EP1910681B1 - Pompe a palettes - Google Patents

Pompe a palettes Download PDF

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Publication number
EP1910681B1
EP1910681B1 EP06760796.0A EP06760796A EP1910681B1 EP 1910681 B1 EP1910681 B1 EP 1910681B1 EP 06760796 A EP06760796 A EP 06760796A EP 1910681 B1 EP1910681 B1 EP 1910681B1
Authority
EP
European Patent Office
Prior art keywords
vane
adjusting ring
housing
pressure
constituted
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
EP06760796.0A
Other languages
German (de)
English (en)
Other versions
EP1910681A2 (fr
Inventor
Johannes Koller
Franz Wimmer
Helmut Buchleitner
Helmut Pamminger
Michael Hiller
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.)
Miba Sinter Holding GmbH and Co KG
Original Assignee
Miba Sinter Holding GmbH and Co KG
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 Miba Sinter Holding GmbH and Co KG filed Critical Miba Sinter Holding GmbH and Co KG
Publication of EP1910681A2 publication Critical patent/EP1910681A2/fr
Application granted granted Critical
Publication of EP1910681B1 publication Critical patent/EP1910681B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • F04C2230/22—Manufacture essentially without removing material by sintering
    • 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
    • F04C2240/70—Use of multiplicity of similar components; Modular construction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/02—Light metals
    • F05C2201/021—Aluminium

