EP2151542B1 - Pompe à piston rotatif dotée de poches pour lubrifiants - Google Patents

Pompe à piston rotatif dotée de poches pour lubrifiants Download PDF

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Publication number
EP2151542B1
EP2151542B1 EP09166834.3A EP09166834A EP2151542B1 EP 2151542 B1 EP2151542 B1 EP 2151542B1 EP 09166834 A EP09166834 A EP 09166834A EP 2151542 B1 EP2151542 B1 EP 2151542B1
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EP
European Patent Office
Prior art keywords
pocket
sliding surface
rotor
pockets
piston pump
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.)
Not-in-force
Application number
EP09166834.3A
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German (de)
English (en)
Other versions
EP2151542A2 (fr
EP2151542A3 (fr
Inventor
Uwe Dr. Meinig
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive 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 Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Publication of EP2151542A2 publication Critical patent/EP2151542A2/fr
Publication of EP2151542A3 publication Critical patent/EP2151542A3/fr
Application granted granted Critical
Publication of EP2151542B1 publication Critical patent/EP2151542B1/fr
Not-in-force 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 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
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors

Definitions

  • the invention relates to rotary piston pumps and is directed in particular to vacuum pumps.
  • the drive of the pump which is permanent during operation of the internal combustion engine, must continue to pay attention to a reduction in the drive power required for the pump against the background of the CO 2 problem and the constant compulsion to reduce fuel consumption.
  • a starting point for improving the efficiency is the reduction of the friction power at the end face of the pump rotor.
  • Lubricant is supplied to the two bearing gaps on the end faces of a rotor of a vacuum pump.
  • the rotor is rotatable about an axis of rotation between two side plates facing its end faces.
  • the side plates are axially movable and are acted upon in the direction of the respective facing end face of the rotor with a pneumatic pressure to seal the delivery chamber of the pump.
  • the rotor has at both end faces in each case a peripheral Gleitdicht Structure surrounding the rotation axis. Radially within this annular sliding surface, the end face of the rotor is axially withdrawn a bit.
  • the two peripheral sliding surfaces provide in cooperation with the axially movable side plates for the tightness of the delivery chamber, while the recessed, central region through the respective side plate through lubricant is supplied.
  • the side plates are for this purpose of open porosity and saturated with the lubricant.
  • the friction between the side plates and the peripheral sliding surfaces of the rotor should still be considerable due to mixed friction.
  • the execution of the side plates with the porosity required for the lubrication with sufficient stability and wear resistance will also not be unproblematic.
  • the DE 33 25 261 A1 known vacuum pump is used as a sealing and lubricating oil centrally supplied to one end face of the rotor and guided via two radially branching off from the central feed throttle channels in a reclaimed at the end face of the rotor annulus.
  • the two narrow throttle passages each extend radially beyond an inner sliding sealing surface of the rotor to open into the recessed annular space which extends in the face of the rotor about an inner sliding surface and is circumferentially enclosed by a peripheral sliding surface sealing the housing cover.
  • the friction in the sliding bearing clearance between the sliding surface of the housing cover and the two sliding surfaces of the rotor, the inner sliding surface and the peripheral sliding surface should be considerable.
  • the JP 2000-337267 A discloses a lubrication of the frontal bearing gaps for a hydraulic pump.
  • the working fluid also serves as a lubricant.
  • An improvement in the lubricating effect is achieved in that formed in the front side of the conveying chamber bounding chamber walls, between the formed in these chamber walls inlet and outlet openings for the working and lubricating medium each have many small, circular depressions and about the axis of rotation of the rotor on a Circle are evenly distributed.
  • the depressions act as lubrication pockets, but you will not learn more about the mode of action and the shape of the wells.
  • the JP 10-068393 A teaches to improve the lubrication of a vacuum pump, to form in a forming with the chamber wall, the sliding bearing gap sliding surface of the rotor a plurality of pockets which are seen in the plan view of the end face of the rotor are each completely within the sliding surface, thus beerbstandet in the circumferential direction of each other and both radially be limited inwardly and outwardly from the sliding surface.
  • the pockets each have the shape of a slender, curved around the axis of rotation part ring.
  • this solution also requires a thick lubricant film, associated with corresponding leakage losses and with regard to the efficiency of the pump.
  • the GB 2 012 874 which is considered to represent the closest prior art, discloses a gas compressor with a rotor whose sides in the axial direction have wedge-shaped recesses with constant inclination.
  • the subject of the invention is a rotary piston pump comprising a housing with a delivery chamber and at least one rotor rotatable about a rotation axis in the delivery chamber.
  • the rotor has on its two end faces sliding surfaces which each form a sliding pair with axially facing sliding surfaces of the chamber.
  • the end-side chamber walls which form said sliding surfaces of the chamber are preferably not movable, but stationary in the housing.
  • at least one of the sliding surfaces i. in at least one of the front-side sliding surfaces of the rotor or in at least one of the front-side sliding surfaces of the chamber, at least one pocket for lubricant is formed.
  • the pocket is bounded circumferentially with respect to the axis of rotation and radially outward by the sliding surface containing the pocket.
  • the bag is shaped so that, when the rotor rotates, a hydrodynamic lubricating film builds up in the gap of the pair of bearings having the pocket.
  • the bag is designed as in the characterizing part of claim 1.
  • the pocket is shaped so that the hydrodynamic lubricant film builds up at the speeds typical for the operation of the rotary piston pump, in which the rotary piston pump is predominantly operated.
  • the bag has for this purpose a sufficient volume and a suitable shape, in particular, it has a care for the lubricating film construction depth profile.
  • the pocket is preferably shaped such that the hydrodynamic lubricating film sets in the sliding gap immediately after the trailing end of the pocket in the direction of rotation of the rotor.
