WO2003069127A1 - Variable-delivery central-vane rotary pump, particularly for oil - Google Patents

Variable-delivery central-vane rotary pump, particularly for oil Download PDF

Info

Publication number
WO2003069127A1
WO2003069127A1 PCT/IT2003/000076 IT0300076W WO03069127A1 WO 2003069127 A1 WO2003069127 A1 WO 2003069127A1 IT 0300076 W IT0300076 W IT 0300076W WO 03069127 A1 WO03069127 A1 WO 03069127A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
rotary pump
vanes
vane
shaft
Prior art date
Application number
PCT/IT2003/000076
Other languages
French (fr)
Other versions
WO2003069127A8 (en
Inventor
Carlo Pachetti
Giacomo Armenio
Daniele Righetti
Original Assignee
Pierburg 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 Pierburg S.P.A. filed Critical Pierburg S.P.A.
Priority to AU2003209707A priority Critical patent/AU2003209707A1/en
Priority to DE60308662T priority patent/DE60308662T2/en
Priority to EP03739640A priority patent/EP1485576B1/en
Publication of WO2003069127A1 publication Critical patent/WO2003069127A1/en
Publication of WO2003069127A8 publication Critical patent/WO2003069127A8/en

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
    • F04C14/226—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 by pivoting the cam around an eccentric axis
    • 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
    • F04C2/352—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 vanes being pivoted on the axis of the outer member

Definitions

  • the present invention relates to a variable-delivery vane pump.
  • the present invention relates to a rotary vane pump of the type comprising a casing; an adjustable stator; and a rotation unit in turn comprising a rotor and a number of vanes .
  • variable-delivery vane pump as claimed in Claim 1.
  • Figure 1 shows a cross section of a variable- delivery vane pump in accordance with the present invention
  • Figure 2 shows a first longitudinal section A-A of the Figure 1 cross section
  • Figure 3 shows a second longitudinal section B-B of the Figure 1 cross section.
  • Rotary pump 10 comprises a casing 11, in which is defined a cavity 12 having a substantially semicircular- section portion 12a and a supporting surface 12b for the reasons explained in detail later on.
  • Cavity 12 also comprises a seat 12c for housing a spring device 13 used as described later on.
  • Cavity 12 also houses an adjustable oscillating stator 14 having a substantially annular section.
  • stator 14 comprises a substantially semicircular-section portion 14a, which mates perfectly with portion 12a of cavity 12 to allow stator 14 to rotate about an axis perpendicular to the Figure 1 plane and through a center Cl.
  • Stator 14 also comprises a first shoulder 14b, which rests on supporting surface 12b in cavity 12, and a second shoulder 14c resting on spring device 13.
  • a circular cavity 15 housing a rotor 16 is defined inside stator 14.
  • the outer surface 16a of rotor 16 and surface 15a of circular cavity 15 define a pumping space 17.
  • rotor 16 is rotated by a drive shaft 18 driven by drive means not shown, and which rotates about an axis 19 (center C2 in Figure 1) .
  • rotor 16 comprises a number of - in the embodiment shown, five - radial openings 16b.
  • a respective vane 20 extends radially from a shaft 21 of axis 22 (center C3 in Figure 1) . And, since shaft 21 is integral with stator 14 , center C3 is also the center of stator 14.
  • Rotor 16 has an inner cavity 16c at least partly housing vanes 20 and shaft 21 to which vanes 20 are hinged. As will be seen, cavity 16c permits movement of shaft 21 to vary eccentricity (EC) (see below) alongside a variation in delivery pressure.
  • EC eccentricity
  • one end of shaft 21 is housed inside a cavity 14d in stator 14, and is fixed to stator 14 by conventional means not shown.
  • each vane 20 has an enlargement 20a for preventing the oil under pressure from flowing through radial opening 16b into cavity 16c, and which simply slides with respect to the walls of corresponding radial opening 16b.
  • Enlargement 20a is so shaped as to ensure rotor 16 rotates vane 20 over the full eccentricity (EC) range.
  • each vane 20 is hinged "bannerfashion" to shaft 21, and is free to rotate with respect to shaft 21 and, therefore, to axis 22 (center C3 in Figure 1) .
  • Pumping space 17 is divided into five pumping pockets 23, each defined by two adjacent vanes 20.
  • Figure 1 shows a suction opening 24 and a delivery opening 25.
  • axis 19 of rotor 16 (center C2 in Figure 1) and axis 22 of stator 14 and shaft 21 (center C3 in Figure 1) are offset by eccentricity EC, which, when increased or decreased by known means by moving stator 14 and shaft 21 integral with it, increases or decreases the delivery of pump 10 respectively.
  • a chamber 26 ( Figure 1) is provided between casing 11 and stator 14, and into which part of the oil delivery, i.e. from delivery opening 25, is fed.
  • chamber 26 contains a certain amount of fluid, in particular oil, of the same pressure as the oil from delivery opening 25.
  • Figures 2 and 3 also show a cover 27 for closing most of the members described above inside casing 11.
  • rotary pump 10 supplies a delivery ranging between zero (when centers C2 and C3 coincide) , and a maximum value when rotor 16 almost rests on surface 15a. Oil delivery is obviously maximum when the eccentricity (EC) of stator 14 with respect to rotor 16 is maximum.
  • variable-delivery rotary vane pump substantially lie in eliminating wear of the vane tips, by eliminating any slide between the vanes and the inner surface of the stator, even at high rotor speed. As a result, leakage between adjacent pumping pockets is practically negligible, thus ensuring acceptable efficiency of the pump.
  • the oscillating stator 14 has a circular surface portion 14a which mates perfectly with a corresponding portion 12a of inner cavity 12 of casing 11, with no need for intermediate members, such as pins or articulated joints, so that stator 14 is easier to fit to casing 11.