Definitions

  • the invention relates to a vane pump, as described in the preamble of claim 1.
  • a controllable vane pump with an adjusting device and in a pivoting arrangement about an axis parallel to a rotor axis pivot axis pivotally mounted in the pump housing collar known.
  • the adjusting ring together with the housing wall and sealing arrangements, form a pressure chamber which is connected in flow with a pressure region.
  • the adjusting device forms a pivoting movement of the adjusting ring under pressure load with a spring force counteracting, formed by a helical compression spring spring arrangement, which is arranged between a housing wall of the pump housing and formed on the adjusting ring by an extension abutment.
  • the DE 25 51 451 A1 discloses a controllable via a control device rotary lobe pump with a rotatable in a pump housing about a rotational axis vane rotor.
  • a piston valve with a vane rotor receiving bore adjustable mounted a bore diameter about a rotor diameter plus a maximum projection of a wing corresponds whereby in dependence on the means of the control device, which controls the relative position of the piston valve via pressurization of the spool variable delivery cell volume is achieved.
  • variable displacement vane pump with a rotatably mounted in the pump housing about a rotational axis rotor with radial slots arranged, which is surrounded by a collar which is arranged variable position in a pump chamber of the pump housing, wherein the adjusting ring about a pivot axis parallel to the axis of rotation is mounted in the pump chamber and between a concentric to the rotor position in a position eccentric to the rotor, for changing the delivery stroke, is adjustable.
  • the change in position of the adjusting ring is effected by means of controllable pressurization of both sides of the pivot bearing assembly extending pressure-tightly separated from each other, bounded by the outer wall of the adjusting ring and the inner wall of the pump housing pressure chambers.
  • a controllable vane pump is known as a lubricant pump, with rotatably mounted in a pump housing, provided with a plurality of radially movable blades rotor is surrounded by a pivotally mounted about a pin collar to limit pumping cells and the one, one to the axis of rotation extending pivot axis forming bolt, is pivotally mounted to change an eccentricity of the adjusting ring with respect to the rotor in the pump housing.
  • peripheral pressure surfaces of the adjusting ring are formed approximately equal.
  • a variable displacement vane pump in which in a pump housing, an annular rotor is rotatably mounted about an axis of rotation, which is surrounded by a mounted parallel to the axis of rotation pivot axis in the housing adjusting ring and the coaxial with a rotor in an eccentric position for Change a flow rate of a medium is adjustable.
  • a vane star is rotatably mounted on an axis which is mounted on an end wall of the adjusting ring and whose axis alignment is parallel to the axis of rotation.
  • variable-volume delivery cells between the rotor ring and the adjusting ring and thus a variable delivery volume, for controlling a delivery pressure by means of a spring arrangement is achieved which counteracts an adjustment of the adjusting ring by the pressurization in a region of its circumference.
  • the DE 100 29 969 C1 describes a vane pump having a seated on a drive shaft and a plurality of radially movable rotor blades having pump rotor which is mounted in an inlet and a drain having rotor chamber of a Pumpenstators which is pivotable within a pump bearing housing about a stationary pivot axis radially to the pump rotor, said Pump stator is associated with a control device for automatic pressure control having a projecting from the pump stator outside transverse to the pivot axis actuator which is pivotable by a pending on the pressure side of the rotor chamber conveying medium against the action of a storage power, wherein the actuator guided in a guide of the pump bearing housing and directly formed by the pumping medium acting on the rotary piston, and wherein the pump stator forms a double-armed lever, one lever arm containing the rotor chamber and the other lever arm the Schwe nkkolben forms.
  • the object of the invention is to provide a vane pump, which has small outer dimensions and thus a compact design and thereby an arrangement on a to be supplied with a lubricating medium engine is very universal.
  • This object of the invention is achieved by the reproduced in the characterizing part of claim 1 features.
  • the surprising advantage of this is the direct pressurization of the adjusting ring in a limited peripheral area whereby a housing training is achieved which is suitable for mass production and thus a cost-effectiveness is achieved and the cavity limiting sealing arrangements are achieved by direct interaction of collar and housing and thus additional, subject to wear underlying sealing elements.