  • the same or the axially opposite sliding surface can or may contain one or more further pocket (s) that do not meet this condition, as long as in the gap of the sliding surfaces as a whole from the transition speed prevails the hydrodynamic lubrication state. If, as preferred, several pockets according to the invention are provided, it is sufficient if these pockets bring about the construction of the hydrodynamic shear film only in combination.
  • the pocket flattens in the circumferential direction, in the direction of its trailing end, thus tapering, preferably over its entire radially measured width. If the taper extends only over part of the radial pocket width, this tapered width region is preferably arranged radially in the middle region of the sliding surface.
  • the pocket forms a wedge in the gap of the sliding surfaces at the trailing end.
  • the pocket may have a variable inclination in the course of the rise to the sliding surface containing it, in particular an inclination which decreases towards the trailing end, so that the bottom of the pocket in the region of the wedge towards the opposite Sliding surface of the sliding couple bulges around.
  • the inclination is constant over at least one larger, preferably the predominant part of the wedge.
  • the pocket bottom may include in the rise one or more curved section (s) in combination with one or more straight section (s). It may also have one or more stages in the wedge-shaped gap, but a continuous course is preferred. It can with respect to the axially opposite sliding surface from the outlet in the sliding surface in the circumferential direction may even have one or more concave sections, as long as the hydrodynamic lubricant film is still built up.
  • the wedge preferably extends over at least a quarter, more preferably over at least half of the pocket depth, the reference depth being the maximum depth of the pocket.
  • the bag may be perpendicular to the bottom of the bag, i. in the axial direction, or increase with increasing inclination and only from half the pocket depth or already before tapering gradually.
  • the taper can already be used immediately in the pocket bottom, i. From the pocket bottom flatten out directly with an inclination to the sliding surface containing them.
  • the inclination to the sliding surface should be at most in the trailing end region of the wedge at most 45 °, more preferably at most 30 °, both in the case of a constant and in the case of a variable inclination.
  • the mentioned angle values should not be exceeded.
  • Lower angles of inclination are advantageous in view of the shear forces acting on the structure of the hydrodynamic lubricant film in the lubricant, in particular in the outlet of the wedge.
  • an inclination directly at the end of the wedge of at most 15 ° is particularly preferred, it also corresponds to preferred embodiments, when the inclination decreases continuously, at least at the end of the wedge, the wedge can expire in particular tangentially into the sliding surface.
  • the wedge length measured in the circumferential direction it is advantageous if the wedge extends over at least half the pocket length, wherein the advantage of this geometry feature increases with decreasing pocket length.
  • a connection can additionally be provided between the pocket and the radially outer edge of the sliding surface or pocket and a circumferential surface radially adjoining the sliding surface, either in the form of a connecting channel lying below the sliding surface or open on the sliding surface.
  • such an optional connection channel is designed so that it provides the flow of lubricant from the bag considerable resistance to flow, which is several times greater than in the case of a pocket which passes through the sliding surface radially with its full pocket cross-section.
  • a radial boundary of the pocket by the sliding surface is thus also seen when a narrow in the circumferential direction or in the depth direction of the pocket flat connecting channel has a flow cross-section which is smaller by a multiple than a largest pocket cross-section.
  • An optional connection channel can be used to selectively use lubricant on the bag radially outward into the chamber and there for lubrication, for example, the tip of a wing of a vane pump.
  • the optional connecting channel is dimensioned such that, in spite of the drainage of lubricant facilitated by it, the hydrodynamic lubricating film forms.
  • the trailing end of the pocket can, seen in plan view of the sliding surface, run straight over its entire radial width and run at least essentially radially, ie pass over the pocket into the sliding surface via a radial edge line.
  • the pocket may also be undercut in plan view of the sliding surface, so that it has a circumferentially extending extension at the trailing end which is bounded radially inwards, in the direction of the axis of rotation of the rotor, by the sliding surface.
  • the undercut counteracts a flow of the lubricant radially inwardly, in particular in preferred embodiments, in which the pocket radially inward, ie in the direction of the axis of rotation, on an inner peripheral surface opens, so that the sliding surface passes radially in the direction of the axis of rotation.
  • the sliding surface is in such embodiments extends annularly around the axis of rotation. A radially inwardly passing through the sliding surface has the advantage that such a pocket can be supplied with lubricant from the central region within the annular sliding surface.
  • further pockets in the manner according to the invention are formed in the sliding surface containing the pocket.
  • the pockets are circumferentially spaced from each other about the axis of rotation, preferably a portion of the sliding surface remains between them, and are bounded radially outward by the sliding surface containing them.
  • the pockets are advantageously arranged distributed around the axis of rotation at least substantially uniformly.
  • the angular distances of respectively adjacent pockets are substantially the same in such embodiments.
  • a rotary vane pump with a single vane, which passes radially through the rotor is regarded as a uniform angle division, an arrangement in which the pockets are distributed symmetrically with respect to the wing.
  • the pockets are seen in plan view of the sliding surface and in cross section preferably equal to each other, but may in principle also differ from each other. You can also deviate from each other in the depth profile, but more preferably they are equal to each other in the depth profile.
  • the depth profile is the course of the axial depth in the circumferential direction on a cylindrical surface which cuts the pocket about the axis of rotation.
  • this pocket may in particular be arranged so that it counteracts a light tilting position of the rotor axis which is present in some applications in pump operation.
  • the pocket is arranged in one of the end-side sliding surfaces of the chamber, ie stationary with respect to the chamber. The tilting position of the rotor, if present during operation, is known in advance, so that the bag can be arranged accordingly.
  • pockets of the type according to the invention are formed in the respective sliding surface of the chamber in the circumferential direction, these pockets are arranged so as to at least partially compensate the tilting position, for example by providing the pockets in the circumferential direction only in half of the sliding surface, in the the gap between the sliding surfaces is smaller due to the tilted position than in the other hemisphere.
