EP3081744A1 - Pompe - Google Patents

Pompe Download PDF

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Publication number
EP3081744A1
EP3081744A1 EP16164901.7A EP16164901A EP3081744A1 EP 3081744 A1 EP3081744 A1 EP 3081744A1 EP 16164901 A EP16164901 A EP 16164901A EP 3081744 A1 EP3081744 A1 EP 3081744A1
Authority
EP
European Patent Office
Prior art keywords
housing part
pump
spring
rotation
rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16164901.7A
Other languages
German (de)
English (en)
Other versions
EP3081744B1 (fr
Inventor
Claus Welte
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 EP3081744A1 publication Critical patent/EP3081744A1/fr
Application granted granted Critical
Publication of EP3081744B1 publication Critical patent/EP3081744B1/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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3448—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member with axially movable vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/603—Centering; Aligning
    • 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
    • F04C2240/20—Rotors
    • 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
    • F04C2240/30—Casings or housings

Definitions

  • the invention relates to a pump, in particular a positive displacement pump for a liquid, such as oil.
  • the pump may be designed, for example, as a vane pump or rotary vane pump.
  • the pump is particularly suitable for installation in a vehicle, such as a motor vehicle and / or to supply a consumer in a motor vehicle.
  • the consumer may be, for example, an internal combustion engine, a transmission, such as a steering gear or automatic transmission.
  • a first aspect relates to the design or attachment of a spring of the pump.
  • a second aspect concerns the design of a shaft-hub connection of the pump.
  • a so-called cartridge pump which has a pump assembly consisting essentially of a rotor, a cam ring, a pressure plate, pressing pins and a spring element.
  • the rotor is rotatably received between the pressure plate and the side plate and is surrounded by the cam ring, which is also disposed between the pressure plate and the side plate.
  • Several pressing pins which are pressed axially into the pressure plate and penetrate the side plate and the cam ring, secure the pressure plate, the side plate and the cam ring rotationally and axially fixed to each other.
  • the spring element is fastened to the pressure plate.
  • the pump assembly can be inserted into a pot-shaped housing, wherein the spring element is supported on the bottom of the cup-shaped housing.
  • the housing is closed by a housing cover, which holds the pump unit in its installed position.
  • the rotor has an internal structure for a shaft-hub connection with a pump shaft.
  • the first aspect is the object of specifying a cost-producible and space-saving pump.
  • the second aspect is the object of reducing wear in the pump.
  • the invention is based on a pump, in particular displacement pump, such as vane or rotary vane pump.
  • the pump comprises a housing which encloses a pump space.
  • a rotor may be rotatably disposed about an axis of rotation relative to the housing.
  • the pump may comprise the rotor and at least one first housing part, in particular a first housing cover, and a second housing part, in particular a second housing cover, between which the rotor is rotatable about an axis of rotation relative to the first and second housing part.
  • the rotor may be directly or indirectly torque-transmitting connected to a pump shaft or be connectable, such as via a shaft-hub connection, in particular according to the second aspect.
  • the rotor When the pump shaft is rotated relative to the first and second housing parts, the rotor rotates.
  • the rotor has recesses, in particular guides, in which conveying elements, such as, for example, vanes, slides or rollers, are movable, in particular displaceable, radially in relation to the axis of rotation.
  • the conveying elements are received or supported by the rotor so that they rotate with the rotor about its axis of rotation.
  • the pump shaft may extend through the housing and be rotatably supported about the axis of rotation on the housing, such as with a first portion on the first housing part and with a second portion on the second housing part.
  • An outer structure for the shaft-hub connection can be formed between the first section and the second section of the pump shaft.
  • the rotor and the pump shaft can be rotationally connected by means of a straight-toothed shaft-hub connection.
  • the shaft-hub connection has an internal toothing with a plurality of teeth and engaging in the internal toothing external toothing with a plurality of teeth.
  • a third housing part in particular a cam ring, can be arranged, which surrounds the rotor over its circumference.
  • the ring-shaped third housing part may be a separate part from the first and second housing part.
