to the outlet sector. This measure reduces the efficiency of the lubricant vane pump.
  • the stator ring of state of the art lubricant vane pumps is normally simply circular.
  • the lubricant vane pump according to the invention is provided with a non-circular stator ring which is provided with an isovolumetric contour in the intermediate sector.
  • the lubricant-air mixture rotating in the pumping chamber through the intermediate sector is neither significantly decompressed nor signiRcantfy compressed so that the constant volume of the iubricant-air-mixture is maintained in the intermediate sector.
  • the intermediate sector angle exceeds the pumping chamber angle by an intermediate closing angle of at least 5° so that the mixture of lubricant and air has a short moment between the disconnection from the inlet sector and connection to the outlet sector to still.
  • the pumping chamber volume of the rotating pumping chamber in the intermediate sector is constant over at least the last 5° before the rotating pumping chamber is opened to the outlet sector. Since the lubricant-air mass in the pumping chamber can still before being connected to the outlet sector, the volumetric pulsation of the lubricant-air mass is reduced significantly before the mass is opened to the outlet sector. With this measure, the pressure peaks in the opening phase and the hydraulic noise caused by the pressure peaks can be reduced significantly without deteriorating the efficiency of the pump,
  • the intermediate closing angle is between 7° and 30° so that the pumping chamber volume is constant over the same angle
  • the isovolumetric dosing angle of the intermediate sector depends on many given conditions, and in particular depends on the maximum rotational speed, the necessary lubricant delivery pressure, the temperature range etc. The larger of the intermediate dosing angle is the more time is provided for the iubncant-air mass to still before it is connected to the outlet sector.
  • the circular rotor hub holding the vanes and the isovolumetric intermediate section of the stator ring both have a constant radius which refer to the same center axis.
  • the stator ring is shiftable between a high pumping volume position and a low pumping volume position .
  • Automotive lubricant vane pumps for internal combustion engines are normally directly connected with and driven by the internal combustion engine.
  • the range of the rotational speed of the pump can vary with a factor of 10 or even more.
  • the pumping volume of the vane pump can be adapted by radially shifting the stator ring so that the pumping chamber displacement per rotation can be adapted .
  • a throttle means which connects the outlet sector with the isovolumetric intermediate sector.
  • the intermediate sector is - seen in direction of the rotor rotation - arranged after the inlet sector and before the outlet sector.
  • the dosed pumping chamber situated in the intermediate sector is only connected to the outlet section by the throttle means as long as the pumping chamber is not arrived at and directly connected to the inlet opening.
  • the throttle means is only working over the last degrees of the intermediate sector.
  • the throttle means does not change its throttle characteristics during the movement of the closed pumping chamber through the intermediate sector.
  • the throttle means allows a throttled and smooth adaption of the lubricant pressure in the intermediate sector to the lubricant pressure in the outlet sector.
  • the throttle means is dimensioned so as to reduce the maximum possible pressure difference at the maximum possible rotational pump speed at least by 1/3, preferably by 1/2.
  • the throttle means can be realized as a precisely calibrated clearance which allows a defined lubricant flow from the outlet section to the intermediate section.
  • the throttle means is realized as a channel in the stator ring body or in a stator side wail of the pump.