  • pockets can also be distributed over the entire circumference, with the ratio of pocket area to remaining sliding area being greater than in the other hemisphere of the relevant sliding area in order to compensate for a tilted position in the corresponding hemisphere.
  • the pocket or preferably a plurality of pockets may or may not be formed in one of the sliding surfaces of the rotor or one of the chamber sides of the rotor facing side.
  • the word "or” is always understood in the usual logical sense as an “inclusive or”, ie includes both the meaning of "either ... or” as well as the meaning of "and”, as far as the specific context is not exclusively only one limited meaning.
  • a single or multiple pockets may or may therefore be provided, for example, only in one or only in both frontal sliding surfaces of the rotor, these two embodiments are particularly preferred, or only in one of the two sliding pairings co-forming sliding surfaces of the chamber or only in both frontal sliding surfaces the chamber.
  • a single pocket or pockets may also be formed in one or both of the sliding surface (s) of the rotor and additionally in one or both facing sliding surfaces of the chamber, including, for example, the case where a single pocket or a plurality of pockets only on one of the two end faces of the rotor and a single or more pockets is formed only in that sliding surface of the chamber or are, which forms a sliding pair on the opposite end face of the rotor with the local Rotorgleit
  • the invention also includes the case that the rotor on one or both ends has a single or more pockets and the chamber is also provided on the same face also with a single or more pockets of the type according to the invention, which associated with the same sliding pair Bags of the rotor and the chamber are radially offset from each other so that they do not overlap during rotation of the rotor.
  • vane pumps having a single or multiple vanes (s) slidably guided by the rotor, and also swing vane pumps.
  • single-wing designs are preferred, ie Versions in which the rotor with the wing divides the delivery chamber into only two cells.
  • the rotary piston pump can be designed with a variable or constant delivery volume. It can be multi-stroke, but is preferably one-stroke.
  • a plurality of rotors, for example two rotors, may be arranged in the delivery chamber, with a pair of bearings preferably being formed in accordance with the invention in each case on both rotors at at least one axial end side.
  • the bag is advantageously formed in shaping on the rotor in a peripheral region of the sliding surface, which is not penetrated by a wing, a sliding or swing wing.
  • the sliding surface with the at least one pocket according to the invention is not interrupted in the circumferential direction, but extends completely circumferentially around the axis of rotation, this consideration plays no role.
  • the plurality of pockets are advantageously arranged in the rotor around the axis of rotation in such a number that at least one of the pockets is arranged in the angular region of each cell of the cell pump.
  • per cell which forms the rotor with its one-piece or divided wing, preferably at least two of the pockets according to the invention are arranged.
  • the rotary piston pump preferably requires a gaseous working fluid while the lubricant is preferably liquid.
  • the invention is directed to a vacuum pump which is installed in a motor vehicle or intended for installation in a motor vehicle.
  • the pump can generate the vacuum required for a brake booster. It is preferably powered by the engine, which is preferably an internal combustion engine.
  • the engine which is preferably an internal combustion engine.
  • the rotor on the circumference of a rotor bearing portion provided with a floating sliding bearing and thus axially fixed, but is movable either within the axial tolerance or a deliberately provided axial play between the end faces of the delivery chamber.
  • the pressure of the crankcase of the engine which generally corresponds approximately to the atmospheric pressure, while at the opposite, opposite projection surface of the rotor in the a relatively high negative pressure acts on a large number of operating states of the pump, so that the rotor is pressed against the relevant sliding surface of the chamber. It arises according to the pressure gradient, a considerable axial thrust, which leads to a large friction in the case of planning in the prior art frontal geometry of the rotor, countermeasures are not taken according to the invention.
  • the mixed friction states in the axial thrust bearing of the rotor due to unfavorable tribological conditions entail the risk of wear, which in many cases must be prevented by a coating of the chamber wall which causes costs.
  • inventive design can be dispensed with a coating only for the purpose of Reibverschl fashionminderung, even if a coating as an additional measure should not be excluded categorically.
  • the invention is not limited to the field of vacuum pumps.
  • the medium to be conveyed may also be a liquid and in such embodiments also simultaneously form the lubricant.
  • Preferred examples of liquid pumps are lubricating oil pumps for supplying an internal combustion engine of a vehicle or another unit of a vehicle with lubricant or hydraulic fluid. Such a pump is preferably driven by the engine of the vehicle.
  • a single or more preferred pocket (s) according to the invention is expediently provided in the case of the sliding pair which has to absorb the axial thrust whose axial sliding surfaces therefore press against each other axially examined.
  • the rotor can be reduced by means of a forming tool to the bag (s) by forming the rotor tool, i. be produced without additional processing and thus virtually cost-neutral.
  • a subsequent machining process for example a grinding process
  • the end face of the rotor is thus produced without additional manufacturing effort a suitable wedge gap geometry which is effective in tribological interaction with the preferably plane chamber wall.
  • the inventive lubricating pocket (s) can be dispensed with an additional anti-wear coating one of the sliding bearing gap forming sliding surfaces.
  • the rotor can be molded in particular by pressing and sintering as a sintered part made of metal or plastic or by injection molding of plastic as an injection molded part.
  • FIG. 1 shows a rotary piston pump in a longitudinal section. It is a vacuum pump, for example for generating a negative pressure for a brake booster of a motor vehicle.
  • the pump is driven by the combustion engine of the vehicle. It comprises a housing 1 with a housing structure 2 and a cover 3, which is detachably connected to the housing structure 2.
  • FIG. 2 shows the pump in a plan view from the side of the lid 3 ago, with the lid 3 is removed.
  • the housing 1 forms a delivery chamber 4 with an inlet 5 and an outlet 6 for the fluid to be delivered, in the exemplary embodiment air.