  • the third housing part may be a section of the first housing part formed by the first housing part or may be a section of the second housing part formed by the second housing part.
  • the first housing part or the second housing part or both can surround the rotor and in particular its conveying elements, for example surrounded in a ring shape.
  • the first housing part, the second housing part and the third housing part enclose and define a pump chamber in which the rotor and the conveying elements are arranged.
  • a conveyor cell is formed which is circumferentially bounded by an inner peripheral surface of the third housing part and along the axis of rotation of the first housing part on one side and of the second housing part on the other side and whose volume is a function of the rotational position of the rotor changed around its axis of rotation.
  • the pump has a plurality of conveying elements and thus a particular same plurality of conveying cells, which are formed between the conveying elements.
  • the inner circumference of the third housing part has a contour along which the conveying elements slide during a rotation of the rotor.
  • the contour is designed such that the volumes of the delivery cells moving through the delivery chamber due to the rotation of the rotor first increase and then decrease.
  • the conveying elements are at least once away from the axis of rotation and moved to the axis of rotation.
  • the pump may, for example, be double-stroke, ie with a first delivery chamber and a second delivery chamber, which are each traversed once by the delivery elements or the delivery cells in one complete revolution. This means that the conveying elements in a full turn alternately twice away from the axis of rotation and twice to the axis of rotation to be moved.
  • the pump may have a first channel, which opens into the region of the delivery chamber, in which the volume increase takes place and have a second channel, which opens into the region of the delivery chamber, in which the reduction in volume of this delivery cell takes place. Due to the increase in volume of the delivery cell, the first channel acts as a suction channel. Due to the volume reduction, the second channel acts as a pressure channel.
  • a multi-stroke pump may have multiple suction channels and multiple pressure channels. In a double-stroke pump, two pressure channels and two suction channels can be provided. A first suction channel can open into the first delivery chamber and a second suction channel can open into the second delivery chamber. A first pressure channel can open into the first delivery chamber and a second pressure channel can open into the second delivery chamber.
  • the conveying elements and / or the rotor each form a sealing gap with the first housing part and the second housing part.
  • the at least one suction channel may be connected to a fluid reservoir, such as an oil reservoir, in particular in fluid communication.
  • the at least one pressure channel may be connected to at least one fluid consumer, such as being in fluid communication with a transmission.
  • the pump may have at least one positioning element, which positions the second housing part with respect to its angular position about the axis of rotation relative to the first housing part.
  • the at least one positioning element may be formed by the first housing part, in particular be formed in one piece or monolithic.
  • the at least one positioning element may be formed as a separate part from the first housing part, which is anchored in the first housing part.
  • the positioning can be screwed or pressed into the first housing part, ie positive and / or non-positive, anchored.
  • the at least one positioning element can be firmly anchored in the first housing part, for example adhesively bonded, soldered or welded.
  • the first housing part can have a bore for each positioning element, in which one end of the positioning element is inserted and thereby anchored in the first housing part.
  • the at least one positioning element may in particular be pin-shaped or cylindrical.
  • the end of the positioning member opposite the anchored end may have the same outer diameter as the anchored end.
  • the second housing part and in particular also the third housing part, can be mounted on the at least one positioning element so as to be secured against rotation about the axis of rotation.
  • the at least one positioning element may extend through a recess provided for each positioning element of the second housing part, such as through a bore or through hole.
  • the at least one positioning element may extend, for example, through a recess of the third housing part, the z. B. may be formed as a bore, slot or the like.
  • the at least one positioning element with its end which is opposite the end anchored in the first housing part, protrude from the second housing part, in particular protrude from the end face of the second housing part, which faces the end face facing the rotor, or which faces an end wall a receiving housing has.
  • the pump may include a spring, such as a diaphragm spring.
  • the second housing part may be arranged between the spring and the rotor.
  • the spring may be supported, for example, on the second housing part and on a receiving housing, in particular an end wall of the receiving housing.
  • the receiving housing may be cup-shaped, for example.