  • the throttle channel can be realized as a small and circular orientated channel slot in the stator ring.
  • Figure 1 shows a perspective view of the lubricant vane pump whereby one side wall cover is removed
  • figure 2 shows an enlarged details of the lubricant vane pump of figure 1.
  • a mechanical variable lubricant vane pump 10 which can be directly driven by an internal combustion engine (not shown).
  • the vane pump 10 pumps a lubricant to the combustion engine with a delivery pressure.
  • the pump 10 is provided with a housing 11 consisting of a main body 16 and two side walls 17 enclosing a pump cavity of the pump 10.. In the figures, only the bottom side wall 17 is shown whereas the top side wall Is removed. Inside, the pump 10 Is provided with a shiftabie stator ring 12 and a pump rotor 14 with seven slidabie vanes 18.
  • the pump rotor 14 is provided with a driven rotor hub 20 which Is provided with vane slits wherein the vanes 18 are arranged radially shiftabie.
  • a support ring 22 is provided which supports the radially inward ends of the vanes 18.
  • the rotor 14 rotates around a static rotor axis 24 in anti-clockwise direction.
  • the stator ring 12 is shiftabie in one radial direction between a low pumping volume position and a high pumping volume position which is shown in figure 1.
  • the geometrical center of the stator ring 12 is thereby shiftabie between a high pumping volume center 26 and a iow pumping volume center 24.
  • the low pumping volume center 24 is more or less identical with the static rotor axis 24,
  • the shiftabie pump stator ring 12 is provided with a stator ring body 13 with an inlet opening 30 at one side and an outlet opening 28 at the opposite side of the stator ring body 13,
  • the pump housing 11 encloses an inlet sector A which is provided with the inlet opening 30, an outlet sector C which Is provided with the outlet opening 28 and an intermediate sector B between the inlet sector A and the outlet sector C,
  • the stator ring 12, the two stator sidewails 17 and the rotor 14 define and enclose seven rotating pumping chambers 19p -193 ⁇ 4 with a pumping chamber angle a of about 51 °.
  • Each pumping chamber 19 continuously rotates from the inlet sector A over the intermediate sector B to the outlet sector C and back to the inlet sector A.
  • the inner circumferentiaf surface of the pump stator ring 12 is not strictly circular and is provided with an isovolumetric contour 38 in the intermediate sector B.
  • the isovolumetric contour 38 starts - seen in direction of rotation - where the inlet sector A ends and continues over an intermediate sector angle of about 80°, so that the intermediate closing angle ⁇ is about 29°, As long as the leading vane 18 of the respective pumping chamber 19 0 is within the intermediate closing angle ⁇ , the pumping chamber 19o rotating through the intermediate sector B is separated from the inlet sector A and the outlet sector B,
  • the stator ring 12 in the isovolumetric intermediate sector B is formed in such a way that the volume of the rotating pumping chamber 19o remains constant over the closing angle ⁇ . Since the pressure conditions are the most dramatic when the s ' h if table stator ring 12 is in its high pumping volume position as shown in figure 1, the isovolumetric contour 38 is optimized for the high pumping volume position of the shiftable stator ring 12.
  • the outlet sector C is always in f!uidic connection with the rotating pumping chamber 19Q in the intermediate sector B by a throttle means 40,
  • the throttle means 40 is realized as a channel 41 in the stator ring body 13,
  • the throttle means 40 allows a pressure adaption of the iubricant-air mass in the rotating pumping chamber 19o before the rotating pumping chamber 19 0 arrives at the outlet sector C r so that the pressure in the rotating pumping chamber 19 0 is significantly increased and adapted to the lubricant pressure in the outlet sector C,