  • the inlet 5 and the outlet 6 open at an inner circumferential surface 14 of the housing 1, in the embodiment of the housing structure 2, in the chamber 4.
  • the inlet 5 is provided with a valve which allows a flow only in the chamber 4.
  • the inlet 5 merges with an additional outlet 7.
  • the outlet 6 is closed by a lamella valve 8 and the outlet 7 by a lamella valve 9, so that fluid through the outlet 6 and also through the outlet 7 only out of the chamber, but not in the chamber can flow in.
  • the additional outlet 7 acquires significance only in the case of a temporary reversal of the direction of rotation V.
  • a rotor 10 is rotatably disposed about a rotation axis R in the chamber 4.
  • the rotor 10 is slidably mounted axially rotatable axially outside of the chamber 4 along a rotor bearing section 11, for which purpose the bearing section 11 and, by way of example, the housing structure 2 form an axially movable slide bearing pairing.
  • the rotor 10 has at the end facing away from the delivery chamber 4 a connection for a rotation secured connection directly with a camshaft or a drive wheel, via which it is in the mounted state of the internal combustion engine, for example, driven by the camshaft.
  • the pump is designed as a single-vane vane pump.
  • a wing 13 passes through the rotor 10 in the radial direction and is guided by the rotor 10 in a rotor slot 12 radially reciprocating back and forth.
  • the rotor 10 and the wing 13 divide the delivery chamber 4 into two delivery cells, one of which is connected to the inlet 5 and the other to the outlet 6.
  • the rotor 10 is arranged eccentrically in the chamber 4, so that it fluidly separates the two conveyor cells and in particular the inlet 5 and the outlet 6 with its outer circumferential surface.
  • FIG. 2 take the rotor 10 and the wing 13 just a symmetry position, in which the two conveyor cells are the same size. If the rotor 10 rotates in the direction of rotation V, the in FIG.
  • the rotor 10 has a sliding surface 15 on an end face remote from the drive side and a sliding surface 17 on the other end side facing the drive side.
  • the sliding surfaces 15 and 17 form with axially opposite sliding surfaces 16 and 18 of the housing 1 each have a sliding pair.
  • the frontal sliding surfaces of the wing 13 are not provided with their own reference numerals, but form with the axially facing chamber walls each have a further pair of bearings.
  • the housing-side sliding surface 16 on the end face of the rotor 10 facing away from the drive side is formed by the cover 3, while the housing structure 2 forms the counter-sliding surface 18 for the rotor sliding surface 17.
  • a lubricating oil or other suitable lubricant is supplied.
  • the lubricant can be conducted into a central cavity passing axially through the rotor 10 and from there spreading over the sealing gaps 15 and 16 on the one hand and the sliding surfaces 17 and 18 on the other hand.
  • a lubricant channel lead in particular through the bearing section 11.
  • the lubricant passes through the centrifugal force acting on the rotating rotor 10 through the axial sliding gap of the sliding pair of sliding surfaces 17 and 18 in the chamber 4 and thereby ensures adequate lubrication of the sliding pair 17 and 18.
  • the lubricant passes through the central cavity of the Rotor 10 at the other end face and there also distributed supported by the centrifugal force radially outwards and provides for the lubrication of the sliding surfaces formed by the sliding surfaces 15 and 16 and also the sliding pairings formed with the wing 13.
  • the rotor 10 is provided in the side facing away from its drive side sliding surface 15 with pockets 20 in which the lubricant collects.
  • the pockets 20 may also be referred to as lubrication pockets.
  • a total of four pockets 20 are formed, in each case two pockets 20 on both sides of the wing 13.
  • the wing 13 divides the sliding surface 15 in two Gleit vomhemissphDC, by way of example and preferably the same further as also preferably shaped as circular ring segments.
  • the pockets 20 are uniformly distributed in the two hemispheres in the sense of a uniform distribution over the circumference of the lubricant.
  • the sliding surface 15 separates the pockets 20 in the circumferential direction from each other and limits them radially outward, so forms radially outward of the two slots 12 a circumferential sliding pair with the axially opposite sliding surface 16.
  • the pockets 20 are radially inwardly in the direction of the axis of rotation R. open, so open at an inner peripheral surface of the rotor 10.
  • the lubricant passes from the central cavity of the rotor 10 into the cavity opening into the pockets 20, accumulates in it and is supported in the operation of the pump by the centrifugal force radially outward to to lubricate the sliding pair of the sliding surfaces 15 and 16 and at the same time to seal the axial sliding gap formed between the sliding surfaces 15 and 16 and thus contribute to the fluidic separation of the delivery cells.
  • the sliding pair of sliding surfaces 17 and 18 also pockets, preferably inventive pockets, these may open radially into the said distribution groove and be supplied via this with the lubricant.
  • the pockets 20 pass respectively at their leading in the direction of rotation V end 23 along a curved in plan view of the sliding surface 15 Taschenö Stammsrand in the sliding surface 15, while they pass at their trailing end 24 each along a straight radial opening edge in the sliding surface 15.
  • the leading edge drops from a tangent to the edge with everywhere continuous curvature against the direction of rotation V in the direction of the trailing end 24 from. This smoothes the flow of the lubricant into the respective pocket 20, counteracts recirculation and the formation of dirt traps.
  • the circumferentially measured length L in each of the pockets 20 continuously decreases in the radial direction from inside to outside.
  • the pockets 20 are each shaped so that a hydrodynamic lubricant film builds up between the sliding surfaces 15 and 16 during operation of the pump as soon as the transition speed required for this purpose is exceeded.
  • the pockets 20 are shaped and arranged to exceed the transition speed in the wear-related operating conditions of the pump. Is the pump for a drive by a Internal combustion engine of a vehicle provided or mounted in the vehicle so, the design is preferably such that the transition speed is below the speed that reaches the rotor 10 when the engine is idling.