  • the active surface is formed by a cross-sectional area of a cavity formed on the circumference of the adjusting ring, a precisely defined effective area and thus adjusting moment reached.
  • An embodiment according to claim 2 is advantageous, because an arrangement of an adjusting ring is possible directly adjacent to a pivot bearing arrangement, whereby small pivoting moments are achieved for the control.
  • the characterized in claim 6 advantageous development ensures a continuous regulation of the performance of the vane pump.
  • the characterized in claim 7 advantageous development ensures a continuous regulation of the performance of the vane pump.
  • the characterized in claim 11 advantageous embodiment allows mass production while maintaining the lowest manufacturing tolerances and achieving high surface qualities, thereby consuming reworking can be saved.
  • a controllable vane pump 1 is shown in plan view of a pump housing with partially removed cover part 3.
  • the pump housing 2 is formed by a one-piece component, in particular as a sintered metal component, and consists of a planar wall sheet 4 with a circumferential wall web 5, whereby a housing pan 6 is formed.
  • An area of the housing pan 6 has an approximately circular ground plan shape, which merges into an approximately tangentially extending trough area.
  • the areas of the housing pan form a rotor chamber 7 and a control chamber 8.
  • a drive shaft 10 is mounted with a vane rotor 11.
  • the vane rotor 11 consists of a cylindrical rotor body 12, which is preferably an odd number of extending approximately in the radial direction, a height 13 passing through receiving slots 14 is provided in which plate-shaped wings in the radial direction - according to double arrow 16 - are displaceably mounted.
  • the conveyance of the medium from a suction region 24 into a pressure region 25 takes place during rotation of the vane rotor 11 by the vane rotor 11 surrounding pumping cells 26 whose receiving volume, as will be described in detail later, is variable.
  • the dimensioning of the vane rotor 11 with respect to its outer diameter 17 and the supernatant 18 of the wings 15 and thus of the outer diameter 17 and the height 13 of the rotor body 12 is made according to a desired power range for the vane pump 1 taking into account the intended speed range of the vane pump 1 and physical data of the medium to be promoted. According to these dimensional specifications, the inner diameter 28 of the adjusting ring 27 is set.
  • the adjusting ring 27 is pivotally mounted in the housing pan 6 in a pivot bearing assembly 29 which forms a pivot axis 30 extending parallel to the axis of rotation 23, wherein in an end position - as in Fig. 1 shown - an inner wall surface 31 is positioned concentrically to the peripheral surface 32 of the rotor body 12, and in another end position - like the Fig. 2 can be seen - an eccentric position is achieved.
  • the pivot bearing assembly 29 is formed in the concrete example by a wall web 5 arranged, in particular integrally formed over a height 13 of the rotor body 12 extending wall rib 33 which projects beyond an inner surface 34 of the wall web 5 with an approximately semicircular cross-section. At this wall rib 33 of the adjusting ring 27 is superposed with a semi-circular in cross-section groove 35.
  • This training corresponds to a sliding bearing for the pivoting of the adjusting ring 27 about the pivot axis 30, which is determined by the outline contour of the wall rib 33 and groove 35.
  • a sealing arrangement 36 between both sides of the pivot bearing assembly 29th different pressure level - which will be discussed later - achieved.
  • a further sealing arrangement 38 is provided by jointly formed sealing surfaces 39, 40 on a sealing web 41 of the adjusting ring 27 and the wall web 5, wherein the sealing surfaces 39, 40 due to the pivoting of the adjusting ring 27 arcuately about the pivot axis 30 are curved.
  • a spring force - according to arrow 50 - causes the counter-torque about the pivot axis 30 corresponding to a normal distance 51 and causes an adjustment of the adjusting ring 27 in the now the Fig. 2 to be taken, eccentric position relative to the rotor body 12, as long as no pressure or low pressure in the cavity 42 is present.
  • the spring force - according to arrow 50 - the spring assembly 48 is adjustable according to a preferred embodiment for controlling a biasing force, for example by means of a spiral compression spring 49 more or less compressive set screw 52.