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

Lubricant vane pump (10) with a pump rotor (14) including at least three slidable vanes (18), a circumferential stator ring (12) and two stator side walls (17) being rectangular to the stator ring (12), whereby the rotor vanes (18), the stator ring (12) and the stator side walls (17) define rotating pumping chambers (19) with a pumping chamber angle (alpha), whereby the stator ring (12) and the stator sidewalls (17) enclose a pump cavity which is separated into an inlet sector (A) with an inlet opening (30), an outlet sector (C) with an outlet opening (28) and an intermediate sector (B) between the inlet sector (A) and the outlet sector (C), whereby the pumping chamber (19-1) running through the intermediate sector (B) is substantially closed and the intermediate sector angle (beta) exceeds the pumping chamber angle by an intermediate closing angle (gamma) of at least 5°, and whereby the stator ring (12) is provided with an intermediate isovolumetric contour (38), so that the pumping chamber volume is constant over at least the last 5,0° of the intermediate sector (B).

Description

Lubricant vane pump
The invention refers to a lubricant vane pump for delivering the lubricant to an internal combustion engine.
A lubricant vane pump is a volumetric pump and is provided with a pump rotor including siidable vanes rotating in a circumferentiai stator ring. The siidable vanes, the stator ring and two stator side walls define a plurality of rotating pumping chambers rotating in the pump cavity which is enclosed by the stator ring and the stator side walls. The pump cavity is separated into an inlet sector with an inlet opening, an outlet sector with an outlet opening and an intermediate sector between the inlet sector and the outlet sector. The intermediate sector is, seen in the rotating direction of, arranged between the inlet sector and the outlet sector and has an intermediate sector angle which is more or less equal to the pumping chamber angle which is defined by two neighbor vanes.
The lubricant pumped by the lubricant vane pump is incompressible oil with an unavoidable fraction of compressible air. When the rotating pumping chamber arrives at the outlet sector, the content of the rotating pumping chamber is not considerably compressed so that the lubricant in the rotating pumping chamber is more or less under atmospheric pressure when the pumping chamber is connected to the pump outlet sector. In the moment when the rotating pumping chamber arrives at the outlet sector the pressurized lubricant of the outlet sector flows backwards into the pumping chamber so that oscillations of the lubricant mass occur until the pressure outside and inside the pumping chamber is equalized. This leads to so-called hydraulic noise which causes acoustic noise and increased wearing of the vane pump.
In the state of the art lubricant vane pumps, the hydrau!ic noise is reduced by pre-compressing the Iubricant-air-mixture in the pumping chamber passing the intermediate sector before the pumping chamber is connected to the outlet sector. This measure reduces the efficiency of the lubricant vane pump.
It is an object of the invention to provide an efficient lubricant vane pump with reduced hydraulic noise.
This object is solved with the lubricant vane pump with the features of claim 1.
The stator ring of state of the art lubricant vane pumps is normally simply circular. The lubricant vane pump according to the invention is provided with a non-circular stator ring which is provided with an isovolumetric contour in the intermediate sector. The lubricant-air mixture rotating in the pumping chamber through the intermediate sector is neither significantly decompressed nor signiRcantfy compressed so that the constant volume of the iubricant-air-mixture is maintained in the intermediate sector.
The intermediate sector angle exceeds the pumping chamber angle by an intermediate closing angle of at least 5° so that the mixture of lubricant and air has a short moment between the disconnection from the inlet sector and connection to the outlet sector to still. The pumping chamber volume of the rotating pumping chamber in the intermediate sector is constant over at least the last 5° before the rotating pumping chamber is opened to the outlet sector. Since the lubricant-air mass in the pumping chamber can still before being connected to the outlet sector, the volumetric pulsation of the lubricant-air mass is reduced significantly before the mass is opened to the outlet sector. With this measure, the pressure peaks in the opening phase and the hydraulic noise caused by the pressure peaks can be reduced significantly without deteriorating the efficiency of the pump,
Preferably, the intermediate closing angle is between 7° and 30° so that the pumping chamber volume is constant over the same angle, The isovolumetric dosing angle of the intermediate sector depends on many given conditions, and in particular depends on the maximum rotational speed, the necessary lubricant delivery pressure, the temperature range etc. The larger of the intermediate dosing angle is the more time is provided for the iubncant-air mass to still before it is connected to the outlet sector.
Preferably, the circular rotor hub holding the vanes and the isovolumetric intermediate section of the stator ring both have a constant radius which refer to the same center axis.
According to a preferred embodiment the stator ring is shiftable between a high pumping volume position and a low pumping volume position . Automotive lubricant vane pumps for internal combustion engines are normally directly connected with and driven by the internal combustion engine. As a consequence, the range of the rotational speed of the pump can vary with a factor of 10 or even more. Four allowing an adaption of the pumping performance and delivery pressure of the vane pump to the lubricant pressure demand, the pumping volume of the vane pump can be adapted by radially shifting the stator ring so that the pumping chamber displacement per rotation can be adapted .