  • the receiving housing may have a peripheral wall which extends around the axis of rotation of the rotor and an end wall arranged on the front side of the peripheral wall, the second housing part being surrounded by the peripheral wall over its circumference and the spring, such as a main portion of the spring, is supported on the front wall.
  • the spring seeks to push away the second housing part from the end wall of the receiving housing.
  • the spring can be fastened to the at least one positioning element.
  • the spring may, for example, be positively connected to the positioning element, in particular snapped or frictionally connected, so that the spring is held on the at least one positioning element and preferably supported or supported on the second housing part. It is preferred that the spring is secured against rotation about the rotational axis, in particular in a positive or / and force-locking manner, to which at least one positioning element is attached.
  • the spring may be attached to the second housing part, such as a form-fitting manner.
  • the spring may have a main portion that can spring away along the axis of rotation toward the first housing part and away from the first housing part.
  • the spring may have a support portion which is connected to the main portion, wherein between the second housing part and the main portion of the spring gap.
  • the at least one support section may, for example, be supported in a planar manner on the second housing part.
  • the main section is particularly intended to be on the end wall of the receiving housing, in particular on a z. B. annular projection of the end wall, z. B. support surface.
  • At least a part of the main section may be arranged between the rotation axis and the at least one support section.
  • the main portion is caused to be closer to the rotation axis than the at least one support portion.
  • the main portion may be annular, wherein a plurality of support portions protrude from the main portion, in particular one per each positioning.
  • the main section may be offset relative to the at least one support section along the axis of rotation.
  • the main portion of the spring may have a recess, in particular a e.g. Have circular breakthrough, through which the pump shaft and / or the pump shaft bearing forming structure of the second housing part extends.
  • the structure forming the pump shaft bearing can be a ring structure integrally formed on the second housing part, which protrudes from the second housing part to the end wall of the receiving housing. As a result, a large support surface for the pump shaft and the thickness of the second housing part remain otherwise low.
  • the spring may have or form at least one fastening element, in particular on or in the region of the supporting section.
  • the at least one fastening element can serve as a support section or a fastening element can be provided for each support section.
  • the spring can be fastened or fastened to the at least one positioning element or the second housing part.
  • the fastening element which is configured, for example, for a positive connection with the fastening element, can be snapped with the at least one positioning element.
  • the at least one positioning element may have a recess, such as an annular groove over its circumference, in which engages the at least one fastening element of the spring.
  • a recess such as an annular groove over its circumference, in which engages the at least one fastening element of the spring.
  • Such an annular groove may be formed as a recess.
  • the at least one fastening element can be designed in the form of a fuse disk or a serrated ring, similar to lock washers according to DIN 6799 or retaining rings for shafts according to DIN 471, in particular with the difference that they are formed by the spring, namely can be formed on the support section.
  • the securing element in particular the lock washer configured according to DIN 6799, for example, or the snap ring configured according to DIN 471, may actually be a disk or a ring, ie not formed on the spring and serving, for example, only axially not removable from the positioning element.
  • the spring on the second Housing part or the fuse element attached or enclosed between the fuse element and the second housing part, wherein the fastening element of the spring may be attached to the positioning.
  • the positioning element can be configured, for example, with a head, wherein the second housing part is enclosed between the first housing part and the head, so that the second housing part can be prevented from being pulled off the first housing part or from the positioning element.
  • the spring may be attached to the second housing part or to the head or enclosed between the head and the second housing part, wherein the fastening element of the spring may be attached to the positioning element.
  • the recess can be an annular groove extending over the circumference of the cylindrical or pin-shaped positioning element, which has a width extending along the longitudinal axis of the positioning element, which is dimensioned such that the fastening element of the spring interacts with the longitudinal axis in the annular groove is included. In this way it can be ensured that the support section or the fastening section of the spring is supported on the second housing part and not on a groove flank of the annular groove.
  • the pump may have a pump shaft which is rotationally connected to the rotor and rotatable about the axis of rotation.
  • the pump shaft may be rotatably mounted at least in the first housing part.