  • the end positions of the adjusting ring 27 are defined by two stop arrangements 53, 54, which are achieved by the arrangement of opposing abutment surfaces 55, 56 by corresponding formations and projections on the wall web 5 and collar 27. Die Anschlagan extract 53, 54 °.
  • the adjusting ring 27 is at the start of operation by driving the vane rotor 11 in the direction of rotation - as indicated by arrow 57 -, for example, by a power take-off of an internal combustion engine in the eccentric end position.
  • the sickle-shaped in this position pump cells 26 are about about kidney-shaped openings 58, 59 in the wall plate 4 and corresponding channel formations in the housing cover 3 with a storage tank 60 to form the suction region 24 and to form the pressure region 25 with supply lines 61 for lubrication points of an internal combustion engine 62nd flow-connected.
  • FIGS. 1 to 3 referred or referred.
  • the pump housing 2 forms with the housing pan 6, as previously described, the rotor chamber 7 and control chamber 8 from.
  • the vane rotor 11 is rotatably mounted on the drive shaft 10 about the rotation axis 23. Including the vane rotor 11 is mounted to form the pumping cells 26 of the adjusting ring 27 in the pivot bearing assembly 29 and between the wing rotor 11 concentric position, as in Fig. 4 shown in the eccentric position, as in Fig. 5 shown, swiveling.
  • the pivot bearing arrangement 29 is pressure-tight, wherein the sealing arrangement 36 is formed.
  • the further and in the distance 37 circumferentially formed on the adjusting ring 27 sealing assembly 38 is formed in the embodiment shown by a groove-shaped recess 63 on a peripheral surface 64 of the adjusting ring 27 and a sealing element 65.
  • the sealing element 65 is a sealing strip 66 in the recess 63 of the adjusting ring 27 relatiwerschietons sealingly engaged.
  • An adjustment of the sealing strip 66 in the recess 63 ensures a sealing contact of opposing sealing surfaces 68, 69 between the sealing strip 66 and your collar 27 both in the concentric end positions as well as in the eccentric end position of the adjusting ring 27.
  • the sealing element 65 is further in the pump housing for adjusting an angular position during adjustment of the adjusting ring 27 pivotally mounted about an axis of rotation 23 parallel to the pivot axis 70. But it is also a fixed arrangement of the sealing element possible, for example, in a resilient design of cooperating with the recess 63 sealing strip 66th
  • the pressure chamber 44 is, as also described above, fluidly connected to the pressure region 25, as shown in dashed lines.
  • the distance 37 between the sealing arrangements 36, 38 is dimensioned such that the effective area 45 for the pressurization on the peripheral surface 64 of the adjusting ring is between 5% and 45% of the total circumferential surface 64 of the adjusting rings 27.
  • Fig. 6 is the training with a pivotable sealing element 65, wherein the sealing strip 66, as a result of the medium pressure in the pressure chamber, regardless of the position of the Adjusting ring 27 tangentially to this applies and thus a line-shaped, sealing abutment on the peripheral surface 64 of the adjusting ring 27, shown.
  • This thus forms the sealing arrangement 36.
  • the sealing strip 66 is advantageous, as the Fig. 5 taken curved in the direction of the cavity shaped whereby the sealing strip 66 with the surface slidably rests against the peripheral surface 64 of the adjusting ring.
  • FIGS. 7 and 8 shows a further embodiment of the vane pump 1, wherein in Fig. 7 the adjusting ring 27 concentric in the wing rotor 11 and in Fig. 8 maximum eccentric position is shown.
  • the adjusting ring 27 is pivotally mounted in the housing pan 6 or the rotor chamber 7 of the pump housing 2 via the pivot bearing arrangement 29, which is parallel to the axis of rotation 23 of the wing rotor 11, via the pivot bearing arrangement 30 already described in the preceding Figures.
  • the pump housing 2 further forms, as also already described, the control chamber 8 with the compression coil spring 49 of the adjusting device 47.
  • the pump housing 2 has a U-shaped housing extension 71 which projects directly adjacent to the pivot bearing arrangement 29 and projects beyond the outer contour of the pump housing 2. This forms with a peripheral edge web 72 a receiving chamber 73. This is limited by the bottom-side wall plate 4 of the pump housing 2 and the edge plate 72 integrally connected to the wall plate 4 and extends approximately over a quarter of the outer contour of the pump housing 2.
  • On the adjusting ring 27 is an outer circumference 74 protruding and einragend into the receiving chamber 73 a U-bow-shaped web 75 arranged, in particular integrally formed, and with a portion of the peripheral surface 64 of the adjusting ring 27, the self-contained, along the outer periphery 74 extending cavity 42 is formed.
