EP1794457B1 - Vane cell pump - Google Patents

Vane cell pump Download PDF

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Publication number
EP1794457B1
EP1794457B1 EP06776763A EP06776763A EP1794457B1 EP 1794457 B1 EP1794457 B1 EP 1794457B1 EP 06776763 A EP06776763 A EP 06776763A EP 06776763 A EP06776763 A EP 06776763A EP 1794457 B1 EP1794457 B1 EP 1794457B1
Authority
EP
European Patent Office
Prior art keywords
stator
cell pump
vane cell
characterized
pump according
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.)
Active
Application number
EP06776763A
Other languages
German (de)
French (fr)
Other versions
EP1794457A1 (en
Inventor
Willi Schneider
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.)
Joma-Hydromechanic GmbH
Joma Hydromechanic GmbH
Original Assignee
Joma-Hydromechanic GmbH
Joma Hydromechanic 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
Priority to DE200510048602 priority Critical patent/DE102005048602B4/en
Priority to DE200610021971 priority patent/DE102006021971B4/en
Application filed by Joma-Hydromechanic GmbH, Joma Hydromechanic GmbH filed Critical Joma-Hydromechanic GmbH
Priority to PCT/EP2006/007944 priority patent/WO2007039013A1/en
Publication of EP1794457A1 publication Critical patent/EP1794457A1/en
Application granted granted Critical
Publication of EP1794457B1 publication Critical patent/EP1794457B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226Control 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