  • the pockets 20 each flat in the direction of their trailing end 24 continuously, so that they form with the axially opposite sliding surface 16 to a trailing end 24 tapered wedge gap.
  • the lubricant is due to the force acting in the lubricant upon rotation of the rotor 10 thrust forces at the trailing end 24 of each of the pockets 20 between the sliding surfaces 15 and 16 and forms there when the transition speed is exceeded, a bearing lubricating film, the sliding surfaces 15 and 16 separated from each other and in the axial sliding gap ensures pure fluid friction. Due to the inventive design of the sliding pair 15 and 16 with the pockets 20, a rotor 10 axially supporting axial plain bearing is created in combination with the axially flying or floating slide bearing of the rotor 10.
  • the sliding mating 15 and 16 with the pockets 20 is preferably further designed so that this thrust bearing also carries full and works at the transition speed is exceeded only in the field of fluid friction when it takes a stemming from the drive side at 11 axial force, an axial thrust must, as is the case in particular in preferred installation situations in which the vacuum pump is arranged on the housing or in a modification in the housing of an internal combustion engine of a motor vehicle.
  • FIG. 3 shows a plan view of the end face of a rotor 10, in the sliding surface 15 pockets 21 are formed according to a second embodiment.
  • the rotor 10 corresponds to the rotor 10 of Figures 1 and 2 and can replace it in the pump.
  • the pockets 21 are rectangular in the radial plane shown. They each pass both at the leading end 23 and at the trailing end 24 along a straight, approximately radially pointing opening edge into the sliding surface 15.
  • the two opening edges extend parallel to each other.
  • the circumferentially extending radially outer opening edge interconnecting the opening edges at the leading end 23 and trailing end 24 is an arc portion on a circle about the axis of rotation R, but could be simply straight, for example.
  • the pockets 21 are open at their radially inner side as in the first embodiment, thus open with their full pocket cross section on the inner circumferential surface of the rotor 10 in the central Cavity.
  • FIG. 3 are the dimensions of the opening edge, along which the respective pocket 21 merges into the sliding surface 15, registered.
  • the length measured in the circumferential direction is L and the width measured in the radial direction is designated B.
  • the length L is constant over the entire width B.
  • FIG. 4 is the sliding pair formed by the sliding surfaces 15 and 16 of the second embodiment in the in FIG. 3 registered section AA shown (without break edges).
  • FIG. 4 is the settlement of the circular cylindrical section AA.
  • the shape of the cross section of the pockets 21 can be seen.
  • FIG. 5 shows one of the pockets 21 in an enlarged view. D denotes the same pocket depth for all pockets 21, which is measured in the axial direction between the lowest point of the respective pocket 21, the pocket bottom, and the plane sliding surface 15 which extends radially to the axis of rotation R.
  • the pockets 21 rise from the bottom of the bag with the same constant inclination ⁇ in each case in the direction of the trailing end 24 of the respective pocket 21.
  • the inclination ⁇ is less than 30 °, in the embodiment, it is about 15 °.
  • the pockets 21 rise from the bottom of the bag into the sliding surface 15 steeply, in the embodiment as preferred with an inclination angle ⁇ of about 90 ° to the sliding surface 15.
  • the opening edge at the leading end 23 may be chamfered, with such a chamfer than for steeply rising pocket wall is expected.
  • the pockets 21 and the axially opposed sliding surface 16 define a substantially triangular wedge-shaped gap which tapers towards the trailing end of each pocket 21.
  • a modification to the first embodiment is thus that the pockets 21 have a different course at the leading end by being straight there and not, as is preferred, continuously falling against the direction of rotation V. Further, in the sliding surface 15, a larger number of the pockets 21 are formed as in the first embodiment. As in the first embodiment, the pockets 21 on both sides of an extending through the slot 12, imaginary dividing plane symmetrical and arranged distributed uniformly in the two hemispheres of the sliding surface 15 in the circumferential direction.
  • FIG. 6 shows an end view of a rotor 10, which has in the illustrated sliding surface 15 pockets 22 of a third embodiment, but otherwise the first and second Embodiment corresponds.
  • the pockets 22 have an undercut with respect to the radial direction, so that over a part of their circumferentially measured length L, which is correspondingly variable in the third embodiment, a web is obtained, which is part of the sliding surface 15, and one through the Undercut obtained projection 25 in each of the pockets 22 radially bounded in the direction of the axis of rotation R.
  • Each of the pockets 22 is extended by its extension 25 in the circumferential direction, namely as preferred against the direction of rotation V, ie at the trailing end.
  • the extensions 25 are each formed in the region of the radial center of the sliding surface 15.
  • the pockets 22 thus extend radially outward from their mouth into the central cavity of the rotor 10, first over a width region of shorter length L, and progressing radially outward into an outer region elongated by the extension 25, but as in the other embodiments bounded radially on the outside by a remaining there peripheral strip of the sliding surface 15 without interruption.
  • FIG. 7 shows the sliding pair of the sliding surfaces 15 and 16 in the development of Kxeiszylinderroughs BB of FIG. 6 (without break lines).
  • the pockets 22 form with the opposite sliding surface 16 each at the trailing end of a wedge gap by the pockets 22 rise from the respective pocket bottom with a constant inclination ⁇ to the trailing end 24 to the axial height of the sliding surface 15.
  • the wedge-shaped gap applies to the first and second embodiments.
  • the pockets 22 at the leading end 23 are modified relative to the second exemplary embodiment in that they rise there from the pocket bottom with a pronounced curvature into the chamber wall which is then again orthogonal to the sliding surface 15.
  • a chamfering advantageously present at the leading edge of the opening is again neglected, since it plays no role in terms of flow technology.