  • a sealing web 76 is arranged on the bottom-side wall plate 4, which extends longitudinally in the direction of the cavity 42 and with opposite, perpendicular to the wall plate 4 extending end faces 77, 78 sealingly abuts against opposite inner surfaces 79 of the web 75.
  • the end faces 77, 78 of the sealing web 76 and these facing inner surfaces 79 of the web 75 have a correspondingly coordinated Outer contour, which ensure an exact sealing system, regardless of the position of the adjusting ring 27 in the pivoting area about the pivot axis 30.
  • An inner width 80 of the cavity 44 is slightly larger than the maximum pivoting distance 81 plus a maximum thickness 82 of the sealing ridge 76.
  • the positioning of the sealing ridge 76 on the wall plate 4 and the adjusting ring 27 facing contact surface 63 of the sealing ridge 76 is in a curvature corresponding to a Adjusted outside diameter 84 of the adjusting ring and thus forms the sealing ridge 76 with the contact surface 83 of the stop surface 55, which limits the maximum pivotability of the adjusting ring 27 in the eccentric adjustment.
  • a groove-shaped recess 84 extending over an entire height of the sealing web 76 is provided in the contact surface 83, in which the medium pressure is present through a connecting channel, connecting line etc. from the pressure region 25 of the vane pump 1.
  • the formation of the cavity 42 on the adjusting ring 27 thus enables a design of the active surface 64 in the inventively provided range between about 5% and 45% of the entire peripheral surface 64 of the adjusting ring 27th
  • the adjusting ring 27 is shown in its two end positions.
  • the adjusting ring 27 is formed around the wall web 5 of the pump housing 2 and the adjusting ring 27 formed pivot bearing assembly 29 and the pivot axis 30 formed by this between the in Fig. 8 shown concentric position in the Fig. 9 shown eccentric position to the vane rotor 11 pivotally, wherein the pivoting moment by the spring assembly 48 of the adjusting device 47 - according to arrow 87 - is applied.
  • the counter-torque is caused by a force - according to arrows 88 - resulting from the medium pressure in the pressure chamber 44.
  • a arranged in the pressure chamber 44 sealing disc 89 which is connected in movement with the adjusting ring 27, is present.
  • the pressure chamber 44 is flow-connected via a connecting channel with the pressure region 25 of the vane pump 1.
  • the design of the sealing disc 89 and the pressure chamber 44 ensures regardless of the tilt angle - according to arrow 90 - a tight contact and thus the sealing arrangements 36, 38 between end surfaces 91, 92 of the sealing disc 89 and the wall web 5.
  • the effective area 45 is approximately between 5% and 45% of an entire circumferential surface 64 of the adjusting ring 27th
  • Fig. 11 is another, not covered by the scope falling training of the vane pump 1 shown.
  • the adjusting ring 27 is pivotally mounted in the pivot bearing assembly 29 about the pivot axis 30 on the wall web 5 of the pump housing 2.
  • the adjusting ring 27 is shown in its concentric position to the vane rotor 11.
  • the spring assembly 48 of the adjusting device 47 is formed in the embodiment shown by a spiral torsion spring 93 with cantilevered spring legs 94, 95, one of which is supported on the crosspiece 5, and the other a spring force - according to arrow 96 - on the adjusting ring 27 in the direction the pivoting - as indicated by arrow 97 - in the eccentric situation exerts.
  • the stop assemblies 53, 54 are on the one hand achieved by contact surfaces 106, 107 of the spring leg 95 and a wall rib 108 for the concentric position of the Stellringes.27 and on the other hand for the eccentric position by contact of the peripheral surface 64 of the adjusting ring 27 on the inner surface 34 of the wall web fifth
  • FIG. 12 is another, not covered by the scope falling training of the vane pump 1 shown.
  • the figure shows the position of the adjusting ring 27 in the pivoted about the pivot axis 30, eccentric position to the vane rotor 11.
  • the adjusting device 47 forms in this embodiment a biased by the spring assembly 48 in the eccentric position rack gear 109, wherein the peripheral surface 64 of the adjusting ring 27th outstanding, one of a plurality of teeth 110 formed from toothed segment 111 arranged, is preferably formed.
  • a multi-part rack 112 which is linearly adjustable by a linearly guided in the pump housing 2 slider 113 - according to double arrow 114 - for pivoting the adjusting ring 27.
  • a spiral compression spring 115 causes a bias on the rack 112 and the slider 113 and is supported on a Wand Schemet 116 of the pump housing 2 on the one hand and on a system of the rack 112 and the slider 113 on the other.