Description

  • The invention relates to a vane pump with an inner rotor and a plurality of vanes, which are mounted radially displaceable in substantially radial slots in the inner rotor and slides directly or indirectly along the inner peripheral surface of a stator, wherein the axis of the stator and the axis of the inner rotor offset to each other and the stator relative to the inner rotor in the radial direction adjustable and thereby the offset is variable, and the stator has a arranged in the housing of the vane pump pivot bearing.
  • From the DE 100 40 711 A1 is a vane pump with an annular inner rotor known, in which a plurality of radially outwardly extending wing elements are received radially displaceable. The radially inner end portions of the wing elements are supported on a non-rotatable central part, the radially outer end portions of a non-rotatable outer ring. The rotor can be rotated about a rotation axis that is offset from the central axis of the central part and the outer ring. In this way, at a rotational movement of the rotor between the wing elements initially larger and then smaller again conveying cells. Due to the change in volume of the delivery cells fluid is first sucked into the delivery cells and then ejected again. The end regions of the wing elements slide on the central part or the outer ring. Such a vane pump can be made simple and inexpensive.
  • To increase the efficiency is from the DE 195 32 703 C1 a vane machine in the form of a pendulum slide pump known. In this, the wing elements are in one Inner rotor slidably received, whereas they are pivotally held in an annular outer rotor. The axis of rotation of the inner rotor is offset with respect to the axis of rotation of the outer rotor, whereby in operation also initially magnifying and then shrinking conveyor cells are formed. The from the DE 195 32 703 C1 However, known pendulum slide pump is complex and therefore expensive to manufacture.
  • Object of the present invention is to provide a vane cell machine which has a high efficiency and at the same time can be easily and inexpensively manufactured.
  • This object is achieved by a vane machine in which the stator protrudes at least one curved piston portion whose piston axis extends in the circumferential direction of the stator to the pivot bearing.
  • In the vane pump according to the invention, a piston or piston portion is provided which serves to adjust the stator and which protrudes from the stator and whose piston axis extends in the circumferential direction to the pivot bearing. The piston movement thus runs in sections in a radius around the pivot bearing. The piston portion has a defined piston surface, which also rotates in the circumferential direction about the pivot bearing, which has the advantage that the actuating forces on the stator are proportional to the compressive forces acting on the piston surface. As a result, exact settings of the stator and thus of the volume of the vane pump to be delivered can be made which are proportional to the pressure acting on the piston section. This makes a sensitive adjustment possible.
  • In a further development it is provided that the piston section and the stator are integrally formed. In particular, the piston portion and the stator are made Plastic or aluminum. As a result, an inexpensive production of the vane pump is possible, and the assembly is simplified. In addition, both pressure and suction forces can act on the piston portion.
  • In one variant, the piston portion loosely abuts the stator. This variant has the advantage that the piston portion and the stator can be made of different materials and that they are easy to install.
  • In another variant, the piston section is attached to the stator, in particular screwed. In this variant too, the stator and the piston section can be made of different materials and pressure and suction forces can be transmitted.
  • A development of the invention provides that the stator is equipped with two piston sections. In this way, the stator, in particular when the two piston sections with respect to the axis of the stator are opposite to each other, be adjusted in the direction of maximum delivery and in the direction of minimum funding, for which control pressures on the piston sections attack.
  • As a result, a very sensitive adjustment or positioning of the stator is achieved, which is required for map control. In particular, when the two piston sections are arranged in opposite directions acting on the stator, even the smallest pressure changes in the positioning of the stator can be considered. In particular, it is not necessary to work against a spring constant, which has the disadvantage that it is necessary to work against a changing force of a spring, ie against a spring constant. It can directly the resulting pressures for displacing the stator and that in both directions, can be used.
  • With preference, the cross section of the piston is rectangular. This embodiment has the advantage that both the production of the piston and the production of the piston section receiving space in the housing can be relatively easily done by the stator receiving portion of the housing is plate-shaped, and provided the portion only with a piston portion receiving breakthrough must be, with the lateral sealing on other plates (end plates) takes place.
  • An optimal guidance of the piston and thus of the stator in the housing is achieved in that in the housing of the vane pump, a cylinder receiving the piston portion is provided. This cylinder has not only the task of forming the piston chamber for the piston section, but also the task of guiding and supporting the stator, so that the pivot bearing has only the task to absorb the forces occurring in the circumferential direction of the pivot bearing, but not in radial Direction of tensile and compressive forces.
  • In a development of the invention, it is provided that the cylinder supports the piston section at least over part of its length on the radially inner and outer running surfaces. As a result, a defined piston chamber is created, which acts on a defined piston surface. In addition, the running parallel to the pivot axis running surfaces simultaneously serve as support surfaces for perpendicular to the pivot axis acting on the stator forces. As a result, the pivot axis is relieved.
  • In a development of the invention, it is provided that an overflow channel is provided on the outer circumference of the stator, which connects an outlet channel on the one end face of the vane pump with an outlet channel on the other end side of the vane pump. This will be the Increased efficiency of the vane pump, since the pumped medium can be transported more effectively, ie loss of energy.
  • The overflow channel runs axially parallel to the axis of the stator. This has the significant advantage that the overflow can be relatively easily manufactured, and that the overflow can be relatively easily connected to the outlet channels by provided in side lids arcuate flow channels.
  • With preference, the overflow is part of the piston section. The piston portion thus has the dual function of an adjusting member for the stator to adjust this between a maximum and a minimum promotion, and also connects the two outlet channels, which open on the two end faces of the interior of the stator.