Abstract

A variable-delivery rotary vane pump (10), particularly for oil, wherein the vanes (20) are hinged to a shaft (21) integral with an adjustable stator (14); and each vane (20) is inserted inside a respective radial opening (16b) in a rotor (16), so that rotation of the rotor (16) rotates the vane (20).

Description

VARIABLE-DELIVERY CENTRAL-VANE ROTARY PUMP, PARTICULARLY FOR OIL
TECHNICAL FIELD
The present invention relates to a variable-delivery vane pump.
More specifically, the present invention relates to a rotary vane pump of the type comprising a casing; an adjustable stator; and a rotation unit in turn comprising a rotor and a number of vanes . BACKGROUND ART
One of the drawbacks typically associated with this type of pump lies in the vanes, which, as they rotate, are subjected to centrifugal force, which alone ensures contact between the vane tip and stator, and therefore sealing between the various pump pockets .
As a result, at low rotation speed, at which the centrifugal force is also low, considerable oil leakage occurs between adjacent pockets, thus impairing volumetric efficiency and, consequently, delivery.
Conversely, the strong centrifugal force produced at high rotation speed results in considerable contact pressure between the vane tip and stator, thus resulting in severe wear of the stator and vanes .
DISCLOSURE OF INVENTION
It is an object of the. present invention to provide a variable-delivery vane pump designed to eliminate the aforementioned drawbacks .
According to the present invention, there is provided a variable-delivery vane pump as claimed in Claim 1. BRIEF DESCRIPTION OF THE DRAWINGS
A non-limiting embodiment of the present invention will be described by way of example with reference to the accompanying drawings, in which:
Figure 1 shows a cross section of a variable- delivery vane pump in accordance with the present invention;
Figure 2 shows a first longitudinal section A-A of the Figure 1 cross section;
Figure 3 shows a second longitudinal section B-B of the Figure 1 cross section.
BEST MODE FOR CARRYING OUT THE INVENTION
Number 10 in the accompanying drawings indicates a rotary pump in accordance with the present invention.
Rotary pump 10 comprises a casing 11, in which is defined a cavity 12 having a substantially semicircular- section portion 12a and a supporting surface 12b for the reasons explained in detail later on.
Cavity 12 also comprises a seat 12c for housing a spring device 13 used as described later on.
Cavity 12 also houses an adjustable oscillating stator 14 having a substantially annular section.
More specifically, stator 14 comprises a substantially semicircular-section portion 14a, which mates perfectly with portion 12a of cavity 12 to allow stator 14 to rotate about an axis perpendicular to the Figure 1 plane and through a center Cl. Stator 14 also comprises a first shoulder 14b, which rests on supporting surface 12b in cavity 12, and a second shoulder 14c resting on spring device 13.
A circular cavity 15 housing a rotor 16 is defined inside stator 14.
The outer surface 16a of rotor 16 and surface 15a of circular cavity 15 define a pumping space 17.
As shown in Figures 2 and 3, rotor 16 is rotated by a drive shaft 18 driven by drive means not shown, and which rotates about an axis 19 (center C2 in Figure 1) .
As shown in more detail in Figure 1, rotor 16 comprises a number of - in the embodiment shown, five - radial openings 16b.
Through each radial opening 16b, a respective vane 20 extends radially from a shaft 21 of axis 22 (center C3 in Figure 1) . And, since shaft 21 is integral with stator 14 , center C3 is also the center of stator 14.
Rotor 16 has an inner cavity 16c at least partly housing vanes 20 and shaft 21 to which vanes 20 are hinged. As will be seen, cavity 16c permits movement of shaft 21 to vary eccentricity (EC) (see below) alongside a variation in delivery pressure.
More specifically, as shown in Figures 2 and 3 , one end of shaft 21 is housed inside a cavity 14d in stator 14, and is fixed to stator 14 by conventional means not shown.