  • the pump shaft may be rotatably mounted in the second housing part, in particular in a bag-shaped recess or in a continuous recess, in particular bore, through the second housing part.
  • the bag-shaped recess has the advantage that the pump chamber is sealed to the side facing away from the pump chamber end face of the second housing part.
  • the through recess has the advantage that it is easier to manufacture and ensures greater stability.
  • the bearing or bearings can be sliding or roller bearings.
  • the pump shaft has a structure, in particular an outer toothing, for a shaft-hub connection with the rotor.
  • the diameter of the structure may be greater than the inner diameter of the first housing part and / or the second housing part or the bearing be. The structure is thus enclosed between the first housing part and the second housing part along the axis of rotation. This will cause the shaft can not be pulled out of the fully assembled pump assembly.
  • the shaft-hub connection can be configured so that the pump shaft with its axis of rotation with respect to the axis of rotation of the rotor by a small angle, d. H. tiltable by a maximum of a few degrees, in particular is pivotable.
  • the axis of rotation of the rotor and the axis of rotation of the pump shaft are congruent.
  • the second housing part can be positioned relative to the first housing part. In this case, minimal errors may occur, which cause the axis of rotation of the pump shaft is slightly inclined with respect to the axis of rotation of the rotor.
  • the teeth or each tooth of the inner and / or outer toothing can each be elongated and extend with its longitudinal direction along the axis of rotation, in particular parallel to the axis of rotation.
  • the teeth may be distributed over the outer circumference of the shaft or the inner circumference of the rotor.
  • the teeth or each tooth of the internal toothing of the shaft-hub connection which may be formed, for example, by the rotor or by an intermediate part rotatably connected to the rotor, can each extend over their length along the longitudinal axis of the rotor to a convex axis of rotation of the rotor have curved head surface.
  • the head surface may be curved one or two-dimensionally.
  • the teeth or every tooth of the External toothing of the pump shaft can have a convexly curved head surface curved away from the axis of rotation of the pump shaft via its length along the longitudinal axis of the rotor.
  • the head surface is the surface formed between the flanks of a tooth which forms the free end of the tooth.
  • the convexly curved head surface may consist of a round curved surface or be formed of a plurality of surface portions, such as flat or planar surface portions which abut each other and are angled to each other to form a convexly curved head surface.
  • the inner and / or outer teeth or any tooth thereof may have a first end and a second end along the axis of rotation of the rotor or the pump shaft.
  • One or each tooth may have a tooth height that decreases from a region between the first end and the second end to at least one of the first end and the second end. For example, in the region of the middle between the first and second end of a tooth, the tooth height may be greatest, decreasing toward the first and / or second end.
  • the first and second ends of the tooth may be faceted, with the facet not counting toward the head surface.
  • a facet is usually mounted at an angle of 30 ° or 45 °, with the tangent to the convexly curved head surface or the plane such as a plane.
  • the first or second surface portion, the convexly curved head surface is inclined with, for example, a maximum of an angle of 3 °, in particular at most 1 °, with respect to the axis of rotation of the rotor or the pump shaft.
  • the tooth height may be progressive towards the first or second end, i. H. with an increasing slope, or linear, i. with constant slope, decrease.
  • the respective tooth height can be formed between a tooth root and the head surface of each tooth.
  • the head surface may be crowned between the first end and the second end.
  • the top surface of the respective tooth may be at least partially planar between the first end and the second end, wherein the plane surface portion with respect to the Rotary axis is inclined or parallel.
  • the planar surface portion disposed approximately midway between the first and second ends may be parallel to the axis of rotation.
  • the head surface may have a first surface portion and a second surface portion, wherein the second surface portion between the first surface portion and the first end is arranged, wherein the tooth height in the first surface portion is constant and decreases in the second surface portion toward the first end.
  • the head surface may further include a third surface portion, the third surface portion disposed between the first surface portion and the second end, the tooth height decreasing in the third surface portion toward the second end.