According to a preferred embodiment a throttle means is provided which connects the outlet sector with the isovolumetric intermediate sector. The intermediate sector is - seen in direction of the rotor rotation - arranged after the inlet sector and before the outlet sector. When a rotating pumping chamber is positioned between the inlet sector and the outlet sector no direct and unresisted fluidlc connection of the pumping chamber to the outlet opening or the inlet opening exists. But the pumping chamber is in fluidlc connection with the outlet section by the throttle means to smoothly approximate the pressure in the rotating pumping chamber to the delivery pressure in the pump delivery section.
The dosed pumping chamber situated in the intermediate sector is only connected to the outlet section by the throttle means as long as the pumping chamber is not arrived at and directly connected to the inlet opening. The throttle means is only working over the last degrees of the intermediate sector. The throttle means does not change its throttle characteristics during the movement of the closed pumping chamber through the intermediate sector. The throttle means allows a throttled and smooth adaption of the lubricant pressure in the intermediate sector to the lubricant pressure in the outlet sector. Preferably, the throttle means is dimensioned so as to reduce the maximum possible pressure difference at the maximum possible rotational pump speed at least by 1/3, preferably by 1/2. Generally, the throttle means can be realized as a precisely calibrated clearance which allows a defined lubricant flow from the outlet section to the intermediate section. Preferably, the throttle means is realized as a channel in the stator ring body or in a stator side wail of the pump. The throttle channel can be realized as a small and circular orientated channel slot in the stator ring.
One embodiment of the invention is described with reference to the enclosed drawings, wherein :
Figure 1 shows a perspective view of the lubricant vane pump whereby one side wall cover is removed, and
figure 2 shows an enlarged details of the lubricant vane pump of figure 1.
In the figures, a mechanical variable lubricant vane pump 10 is shown which can be directly driven by an internal combustion engine (not shown). The vane pump 10 pumps a lubricant to the combustion engine with a delivery pressure. The pump 10 is provided with a housing 11 consisting of a main body 16 and two side walls 17 enclosing a pump cavity of the pump 10.. In the figures, only the bottom side wall 17 is shown whereas the top side wall Is removed. Inside, the pump 10 Is provided with a shiftabie stator ring 12 and a pump rotor 14 with seven slidabie vanes 18. The pump rotor 14 is provided with a driven rotor hub 20 which Is provided with vane slits wherein the vanes 18 are arranged radially shiftabie. In the center of the rotor hub 20 a support ring 22 is provided which supports the radially inward ends of the vanes 18. The rotor 14 rotates around a static rotor axis 24 in anti-clockwise direction.
The stator ring 12 is shiftabie in one radial direction between a low pumping volume position and a high pumping volume position which is shown in figure 1. The geometrical center of the stator ring 12 is thereby shiftabie between a high pumping volume center 26 and a iow pumping volume center 24. The low pumping volume center 24 is more or less identical with the static rotor axis 24,
The shiftabie pump stator ring 12 is provided with a stator ring body 13 with an inlet opening 30 at one side and an outlet opening 28 at the opposite side of the stator ring body 13, The pump housing 11 encloses an inlet sector A which is provided with the inlet opening 30, an outlet sector C which Is provided with the outlet opening 28 and an intermediate sector B between the inlet sector A and the outlet sector C, The stator ring 12, the two stator sidewails 17 and the rotor 14 define and enclose seven rotating pumping chambers 19p -19¾ with a pumping chamber angle a of about 51 °. Each pumping chamber 19 continuously rotates from the inlet sector A over the intermediate sector B to the outlet sector C and back to the inlet sector A.
The inner circumferentiaf surface of the pump stator ring 12 is not strictly circular and is provided with an isovolumetric contour 38 in the intermediate sector B. The isovolumetric contour 38 starts - seen in direction of rotation - where the inlet sector A ends and continues over an intermediate sector angle of about 80°, so that the intermediate closing angle γ is about 29°, As long as the leading vane 18 of the respective pumping chamber 190 is within the intermediate closing angle γ, the pumping chamber 19o rotating through the intermediate sector B is separated from the inlet sector A and the outlet sector B,
The stator ring 12 in the isovolumetric intermediate sector B is formed in such a way that the volume of the rotating pumping chamber 19o remains constant over the closing angle γ. Since the pressure conditions are the most dramatic when the s'h if table stator ring 12 is in its high pumping volume position as shown in figure 1, the isovolumetric contour 38 is optimized for the high pumping volume position of the shiftable stator ring 12.
The outlet sector C is always in f!uidic connection with the rotating pumping chamber 19Q in the intermediate sector B by a throttle means 40, The throttle means 40 is realized as a channel 41 in the stator ring body 13, The throttle means 40 allows a pressure adaption of the iubricant-air mass in the rotating pumping chamber 19o before the rotating pumping chamber 190 arrives at the outlet sector Cr so that the pressure in the rotating pumping chamber 190 is significantly increased and adapted to the lubricant pressure in the outlet sector C,