At respective radial opening 16b in rotor 16, each vane 20 has an enlargement 20a for preventing the oil under pressure from flowing through radial opening 16b into cavity 16c, and which simply slides with respect to the walls of corresponding radial opening 16b.
Enlargement 20a is so shaped as to ensure rotor 16 rotates vane 20 over the full eccentricity (EC) range.
Between the ends of vanes 20 and surface 15a of cavity 15 housing rotor 16, a clearance is provided to prevent even accidental sliding between the two surfaces during rotation of rotor 16, which, as stated, also rotates vanes 20. Clearance selection, in fact, is critical, in that, besides preventing even accidental sliding between the ends of vanes 20 and surface 15a, it must also minimize leakage between adjacent pumping pockets 23, which, as stated, is responsible for greatly reducing the overall efficiency of pump 10.
As shown in Figures 2 and 3, each vane 20 is hinged "bannerfashion" to shaft 21, and is free to rotate with respect to shaft 21 and, therefore, to axis 22 (center C3 in Figure 1) .
Pumping space 17 is divided into five pumping pockets 23, each defined by two adjacent vanes 20.
Pumping action is performed by drive shaft 18, which rotates rotor 16, which in turn rotates vanes 20 inserted inside radial openings 16b. Rotation of vanes 20 with respect to shaft 21, fixed to and integral with stator 14, is obviously permitted by vanes 20, as stated, being hinged "bannerfashion" to shaft 21. As shown in Figures 2 and 3, the hinges of vanes 20 are intercalated to occupy the whole usable longitudinal portion of shaft 21.
Figure 1 shows a suction opening 24 and a delivery opening 25.
As shown in Figure 2, axis 19 of rotor 16 (center C2 in Figure 1) and axis 22 of stator 14 and shaft 21 (center C3 in Figure 1) are offset by eccentricity EC, which, when increased or decreased by known means by moving stator 14 and shaft 21 integral with it, increases or decreases the delivery of pump 10 respectively.
A chamber 26 (Figure 1) is provided between casing 11 and stator 14, and into which part of the oil delivery, i.e. from delivery opening 25, is fed.
In other words, chamber 26 contains a certain amount of fluid, in particular oil, of the same pressure as the oil from delivery opening 25. Figures 2 and 3 also show a cover 27 for closing most of the members described above inside casing 11.
In actual use, by varying the distance between center C3 and center C2 (which is fixed) , by the user moving stator 14 and integral shaft 21 using known means, rotary pump 10 supplies a delivery ranging between zero (when centers C2 and C3 coincide) , and a maximum value when rotor 16 almost rests on surface 15a. Oil delivery is obviously maximum when the eccentricity (EC) of stator 14 with respect to rotor 16 is maximum.
Once the desired oil delivery is established at low speed of the motor (not shown) , an increase in the speed of the motor increases delivery and pressure in known manner, and therefore also the pressure in chamber 26.
The increase in pressure in chamber 26 produces a force which pushes shoulder 14c onto spring device 13, thus reducing eccentricity (EC) (the distance between C2 and C3) and retroactively reducing oil delivery.
As such, no pumping action is wasted on surplus oil which would have to be bypassed later, thus greatly improving efficiency.
The advantages of the variable-delivery rotary vane pump according to the present invention substantially lie in eliminating wear of the vane tips, by eliminating any slide between the vanes and the inner surface of the stator, even at high rotor speed. As a result, leakage between adjacent pumping pockets is practically negligible, thus ensuring acceptable efficiency of the pump.
Moreover, the oscillating stator 14 has a circular surface portion 14a which mates perfectly with a corresponding portion 12a of inner cavity 12 of casing 11, with no need for intermediate members, such as pins or articulated joints, so that stator 14 is easier to fit to casing 11.