  • With preference, an overflow channel is provided between the stator and the machine housing, which connects the inlet channel on one end face of the vane pump with the inlet channel on the other end face of the vane pump. This overflow channel is formed by the space required for the displacement of the stator in the housing.
  • The overflow channels for both the inlet channel and the outlet channel offer the advantage that the vane pump can be flown from both end sides, whereby an optimal filling of the working spaces is made possible. In addition, the pumped medium can flow off quickly and without loss, since it can leave the working space via both end faces.
  • A particularly preferred embodiment of the invention provides that protrudes from the stator, a support member for a printing element. This support element is in particular one piece on Stator provided and serves to receive the force of a compression spring, in particular a coil spring. But it is also conceivable that the pressure element is a leaf spring, a leg spring or a pneumatic cushion. This pressure element, which is biased in particular, has the task of adjusting the stator in the direction of the maximum delivery of the pump. This is necessary if in a fault, the pneumatic or hydraulic control fails over the piston sections. The control by means of the pressure element ensures that the vane pump continues to operate at its maximum power in order to supply the connected system with the medium to be conveyed.
  • Further advantages, features and details of the invention will become apparent from the following description in which two particularly preferred embodiments are described in detail with reference to the drawing. In this case, the features shown in the drawing and mentioned in the claims and in the description may each be individually invention itself or in any combination invention.
  • In the drawing show:
  • FIG. 1
    a cross section through a first embodiment of the vane pump according to the invention;
    FIG. 2
    a perspective view of the stator with inserted rotor, partially cut away;
    FIG. 3
    a cross section through a second embodiment of the vane pump according to the invention, showing the position of the inner rotor at maximum promotion;
    FIG. 4
    a cross section according to FIG. 3 showing the position of the inner rotor at minimum conveyance; and
    FIG. 5
    a perspective view of the vane pump according to FIG. 3 ,
  • For a better understanding of the invention is based on the DE 10 2005 048 602 Reference is made, the content of which is hereby introduced.
  • The FIG. 1 schematically shows a housing 10 of a generally designated 12 vane pump, in which a drive shaft 14 is mounted. This drive shaft 14 drives an inner rotor 16, which has a plurality of radial slots 18, in which wings 20 are mounted radially displaceable. These wings 20 have a thickened end 22 to which sliding blocks 24 are pivotally mounted. The sliding shoes 24 abut against the inner circumferential surface 26 of a stator 28, resulting in FIG. 2 is apparent. In this case, the inner rotor 16, two wings 20, two sliding shoes 24 and the stator 28 each have a working space 30. The working space 30 increases and decreases in rotating inner rotor 16, whereby a fluid is conveyed.
  • Moreover, in the FIGS. 1 and 2 recognizable that the stator 28 has a bearing eye 32 which surrounds a pin 34 and a housing-fixed pivot bearing 36 forms. The stator 28 can therefore be pivoted in the direction of the double arrow 38 within the housing 10 about the pivot bearing 36. For this purpose, the stator 28 has two piston sections 40 and 42, which protrude from the outer periphery of the stator 28 and the piston axes 44 extend in the circumferential direction about the pivot bearing 36, that is concentric to this. The piston sections 40 and 42 are each guided in a cylinder 46, which in the housing 10 of the vane pump 12th is provided. The axis of the cylinder 46 also extends concentrically about the pivot bearing 36. The cylinder 46 abuts over a portion of the length of the piston portions 40 and 42 at the radially inner and outer raceway surfaces of the piston portions 40 and 42. The piston portions 40 and 42 each have a piston surface 48, which are acted upon by a pressure and exert a pivoting force about the pivot bearing 36 on the stator 28.
  • From the FIGS. 1 and 2 is clearly visible that the stator 28 is formed with its piston portions 40 and 42 substantially disc or plate-shaped, so that the piston portions 40 and 42 have rectangular cross-sections. The sealing of the pressure chambers 50 and 52 takes place in each case via disc-shaped or plate-shaped elements which are placed on the end faces 54 and 56 of the stator 28. As a result, the work spaces 30 are closed at the front.
  • Out FIG. 2 can still be seen that from the stator 28, a support member 58 protrudes, which has a centering nose for a pressure element 62, for example a spiral spring 64. The pressure element 62 exerts a force on the stator 28, which causes a pivoting of the stator 28 about the pivot bearing 36 in the clockwise direction. In this way, the stator 28 is permanently urged in the direction of maximum delivery, so that the vane pump 12 assumes its position for the maximum promotion in case of failure.
  • In the Figures 3 and 5 showing a second embodiment of the vane pump 12 according to the invention, the stator 28 is shown in the maximum funding. The FIG. 4 shows the minimum promotion, in which the axis 66 of the stator 28 has almost no offset 70 to the axis 68 of the inner rotor 16. This offset 70, or the eccentricity of the inner rotor 16, determines the delivery volume of the vane pump 12.
  • In the FIGS. 3 to 5 is still recognizable that on the piston portion 40, an extension 72 is provided which has a substantially triangular cross-section. This extension 72 has an overflow channel 74, which is clearly in FIG. 5 is shown, and connects the two end faces 54 and 56 with each other. In this way, the outlet channels, not shown in the drawing, which are provided in the front side mounted cover plates and in which the conveyed medium flows out of the working spaces 30, are connected to each other, so that the working spaces 30 can be emptied through both end faces 54 and 56.
  • Moreover, in the FIGS. 4 and 5 recognizable that between the stator 28 and the housing 10, an overflow channel 76 is provided which surrounds the stator 28 and connects the provided on both end faces 54 and 56 inlet channels together. In this way, the working spaces 30 can be filled from both end faces 54 and 56.
  • The two transfer ports 74 and 76 thus serve to increase the efficiency of the vane pump 12 by the working spaces 30 can be filled and emptied more effectively. Losses are thereby reduced.
  • Of the FIG. 5 can be found that the housing 10 of the vane pump 12 is formed substantially disc-shaped or plate-shaped, in which the receiving space for the stator 28 and the cylinder 46 are incorporated as openings. The frontal sealing is done by placing one plate at a time. The production of such components is relatively simple and the assembly can be done by machine.