Claims

Lubricant vane pump (10) with
a pump rotor (14) Including at least three slid'able vanes (18), a circumferential stator ring (12) and two stator side walls (17) being arranged rectangular to the stator ring (12), whereby the rotor vanes (18), the stator ring (12) and the stator side walls (17) define rotating pumping chambers ( 19) with a pumping chamber angle (a),
whereby the stator ring (12) and the stator side wails (17) enclose a pump cavity which is separated into an inlet sector (A) with an inlet opening (30), an outlet sector (C) with an outlet opening (28) and an intermediate sector (B) between the inlet sector (A) and the outlet sector (C),
whereby the pumping chamber (19Q) running through the intermediate sector (B) is substantially closed and the intermediate sector angle (β) exceeds the pumping chamber angle (a) by an intermediate closing angle (γ) of at least 5°, and
whereby the stator ring (12) is provided with an intermediate isovofumetric contour (38), so that the pumping chamber volume is constant over the intermediate closing angle (γ) of the intermediate sector (B).
Lubricant vane pump ( 10) of claim 1, whereby the intermediate isovoiumetric contour (38) is provided so that the pumping chamber volume in the intermediate sector (B) is constant over 7° to 30°. Lubricant vane pump (10) of one of the preceding claims, whereby the stator ring (12) is radially shiftabje between a high pumping volume position and a low pumping volume position.
Lubricant vane pump (10) of claim 3, whereby the intermediate isovolumetric contour (38) is provided isovolumetric with respect to the high pumping volume position of the stator ring ( 12).
Lubricant vane pump (10) of one of the preceding .claims,- whereby a fluidic throttle means (40) is provided connecting the outlet sector (C) and the pumping chamber (1.9o) in the isovolumetric sector (B).
Lubricant vane pump (10) of one of the preceding claims, whereby the throttle means (40) is a channel (41) in a side wall (17) or in the stator ring body (28).
EP11754860.2A 2011-08-30 2011-08-30 Lubricant vane pump Not-in-force EP2751393B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2011/064916 WO2013029662A1 (en) 2011-08-30 2011-08-30 Lubricant vane pump

Publications (2)

Publication Number Publication Date
EP2751393A1 true EP2751393A1 (en) 2014-07-09
EP2751393B1 EP2751393B1 (en) 2021-02-24

Family

ID=44587816

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11754860.2A Not-in-force EP2751393B1 (en) 2011-08-30 2011-08-30 Lubricant vane pump

Country Status (2)

Country Link
EP (1) EP2751393B1 (en)
WO (1) WO2013029662A1 (en)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2827857A (en) * 1950-06-07 1958-03-25 Theodore F Eserkaln Rotary pump
US2924178A (en) * 1955-01-28 1960-02-09 John X Hogan Fluid proportioning pump
CA2103539C (en) * 1992-12-28 2003-12-02 James Jay Davis Vane pump
GB9721816D0 (en) * 1997-10-16 1997-12-17 Kit Systems Limited Motors and pumps
GB2389875A (en) * 2002-06-21 2003-12-24 Boc Group Plc Vane pump with a non-circular bore
DE102006033337A1 (en) * 2006-07-19 2008-01-24 Zf Lenksysteme Gmbh Displacement pump used as a vane pump comprises a compression chamber with outlet openings and a valve for opening and closing the outlet openings
DE102007033194A1 (en) * 2007-07-17 2009-01-22 Zf Lenksysteme Gmbh Displacement pump for use with variable displacement volume, has rotor enclosed by adjusting ring, where internal contour of adjusting ring is designed to modify volume of two suction zones or two pressure zones
EP2351934A1 (en) * 2010-01-11 2011-08-03 Pierburg Pump Technology GmbH Variable-displacement lubricant pump

Also Published As

Publication number Publication date
WO2013029662A1 (en) 2013-03-07
EP2751393B1 (en) 2021-02-24

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