  • the wedge-shaped gap can, as shown by way of example, extend at the trailing end over the entire width B of the pockets 22 or, in a modification, only over the radial width of the respective extension 25. However, an extent over the entire radial width B is preferred.
  • the pockets 22 are seen in the radial plane at the leading end 23 are each continuously curved and fall as in the first embodiment in the direction of the trailing end 24 from a set to the opening edge of the front end 23 tangent. As in the first embodiment, the formation of dirt traps and recirculations are thereby prevented at the leading end.
  • nachzutragen still be that in the region of the circumferentially elongated extension 25 is a larger pocket length L than in the radially inner and narrower pocket area is available to form the wedge-shaped gap.
  • the pockets 22 can accordingly increase in the region of the respective extension 25 with a smaller inclination ⁇ in the direction of the trailing end 24, since the increase can be distributed over a greater length.
  • FIGS. 8 to 11 each show a development of a circular cylindrical sectional area in the manner of the sectional views of FIGS. 4 and 7 (each without break line). Shown are pockets that are modified with respect to their cross-section, ie their axial depth profile, compared to the second and the third embodiment.
  • the pockets are designated 26. They each rise from the pocket bottom in the direction of the trailing end 24 with a variable inclination ⁇ up to the sliding surface 15.
  • the leading ends 23 each correspond to the second embodiment, the local inclination ⁇ is again about 90 °, with a chamfer is neglected.
  • the wedge-gap-inducing rejuvenation sets like in the second embodiment, directly at the steep pocket wall of the leading end 23, thus extending over at least substantially the entire length L of the respective pocket 26.
  • the inclination ⁇ decreases continuously in the direction of the trailing end 24, so that the bottom of the Pockets 26 in each case continuously bulges around in the direction of the opposite sliding surface 16, in relation to the sliding surface 16 is thus formed round convex.
  • the inclination ⁇ is in the bag base between 40 and 60 °, but could well be up to 90 ° or less than 30 °. At the bottom of the bag could also be as in the third embodiment, a pronounced Kehlung be present.
  • the inclination ⁇ is at the trailing end 24 at the transition into the sliding surface 15 less than 15 °, in particular, the bottom of the pocket 26 can pass tangentially into the sliding surface 15, so the inclination ⁇ continuously decrease to the value "zero".
  • FIG. 9 shows pockets 27 of a fifth embodiment which differ substantially from the pockets of the other embodiments in that a wedge-shaped gap is also formed at the leading end 23 of each pocket 27.
  • the pockets 27 are symmetrical in the cross section shown with respect to the direction of rotation V and the opposite direction, ie the pockets 27 each rise from the pocket bottom in and against the direction of rotation V with the same inclination into the sliding surface 15.
  • the course of the inclination ⁇ thus corresponds to the course of the inclination ⁇ .
  • consistency is assumed for the inclinations ⁇ and ⁇ .
  • An advantage of forming a wedge gap with both the leading end 23 and the trailing end 24 is that the rotor 10 is rotationally invariant with respect to the formation of the hydrodynamic lubricating film, which may be advantageous for certain applications.
  • FIG. 10 shows pockets 28 of a sixth embodiment.
  • the wedge-shaped gap at the trailing end 24 only extends over approximately half the total length of each pocket 28 and only over one to two quarters of the pocket depth D. Seen in cross-section in this way in the region of the leading end 23 a pronounced Collection space for the lubricant and in the region of the trailing end 24 a smaller wedge gap than in the previous examples obtained.
  • FIG. 11 shows pockets 29 of a seventh embodiment.
  • the wedge gap is even flatter than in the pockets 28 of the sixth embodiment and also slightly longer.
  • the inclination ⁇ is correspondingly lower and in the wedge gap is less than 10 ° everywhere.
  • the wedge-shaped gap therefore extends over slightly more than half the length L and between one-sixth and one-fourth of the pocket depth D of the respective pocket 29.
  • the pockets 29 are also modified relative to the pockets 28 in the region of the leading end 23, where they have a pronounced Have Kehlung, which has approximately the shape of a semicircle, for example.
  • the bottom of the bag is formed by the trough-shaped groove and the subsequent wedge gap in the direction of the trailing end 24.
  • the chamber wall immediately at the leading end 23 corresponds to the third embodiment ( FIG. 7 ).
  • the pockets 20, 21 and 22 of the first, second and third embodiments may optionally have any of the different depth profiles, that is, each of the depth profiles may be combined with each of the pocket contour related to the radial direction and the circumferential direction.
  • wedge gaps at the leading end 23 and at the trailing end 24, as exemplified in FIG. 9 are also obtained with a variable inclination ⁇ and ⁇ , for example in the manner of the wedge gap of FIG. 8
  • the wedge column of the FIGS. 10 and 11 in the direction of the trailing end 24 a variable inclination ⁇ , for example, congruent to the embodiment of FIG. 8 exhibit.