Claims (17)

  1. A vane cell pump (12) with an inner rotor (16) and a plurality of vanes (20), which are essentially mounted radially displaceable in radial slots (18) in the inner rotor (16) and slide directly and indirectly on the internal circumferential surface (26) of a stator (28), the axis (66) of the stator (28) and the axis (68) of the inner rotor (16) being offset (70) in relation to one another, and the stator (28) being radially adjustable in relation to the inner rotor (16), and the offset (70) being consequently modifiable, and the stator (28) comprising a pivot bearing (36) arranged in the housing (10) of the vane cell pump (12), characterized in that at least one curved piston section (40 or 42) protrudes from the stator (28), whose piston axis (44) runs in the circumferential direction with respect to the pivot bearing (36).
  2. The vane cell pump according to claim 1, characterized in that the piston section (40 or 42) and the stator (28) are constructed in one piece.
  3. The vane cell pump according to claim 1, characterized in that the piston section (40 or 42) rests loosely on the stator (28).
  4. The vane cell pump according to claim 1, characterized in that the piston section (40 or 42) is attached, particularly screwed to the stator (28).
  5. The vane cell pump according to one of the preceding claims, characterized in that the stator (28) is equipped with two piston sections (40 or 42).
  6. The vane cell pump according to claim 5, characterized in that both piston sections (40 and 42) are opposite to one another in relation to the axis (66) of the stator (28).
  7. The vane cell pump according to claim 5 or 6, characterized in that both piston sections (40 and 42) act in opposite directions.
  8. The vane cell pump according to one of the preceding claims, characterized in that cross section of the piston section (40 and/or 42) has a rectangular shape.
  9. The vane cell pump according to one of the preceding claims, characterized in that a cylinder (46) is arranged in the housing (10) of the vane cell pump (12) to locate the piston section (40 or 42).
  10. The vane cell pump according to claim 9, characterized in that the cylinder (46) supports the piston section (40 or 42) at least over part of its length in an internal and an external radial tread surface.
  11. The vane cell pump according to one of the preceding claims, characterized in that on an external circumference of the stator (28) an overflow duct (74) is provided, which connects an outlet duct on one face side (54) of the vane cell pump (12) with an outlet duct on the other face side (56) of the vane cell pump (12).
  12. The vane cell pump according to claim 11, characterized in that the overflow duct (74) runs axially parallel to the axis (66) of the stator (28).
  13. The vane cell pump according to claim 11 or 12, characterized in that the overflow duct (74) is part of the piston section (40).
  14. The vane cell pump according to one of the preceding claims, characterized in that between the stator (28) and the housing (10) an overflow duct (76) is provided, which connects an inlet duct on one face side (54) of the vane cell pump (12) with an inlet duct on the other face side (56) of the vane cell pump (12).
  15. The vane cell pump according to one of the preceding claims, characterized in that a supporting element (58) for a compression element (62) protrudes from the stator (28).
  16. The vane cell pump according to claim 15, characterized in that the supporting element (58) and the stator (28) are constructed in one piece.
  17. The vane cell pump according to claim 15 or 16, characterized in that a compression spring, particularly a spiral coiled spring (64) meshes with the supporting element (58).
EP06776763A 2005-10-06 2006-08-11 Vane cell pump Active EP1794457B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE200510048602 DE102005048602B4 (en) 2005-10-06 2005-10-06 Vane machine, in particular vane pump
DE200610021971 DE102006021971B4 (en) 2005-10-06 2006-05-03 Vane pump
PCT/EP2006/007944 WO2007039013A1 (en) 2005-10-06 2006-08-11 Vane cell pump