  • the slide 113 protrudes with an extension 119 forming a pressure piston 118 into the pressure space 44 formed in the pump housing 102, which is in flow communication with the pressure region 25 of the vane pump 1.
  • An end face 120 of the extension 119 forms the active surface 45, in which the medium pressure for adjusting the slider 113 - as indicated by arrow 121 - and thus the rack 112, whereby the adjustment of the adjusting ring 27 is effected in the concentric position with respect to the vane rotor 11.
  • the rack 112 consists for example of at least two sheet-shaped racks with identical tooth profile which are slidably mounted relative to each other in the direction of longitudinal extension of each of which is drivingly attached to the slider 113 and which is further acted upon by the coil spring 49. This causes a clearance compensation of the rack and pinion drive 109th
  • Fig. 13 is another, not covered under the scope of the design of the vane pump 1 shown.
  • the adjusting device 47 is formed by the rack and pinion gear 109 with the slider 113, the rack 112 and the toothed segment 111 on the adjusting ring 27.
  • the slide 113 also projects, as already described in the preceding figure, with the extension 119 formed as a pressure piston 118 into the pressure chamber 44.
  • the spring assembly 48 of the adjusting device 47 is formed in this embodiment shown by the adjusting ring 27 at a distance, the circumferential surface 64 in the curvature approximately adapted leaf spring 122.
  • This is articulated approximately centrally via a pivot bearing 123 on the adjusting ring 27 and supported with a cantilever spring arm 124 on the wall web 5 of the pump housing 2 and a rib-like projection on the inner surface of the wall web 5 and with another, projecting from the pivot bearing 123 spring arm 125, for bias of the slide 113 and the rack 112, in the direction of the pressure chamber 44-according to arrow 126 - supported on a connecting web 127 of the rack 112.
  • a backlash compensation of the rack and pinion drive 109 may also be provided as previously described.
  • adjusting ring 27 in the housing pan 6 formed by a bottom wall plate 4 and the wall web 5 in a linear direction - according to double arrow 128 - arranged adjustable, with opposing inner wall surfaces 129, 130 of the pump housing 2 and side surfaces 131, 132 of the adjusting ring 27 form a linear guide arrangement 133.
  • the adjusting ring 27 is shown in the pump housing 2 at the stop of opposing abutment surfaces 134, 135 between the wall web 5 and the adjusting ring 27 in the eccentric end position.
  • a gap formation between the wall web 5 and the end face forming active surface 45 between the abutment assemblies 53, 54 of the flow chamber connected to the pressure chamber 25 of the vane pump 1 pressure chamber 44 is formed.
  • the adjusting device 47 is formed in the illustrated embodiment by 2 spiral compression springs 137 which are arranged in, formed in the housing, spring chambers 138 and the adjusting ring 27 in the eccentric position by the bias of the coil springs 137 - tension - according to arrows 139.
  • the biasing force of the helical compression springs 137 is predetermined according to the desired pressure level. With increasing pressure, an adjustment of the adjusting ring 27 in the direction of the concentric position with respect to the vane rotor 11th
  • 27 linear sealing elements 140 are provided in the side surfaces 131, 132 of the adjusting ring, which form the sealing arrangements 36, 38 between the adjusting ring 27 and the housing web 5.
  • a further embodiment of the vane pump 1 is shown as a tandem pump 141.
  • the pump housing 2 in this case has two, opposite in relation to a central wall 142, limited by this and the wall webs 5, housing trays 6.
  • a vane rotor 11, surrounded by a respective adjusting ring 27 are arranged in each of the housing trays 6.
  • the embodiment shown can be designed, for example, for an identical or different depth 143 of the two housing trays 6.
  • Such a design makes it possible to design the power range of such a vane pump 1 within wide limits - using similar components, e.g. by sizes specified in type series.
  • the pump housing 2 and the rotor body 12 made of molded parts made of sintered metal.
  • the housing cover 3 A1 die-cast molded parts are preferably used.
  • the drive shaft 10 and wings 15 are preferably made of steel.
  • sintered metal components Due to the production process, sintered metal components have a high, consistent quality standard and guarantee production while maintaining the lowest tolerances. As a result, such components are often suitable for use without the need for costly reworking.