  • the pockets 28 and 29 may also run out to the leading end 23 in a wedge-shaped gap, but a particularly large proportion of the sliding surface 15 would be claimed by the thus shaped pocket 28 or 29 by such a geometry in relation to the length of the respective wedge gap.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Reciprocating Pumps (AREA)

Claims (17)

  1. Pompe à piston rotatif, comportant :
    un carter (1) avec une chambre (4),
    un rotor (10) pouvant tourner dans la chambre (4) autour d'un axe de rotation (R), lequel rotor comporte, sur une face frontale, une surface de glissement (15) qui forme un appariement de glissement avec une surface de glissement (16) de la chambre (4),
    et au moins une poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) formée dans l'une des surfaces de glissement (15, 16) pour des lubrifiants, laquelle poche est délimitée par rapport à l'axe de rotation (R) dans une direction circonférentielle et radialement à l'extérieur de la surface de glissement (15) qui la contient,
    la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) étant formée de telle sorte qu'un film lubrifiant hydrodynamique se développe entre les surfaces de glissement (15, 16) lorsque le rotor (10) est en rotation, caractérisée en ce que
    la poche (20 ; 21 ; 22 ; 26 ; 27 ; 29) dans laquelle une direction circonférentielle par rapport à la surface de glissement (15) la contenant augmente avec une inclinaison (α) qui est plus petite qu'une inclinaison (β) avec laquelle la poche (20 ; 21 ; 22 ; 26 ; 27 ; 29) augmente dans l'autre direction circonférentielle par rapport à la surface de glissement (15) la contenant, et/ou
    la poche (22) a une extension (en 25) en vue dans une direction radiale par rapport à l'axe de rotation (R), à travers laquelle un tenon radialement à l'intérieur et délimitant la poche (22) est obtenu sur l'extrémité arrière (24), lequel tenon forme de préférence une partie de la surface de glissement (15).
  2. Pompe à piston rotatif selon la revendication précédente, caractérisée en ce que la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) forme un espace en coin avec la surface de glissement axialement opposée (16), lequel espace s'amincit en direction d'une extrémité (24) de la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) en arrière par rapport à un sens de rotation (V).
  3. Pompe à piston rotatif selon la revendication précédente, caractérisée en ce que l'espace en coin s'étend sur au moins un quart, de préférence sur la moitié ou une majeure partie de la longueur (L) de la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) mesurée dans la direction circonférentielle.
  4. Pompe à piston rotatif selon l'une des deux revendications précédentes, caractérisée en ce que l'espace en coin s'étend sur au moins un quart, de préférence sur au moins la moitié de la profondeur (D) de la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29).
  5. Pompe à piston rotatif selon l'une des trois revendications précédentes et présentant au moins l'une des caractéristiques suivantes :
    - la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) se termine dans la surface de glissement (15) contenant la poche avec une inclinaison (α) mesurée sur la surface de glissement (15) ≤ 45°, de préférence ≤ 30°,
    - la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) s'amincit sur au moins un sixième de la longueur de poche (L) mesurée dans la direction circonférentielle avec une inclinaison (α) mesurée sur la surface de glissement (15) ≤ 45°, de préférence ≤ 30°,
    - la porche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) s'amincit sur au moins la moitié de la profondeur de poche (D) avec une inclinaison (α) mesurée sur la surface de glissement (15) ≤ 45°, de préférence ≤ 30°.
  6. Pompe à piston rotatif selon l'une des quatre revendications précédentes, caractérisée en ce que l'espace en coin s'amincit sur au moins un sixième, de préférence sur au moins la moitié de la longueur (L) de la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) mesurée dans la direction circonférentielle par rapport à la surface de glissement (15) contenant la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) soit avec une inclinaison (α) constante, soit avec une inclinaison (α) qui diminue en continu.
  7. Pompe à piston rotatif selon l'une des revendications précédentes, caractérisée en ce que la poche (20 ; 21 ; 22 ; 26 ; 27 ; 29) augmente sur son côté à l'avant par rapport à un sens de rotation du rotor (10) perpendiculairement jusqu'à la surface de glissement (15) contenant la poche (20 ; 21 ; 22 ; 26 ; 27 ; 29), dans laquelle un chanfrein peut être présent lors de la transition vers la surface de glissement (15).
  8. Pompe à piston rotatif selon l'une des revendications précédentes, caractérisée en ce qu'une longueur (L) de la poche (20 ; 22) mesurée dans la direction circonférentielle varie sur la largeur radiale (B) de la poche (20 ; 22).
  9. Pompe à piston rotatif selon l'une des revendications 1 à 7, caractérisée en ce qu'une longueur (L) de la poche (21) mesurée dans la direction circonférentielle est constante sur toute la largeur radiale (B) de la poche (21).
  10. Pompe à piston rotatif selon l'une des revendications précédentes, caractérisée en ce que la poche (20 ; 22) comporte une extrémité (23) à l'avant par rapport à un sens de rotation (V) du rotor (10), laquelle extrémité diminue dans le sens de rotation (V) inverse dans une vue de dessus de la surface de glissement (15) contenant la poche (20 ; 22) radialement à l'extérieur d'une tangente radiale fictive à l'extrémité avant (23).
  11. Pompe à piston rotatif selon l'une des revendications précédentes, caractérisée en ce que la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) s'étend en direction de l'axe de rotation (R) jusque dans une surface circonférentielle intérieure du rotor (10).
  12. Pompe à piston rotatif selon l'une des revendications précédentes, caractérisée en ce que dans la surface de glissement (16) de la chambre (4), la seule poche ou plusieurs poches (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29), de préférence du même type, est ou sont formées et dans le cas uniquement d'une seule poche, cette poche unique, et dans le cas de plusieurs poches, toutes les poches de cette surface de glissement (16) sont agencées dans la direction circonférentielle de sorte qu'une position de basculement de l'axe de rotation (R) du rotor (10) connue à l'avance et résultant du fonctionnement de la pompe est contrecarrée.