  • the teeth of the internal toothing and / or the external toothing may have a convexly curved first tooth flank surface and / or a convexly curved second tooth flank surface over their length along the axis of rotation.
  • the curved tooth flank surface may consist of a round curved surface or be formed of a plurality of surface portions, such as flat or planar surface portions which abut each other and are angled to each other to form a convexly curved tooth flank surface.
  • the or each tooth of the internal toothing and / or the external toothing has a tooth width between the first and second tooth flank surfaces.
  • the tooth width decreases from a region between the first end and the second end toward at least one of the first end and the second end, preferably towards both ends.
  • the tooth width may be progressive towards the first or second end, i. H. with an increasing slope of the tangent to the first or second tooth flank surface, or decrease linearly.
  • the first and / or the second tooth flank can be spherical.
  • the first tooth flank or the second tooth flank is at least equidistantly planar between the first end and the second end, wherein the planar surface section is inclined or parallel with respect to the axis of rotation.
  • the first and / or the second tooth flank surface may have a first surface portion and a second surface portion, wherein the second surface portion is disposed between the first surface portion and the first end, wherein the tooth width in the first surface portion is constant and decreases in the second surface portion toward the first end.
  • the first and / or second tooth flank may each have a third surface portion, wherein the third surface portion is disposed between the first surface portion and the second end, wherein the tooth width decreases in the third surface portion towards the second end.
  • the first housing part, the second housing part, the third housing part, the rotor, the conveying elements, the positioning elements, the spring and the pump shaft essentially form a pump assembly which can be handled as a unit. Because the spring is fastened to the at least one positioning element, the assembly can be prevented from falling apart. The fastening portions of the spring or the fuse elements separate from the spring cause an axial shaft securing, so that the pump assembly does not fall apart.
  • the receiving housing which can be formed for example by a transmission housing for a motor vehicle, or be inserted into the receiving housing, for example via an opening of the receiving housing opposite the end wall.
  • the axial securing element may, for example, be annular and be inserted in an annular groove which is formed on the preferably cylindrical inner circumference of the receiving housing.
  • the axial securing element may be formed by a cover which closes the opening at least partially or completely.
  • a seal may be arranged, which has a first space which is formed between the end wall and the second housing part in Seal with respect to a second space formed between the peripheral wall and the first and / or third housing part, seal.
  • the first space may be connected by means of the first channel to the pump chamber in which the rotor is arranged.
  • the second space may be connected to the pumping chamber by means of the second channel.
  • the first space can be arranged on the suction side and the second space on the pressure side or the second space on the suction side and the first space on the pressure side.
  • the pressure space between the end wall and the second housing part may be formed, wherein the suction space between the peripheral wall and the first / and third or third housing part may be formed.
  • the suction chamber may be connected to the at least one suction channel with the at least one delivery chamber.
  • the pressure chamber may be connected to the at least one pressure channel with the at least one delivery chamber.
  • the peripheral wall may be arranged an additional seal, wherein the second space between the first and second seal is arranged.
  • the second seal may effect the sealing of the second space outwardly or to the opening of the receptacle housing.
  • the axial securing element is only slightly loaded with an axial force during the pumping operation.
  • the spring force is at least so strong to choose that parts of the pump assembly are at least as strong compressed along the axis of rotation that the pump chamber is sufficiently sealed.
  • the second housing part acts like a piston which increases the pressure along the axis of rotation on the Axiatschungselement with pressure increase and thus the parts of the pump assembly sealingly pressed together with an increasing force increasing delivery pressure.
  • the spring may be formed of metal, such as spring steel.
  • the spring may comprise a plastic, such as an elastomer or polymer material.
  • the spring may for example be made of an elastomer or Polymer material may be formed or formed from a partially or completely coated with the plastic, such as overmolded, metal spring. This has the advantage that the spring can fulfill a dual function as a seal.
  • the end wall may have a Abragung or a sealing seat against which the spring is sealingly supported, in particular with the surface of the spring formed from the plastic.
  • the second housing part may have a sealing seat on which the spring, in particular with the surface formed from the plastic sealingly supported.