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

Claims (14)

  1. Pompe à palettes (1), en particulier pompe à huile réglable pour un système de lubrification, comportant un corps de pompe (2) avec au moins une cuve (6) et comportant un rotor à palettes (11), qui est disposé dans la cuve (6) et est monté rotatif dans le corps de pompe (2) au-dessus d'un arbre d'entraînement (10) formant un axe de rotation (23), et qui loge des palettes (15) dans des fentes de réception (14) orientées radialement, et comportant une bague de réglage (27), qui délimite, du côté périphérique, des cellules (26) entourant le rotor à palettes (11) et qui est montée pivotante avec une paroi intérieure (31) cylindrique entre une position concentrique au rotor à palettes (11) et une position excentrique à celui-ci dans un système de palier pivotant (29) qui forme un axe de pivotement (30) parallèle à l'axe de rotation (23), et comportant une zone d'aspiration et une zone de pression (24, 25), séparées l'une de l'autre de manière étanche à la pression, et comportant un dispositif de réglage (47) qui règle le niveau de pression dans un flux de transport, et une surface active (45) du côté périphérique sur la bague de réglage (27), laquelle est délimitée par des systèmes d'étanchéité (36, 38) écartés l'un de l'autre entre la bague de réglage (27) et le corps de pompe (2) et laquelle forme avec un bord de paroi (5) du corps de pompe (2) une chambre sous pression (44) reliée par une liaison fluidique à la zone de pression (25), caractérisée en ce que le système de palier pivotant (29) est formé par une nervure (33), qui est disposée, de préférence formée, sur le bord de paroi (5) et s'étend sur une hauteur (13) du corps de rotor (12) et qui, avec une section transversale sensiblement semi-circulaire s'avance au-delà d'une face intérieure (34) du bord de paroi (5), et la bague de réglage (27) avec une rainure (35) à section transversale semi-circulaire est posée sur la nervure (33), et en ce que la surface active (45) est formée par une surface de section transversale d'une cavité (42) réalisée sur la périphérie de la bague de réglage (27).
  2. Pompe à palettes selon la revendication 1, caractérisée en ce que la surface active (45), sollicitée en pression, de la chambre sous pression (44) mesure entre 5 % et 45 % d'une surface périphérique (64) de la bague de réglage (27).
  3. Pompe à palettes selon la revendication 1, caractérisée en ce qu'une zone de pivotement de la bague de réglage (27) est délimitée par au moins un dispositif de butée (53, 54).
  4. Pompe à palettes selon la revendication 3, caractérisée en ce que les dispositifs de butée (53, 54) sont formés par des ergots de butée s'avançant au-delà de la surface périphérique (64) de la bague de réglage (27).
  5. Pompe à palettes selon la revendication 4, caractérisée en ce que des creux dans le bord de paroi (5) sont associés aux ergots de butée en tant que limite de la position finale de la zone de pivotement de la bague de réglage (27).
  6. Pompe à palettes selon la revendication 1, caractérisée en ce que le dispositif de réglage (47), agissant à l'encontre du couple de pivotement de la bague de réglage (27) qui dépend de la pression, est formé par un système à ressort (48), par exemple un ressort de pression hélicoïdal (49), agissant entre le corps de pompe (2) et la bague de réglage (27).
  7. Pompe à palettes selon la revendication 6, caractérisée en ce qu'une force du système à ressort (48) est réglable par un dispositif de serrage associé à celui-ci.
  8. Pompe à palettes selon la revendication 7, caractérisée en ce que le dispositif de serrage est formé par une vis de réglage (52).
  9. Pompe à palettes selon la revendication 1, caractérisée en ce que le corps de pompe (2) comporte des cuves (6) qui, séparées par une cloison intermédiaire (142), sont réalisées symétriquement à un plan médian (136), perpendiculaire à l'axe de rotation (23).
  10. Pompe à palettes selon la revendication 9, caractérisée en ce que dans chacune des cuves (6) sont disposés des rotors à palettes (11) reliés en entraînement par un arbre d'entraînement (10) commun.
  11. Pompe à palettes selon la revendication 1, caractérisée en ce que le corps de pompe (2), formé d'un seul tenant par le panneau de paroi (4) et le bord de paroi (5), et le corps de rotor (12) et la bague de réglage (27) sont formés de préférence par un corps en métal fritté.
  12. Pompe à palettes selon la revendication 1, caractérisée en ce que l'arbre d'entraînement (10) et les palettes (15) sont réalisées en acier allié.
  13. Pompe à palettes selon la revendication 1, caractérisée en ce que le couvercle (3) du corps de pompe est réalisé de préférence dans un alliage d'aluminium.
  14. Pompe à palettes selon la revendication 13, caractérisée en ce que le couvercle (3) du corps de pompe est réalisé de préférence dans une fonte d'aluminium coulée sous pression.
EP06760796.0A 2005-07-29 2006-07-20 Pompe a palettes Active EP1910681B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0127905A AT502189B1 (de) 2005-07-29 2005-07-29 Flügelzellenpumpe
PCT/AT2006/000309 WO2007012096A2 (fr) 2005-07-29 2006-07-20 Pompe a palettes

Publications (2)

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EP1910681A2 EP1910681A2 (fr) 2008-04-16
EP1910681B1 true EP1910681B1 (fr) 2015-08-26

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US (1) US8545199B2 (fr)
EP (1) EP1910681B1 (fr)
JP (1) JP2009503318A (fr)
CN (1) CN101268279B (fr)
AT (1) AT502189B1 (fr)
WO (1) WO2007012096A2 (fr)

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WO2014077835A1 (fr) * 2012-11-16 2014-05-22 Moog Inc. Pompes à palettes et leurs procédés de commande
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Also Published As

Publication number Publication date
AT502189A4 (de) 2007-02-15
AT502189B1 (de) 2007-02-15
JP2009503318A (ja) 2009-01-29
WO2007012096A2 (fr) 2007-02-01
EP1910681A2 (fr) 2008-04-16
CN101268279A (zh) 2008-09-17
US8545199B2 (en) 2013-10-01
CN101268279B (zh) 2012-11-07
US20100008806A1 (en) 2010-01-14
WO2007012096A3 (fr) 2007-06-28

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