Claims

1) A variable-delivery rotary pump (10) with central vanes (20) , comprising a casing (11) housing an adjustable stator (14) , a rotor (16) , and a number of vanes (20) rotated by said rotor (16) and defining a corresponding number of pumping pockets (23) ; the rotary pump (10) being characterized in that said number of vanes (20) are hinged to a shaft (21) integral with said adjustable stator (14) ,- each vane (20) being inserted inside a respective radial opening (16b) in said rotor (16) , so that rotation of said rotor (16) rotates said vane (20) ..
2) A rotary pump (10) as claimed in Claim 1, wherein said rotor (16) comprises a cavity (16c) at least partly housing the vanes (20) and said shaft (21) ,• said cavity (16c) permitting movement of said shaft (21) to vary eccentricity (EC) alongside a variation in delivery pressure. 3) A rotary pump (10) as claimed in Claim 1, wherein the hinges of said vanes (20) are fixed to said shaft (21) and intercalated with one another.
4) A rotary pump (10) as claimed in any one of the foregoing Claims, wherein, between the ends of said vanes (20) and the surface (15a) of a further cavity (15) housing said rotor (16) , a clearance is provided to prevent sliding between the two surfaces during rotation of said rotor (16) ; leakage between each pumping pocket (23) and those adjacent to it also being minimized at the same time.
5) A rotary pump (10) as claimed in any one of Claims 2 to 4, wherein, at the respective radial opening (16b) in said rotor (16) , each vane (20) comprises an enlargement (20a) shaped to prevent the oil in pressure in said radial opening (16b) from flowing into said cavity (16c) over the whole eccentricity (EC) range.
6) A rotary pump (10) as claimed in Claim 1, wherein the shaft (21), to which the vanes (20) are hinged, is fixed to the adjustable stator (14) and therefore movable with it during automatic adjustment of eccentricity (EC) by the delivery pressure.
7) A rotary pump (10) as claimed in any one of the foregoing Claims, wherein the adjustable stator (14) comprises a circular surface portion (14a) which mates perfectly with a corresponding portion (12a) of an inner cavity (12) of the casing (11) with no need for intermediate members, such as pins or articulated joints. 8) A rotary pump (10) as claimed in any one of the foregoing Claims, wherein, at the respective radial opening (16b) in said rotor (16) , each vane (20) comprises an enlargement (20a) shaped to ensure rotation of said vane (20) by said rotor (16) over the whole eccentricity (EC) range.
PCT/IT2003/000076 2002-02-15 2003-02-14 Variable-delivery central-vane rotary pump, particularly for oil WO2003069127A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU2003209707A AU2003209707A1 (en) 2002-02-15 2003-02-14 Variable-delivery central-vane rotary pump, particularly for oil
DE60308662T DE60308662T2 (en) 2002-02-15 2003-02-14 Rotary vane pump with variable capacity
EP03739640A EP1485576B1 (en) 2002-02-15 2003-02-14 Variable-delivery central-vane rotary pump, particularly for oil