Publications (2)

Publication Number Publication Date
EP1794457A1 EP1794457A1 (en) 2007-06-13
EP1794457B1 true EP1794457B1 (en) 2009-07-08

Family

ID=37271120

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06776763A Active EP1794457B1 (en) 2005-10-06 2006-08-11 Vane cell pump

Country Status (6)

Country Link
US (1) US7785087B2 (en)
EP (1) EP1794457B1 (en)
JP (1) JP4834734B2 (en)
KR (1) KR101146845B1 (en)
DE (1) DE502006004164D1 (en)
WO (1) WO2007039013A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013221567A1 (en) * 2013-10-23 2015-04-23 Mahle International Gmbh Pendulum slide cell pump for pumping a fluid

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202005021925U1 (en) * 2004-12-22 2011-08-11 Magna Powertrain Inc. Vane pump
US9181803B2 (en) 2004-12-22 2015-11-10 Magna Powertrain Inc. Vane pump with multiple control chambers
DE502006004164D1 (en) 2005-10-06 2009-08-20 Joma Hydromechanic Gmbh Vane pump
DE502006002760D1 (en) * 2005-10-06 2009-03-19 Joma Hydromechanic Gmbh Vane pump
US7736134B2 (en) * 2006-10-10 2010-06-15 Joma-Polytec Kunststofftechnik Gmbh Vane machine, in particular vane pump
WO2008124174A1 (en) * 2007-04-10 2008-10-16 Borgwarner Inc. Variable displacement dual vane pump
EP3159575B1 (en) 2014-06-20 2018-06-27 Bando Chemical Industries, Ltd. Transmission belt and belt transmission device equipped with same
US10119540B2 (en) * 2015-12-08 2018-11-06 Ford Global Technologies, Llc Variable displacement vane pump

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2250947A (en) 1938-06-17 1941-07-29 Jr Albert Guy Carpenter Pump
DE1403748C3 (en) 1961-10-13 1974-08-29 Breinlich, Richard, Dr., 7120 Bietigheim
GB1310358A (en) * 1969-07-21 1973-03-21 Hobourn Eaton Mfg Co Ltd Rotary pumps
JPS5762986A (en) * 1980-10-02 1982-04-16 Nissan Motor Co Ltd Variable displacement type vane pump
US4362044A (en) * 1980-10-14 1982-12-07 Tubeco, Inc. Pipe-bending die and method
JPH0310038B2 (en) * 1983-02-14 1991-02-12 Toyoda Machine Works Ltd
DE19504220A1 (en) 1995-02-09 1996-08-14 Bosch Gmbh Robert Adjustable hydrostatic pump
DE19532703C1 (en) * 1995-09-05 1996-11-21 Guenther Beez Pump or hydraulic motor with inner and outer rotors
DE19533686C2 (en) * 1995-09-12 1997-06-19 Daimler Benz Ag Adjustable vane pump as a lubricant pump
DE19631974C2 (en) 1996-08-08 2002-08-22 Bosch Gmbh Robert Vane machine
DE10029969C1 (en) 2000-06-26 2001-08-30 Joma Hydromechanic Gmbh Vane pump
DE10040711C2 (en) 2000-08-17 2003-11-06 Joma Hydromechanic Gmbh Vane pump
DE502006004164D1 (en) 2005-10-06 2009-08-20 Joma Hydromechanic Gmbh Vane pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013221567A1 (en) * 2013-10-23 2015-04-23 Mahle International Gmbh Pendulum slide cell pump for pumping a fluid

Also Published As

Publication number Publication date
JP4834734B2 (en) 2011-12-14
DE502006004164D1 (en) 2009-08-20
WO2007039013A1 (en) 2007-04-12
KR101146845B1 (en) 2012-05-16
EP1794457A1 (en) 2007-06-13
WO2007039013A8 (en) 2007-09-27
KR20080049689A (en) 2008-06-04
US7785087B2 (en) 2010-08-31
US20080014108A1 (en) 2008-01-17
JP2009510331A (en) 2009-03-12

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