  13. Pompe à piston rotatif selon l'une des revendications précédentes et présentant au moins l'une des caractéristiques suivantes :
    - la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) est formée dans la surface de glissement (15) du rotor (10),
    - la poche est formée dans la surface de glissement (16) de la chambre (4),
    - la poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) est formée dans la surface de glissement (15) du rotor (10) ou dans la surface de glissement (16) de la chambre (4), et dans l'autre surface de glissement est également formée au moins une poche qui correspond de préférence également à au moins une des revendications précédentes, dans laquelle la poche du rotor et la poche de la chambre sont radialement décalées l'une par rapport à l'autre, de sorte qu'elles ne peuvent pas se chevaucher au moins sensiblement lors de la rotation du rotor,
    - le rotor (10) comporte, sur son autre face avant, une surface de glissement supplémentaire (17) qui forme un appariement de glissement supplémentaire avec une surface de glissement supplémentaire (18) de la chambre (4), et dans au moins l'une des surfaces de glissement supplémentaires (17, 18) est formée au moins une poche supplémentaire (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) pour du lubrifiant de sorte qu'un film lubrifiant hydrodynamique se développe également entre les surfaces de glissement supplémentaires (17, 18) lors de la rotation du rotor (10), dans laquelle la au moins une poche supplémentaire (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) correspond également à l'une des revendications précédentes.
  14. Pompe à piston rotatif selon l'une des revendications précédentes, caractérisée en ce que dans au moins une des surfaces de glissement (15, 16, 17, 18), plusieurs poches (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) sont formées et sont espacées les unes des autres dans la direction circonférentielle ainsi que radialement à l'extérieur de la surface de glissement (15) les contenant, en ce que les poches (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) sont formées de sorte que le film lubrifiant hydrodynamique se développe entre la surface de glissement (15) contenant les poches (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) et la surface de glissement (16) axialement opposée, et en ce qu'au moins deux des poches (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) formées dans la même surface de glissement (15) correspondent à au moins l'une des revendications 2 à 13.
  15. Pompe à piston rotatif selon l'une des revendications précédentes, caractérisée en ce que le rotor (10) est axialement mobile en va-et-vient par rapport au carter (1) et est de préférence monté de manière axialement en porte-à-faux dans un palier à glissement radial (en 11).
  16. Pompe à piston rotatif selon l'une des revendications précédentes et présentant au moins l'une des caractéristiques suivantes :
    - la pompe à piston rotatif est une pompe à vide,
    - la pompe à piston rotatif est une pompe à palettes, de préférence une pompe à une seule palette,
    - la pompe à piston rotatif est intégrée ou prévue pour l'installation dans un véhicule et comporte de préférence une roue d'entraînement pour un entraînement en rotation du rotor (10) par un moteur à combustion du véhicule.
  17. Pompe à piston rotatif selon l'une des revendications précédentes et présentant l'une des caractères suivantes :
    - le rotor (10) est une pièce frittée, de préférence en acier fritté,
    - le rotor (10) est formé à partir de matière plastique, de préférence dans la pièce moulée par injection ou sous la forme d'une pièce frittée,
    - le rotor (10) est formé, sans outil, avec la au moins une poche (20 ; 21 ; 22 ; 26 ; 27 ; 28 ; 29) par un procédé de mise en forme, de préférence par un procédé de frittage ou un procédé de moulage par injection.
EP09166834.3A 2008-08-04 2009-07-30 Pompe à piston rotatif dotée de poches pour lubrifiants Not-in-force EP2151542B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810036273 DE102008036273B4 (de) 2008-08-04 2008-08-04 Rotationskolbenpumpe mit Taschen für Schmiermittel

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EP2151542A2 EP2151542A2 (fr) 2010-02-10
EP2151542A3 EP2151542A3 (fr) 2011-12-14
EP2151542B1 true EP2151542B1 (fr) 2015-07-08

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010028061A1 (de) * 2010-04-22 2011-10-27 Robert Bosch Gmbh Flügelzellenpumpe
DE102011018394A1 (de) 2011-04-21 2012-10-25 Daimler Ag Verdrängerpumpe eines Kraftfahrzeugs
DE102014102643A1 (de) 2014-02-27 2015-08-27 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit Kunststoffverbundstruktur
DE202014106121U1 (de) 2014-12-17 2015-01-15 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit kompakter Stellstruktur zur Verstellung des Fördervolumens
JP6382877B2 (ja) * 2016-03-24 2018-08-29 大豊工業株式会社 ベーンポンプ
CN109563740B (zh) * 2016-10-10 2021-07-27 威伯科欧洲有限责任公司 具有转子端凹槽的旋转真空泵
DE102017101142A1 (de) 2017-01-20 2018-07-26 Otto Altmann Wärmetauscher bzw. Wärmetauscheranordnung für eine Kühleinrichtung und eine Kühleinrichtung mit einem solchen Wärmetauscher
DE102017128787A1 (de) 2017-12-04 2019-06-06 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe
DE102022113977A1 (de) 2022-06-02 2023-12-07 Zf Cv Systems Europe Bv Pneumatisches Ventil und Verdichter

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GB2012874A (en) * 1977-12-07 1979-08-01 Seiko Instr & Electronics Rotary Positive-displacement Fluid-machines
JPS56106088A (en) * 1980-01-29 1981-08-24 Matsushita Electric Ind Co Ltd Rotary type fluid equipment
DE3014519A1 (de) * 1980-04-16 1981-10-22 Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt Drehkolbenmaschine, insbesondere zellenpumpe
JPH04279792A (ja) * 1991-03-08 1992-10-05 Toshiba Corp 流体圧縮機
DE3301098A1 (de) * 1983-01-14 1984-07-19 Knorr-Bremse GmbH, 8000 München Rotationskompressor
DE3325261A1 (de) * 1983-07-13 1985-01-24 Robert Bosch Gmbh, 7000 Stuttgart Vakuumpumpe
JPH1068393A (ja) * 1996-08-28 1998-03-10 Mikuni Corp バキュームポンプ
JP4229522B2 (ja) * 1999-05-24 2009-02-25 株式会社ショーワ 可変容量型ベーンポンプ

Also Published As

Publication number Publication date
DE102008036273B4 (de) 2013-09-26
DE102008036273A1 (de) 2010-02-11
EP2151542A2 (fr) 2010-02-10
EP2151542A3 (fr) 2011-12-14

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