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITBO2002A000076 2002-02-15
IT2002BO000076A ITBO20020076A1 (en) 2002-02-15 2002-02-15 VARIABLE FLOW CENTRAL ROTARY PUMP, ESPECIALLY FOR OIL

Publications (2)

Publication Number Publication Date
WO2003069127A1 true WO2003069127A1 (en) 2003-08-21
WO2003069127A8 WO2003069127A8 (en) 2004-04-08

Family

ID=11439907

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IT2003/000076 WO2003069127A1 (en) 2002-02-15 2003-02-14 Variable-delivery central-vane rotary pump, particularly for oil

Country Status (5)

Country Link
EP (1) EP1485576B1 (en)
AU (1) AU2003209707A1 (en)
DE (1) DE60308662T2 (en)
IT (1) ITBO20020076A1 (en)
WO (1) WO2003069127A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007012096A2 (en) 2005-07-29 2007-02-01 Miba Sinter Holding Gmbh & Co Kg Vane-cell pump
GB2470012A (en) * 2009-05-05 2010-11-10 Gm Global Tech Operations Inc Pivoting seat for variable displacement cam ring pressure balance spring

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3807912A (en) * 1972-09-25 1974-04-30 Keller Corp Fluid flow device having high degree of flexibility
US4437819A (en) * 1981-06-06 1984-03-20 Zahnradfabrik Friedrichshafen, Ag Controllable vane pump
US4678413A (en) * 1986-01-22 1987-07-07 Edward Ries Variable displacement vane pump or motor
WO1991015661A2 (en) * 1990-04-11 1991-10-17 Epifanio Leanza Variable-volume rotating fluid-dynamic machine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3807912A (en) * 1972-09-25 1974-04-30 Keller Corp Fluid flow device having high degree of flexibility
US4437819A (en) * 1981-06-06 1984-03-20 Zahnradfabrik Friedrichshafen, Ag Controllable vane pump
US4678413A (en) * 1986-01-22 1987-07-07 Edward Ries Variable displacement vane pump or motor
WO1991015661A2 (en) * 1990-04-11 1991-10-17 Epifanio Leanza Variable-volume rotating fluid-dynamic machine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007012096A2 (en) 2005-07-29 2007-02-01 Miba Sinter Holding Gmbh & Co Kg Vane-cell pump
US8545199B2 (en) 2005-07-29 2013-10-01 Miba Sinter Holding Gmbh & Co Kg Regulatable vane-cell pump with a sealing web curving in an arc
GB2470012A (en) * 2009-05-05 2010-11-10 Gm Global Tech Operations Inc Pivoting seat for variable displacement cam ring pressure balance spring
US8602749B2 (en) 2009-05-05 2013-12-10 GM Global Technology Operations LLC Variable displacement vane pump
GB2470012B (en) * 2009-05-05 2016-04-27 Gm Global Tech Operations Llc Variable Displacement Vane Pump

Also Published As

Publication number Publication date
DE60308662T2 (en) 2007-08-23
AU2003209707A1 (en) 2003-09-04
DE60308662D1 (en) 2006-11-09
EP1485576A1 (en) 2004-12-15
WO2003069127A8 (en) 2004-04-08
EP1485576B1 (en) 2006-09-27
ITBO20020076A0 (en) 2002-02-15
ITBO20020076A1 (en) 2003-08-18

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