  • the spring formed as a seal may e.g. a first part of the pressure chamber, in which the first outlet channel opens, with respect to a second part of the pressure chamber, in which opens the second outlet channel, seal. This can provide a pump with two pressure levels.
  • the spring formed as a seal may e.g. the pressure chamber into which the first and possibly the second outlet channel open, with respect to the suction chamber, in which the first and possibly the second inlet channel open, seal.
  • FIG. 1 shows a pump assembly, which in a receiving housing 20, as in FIG. 2 shown, can be used.
  • the pump assembly comprises an example designed as a plate spring spring 5, which in the FIGS. 4 to 10 in various embodiments.
  • FIG. 1 has a rotor 4, which is rotationally connected via a shaft-hub connection 30 with a pump shaft 10 of the pump 1.
  • the rotor 4 has serving as a guide, in particular slot-shaped recesses.
  • Each recess is a conveying element 13, in particular a wing assigned.
  • the wing 13 is in its recess radially or away from the axis of rotation of the rotor 4 and out to the axis of rotation of the rotor 4, in particular guided with a single translational degree of freedom, displaced back and forth, as best of FIG. 15 is recognizable.
  • the wings 13 are rotated with the rotor 4.
  • the pump 1 has an annular housing part 12, which for better identification referred to as the third housing part 12 can be.
  • the third housing part 12 may be designed as a lifting ring.
  • the third housing part 12 is enclosed between a first housing part 2 and a second housing part 3 and rotationally fixed with respect to the first and second housing part 2, 3.
  • the ring extending around the pump shaft 10 space, which is surrounded by the inner circumference of the third housing part 12 and axially bounded by the second and third housing part 2, 3, may also be referred to as the pump chamber 26.
  • the rotor 4 and the wings 13 are arranged in the pump chamber 26.
  • At least one delivery chamber 27, 28 is formed radially between the rotor 4 and the third housing part 12.
  • the embodiment shown here comprises two delivery chambers, namely a first delivery chamber 27 and a second delivery chamber 28.
  • a conveyor cell 29 is formed in each case, whose volume changes in dependence on the rotational position of the rotor 4 about its axis of rotation. Since the pump has a plurality of wings 13, it also has a plurality of conveyor cells 29 correspondingly. In each of the delivery chambers 27, 28 there are a plurality of delivery cells.
  • the vanes 13 and the rotor 4 form a first sealing gap with the first housing part 2 and a second sealing gap with the second housing part 3.
  • the third housing part 12, in particular the lifting ring, and / or the wings 13 may be magnetized, so that the wings 13 abut due to magnetic force on the inner peripheral surface of the third housing part 12, especially even if the rotor 4 is not rotating. This allows an early build up of pressure at startup or cold start, ie, when the pump shaft 10 starts to rotate.
  • the wings 13 due to the centrifugal force in the rotation of the rotor 4 to the outside, that are pressed away from the axis of rotation of the rotor 4 against the inner peripheral surface of the third housing part 12.
  • the wings 13 and each of the wings 13 forms with the inner peripheral surface of the third housing part 12, a third sealing gap.
  • the inner circumferential surface of the third housing part 12 has a contour which causes the wings 13 to extend at least once during one complete revolution of the rotor 4 (increase in volume of the conveyor cell 29) and retract once (volume reduction of the conveyor cell 29).
  • the pump 1 shown in the example is double-stroke, d. H. with two delivery chambers 27, 28, wherein the wings 13 per delivery chamber 27, 28 extend once and retract once when they are moved by rotation of the rotor 4 through the delivery chamber 27, 28.
  • the blades 13 are caused to extend, retract, extend and retract in one full turn of the rotor 4, or in other words, extend twice and retract twice.
  • a conveyor cell 29 is formed in each case whose volume is increased or reduced by the extension and retraction of this conveyor cell 29 delimiting wings 13, namely in dependence on the contour of the inner circumferential surface of the third housing part 12th
  • the pump 1 has an opening or a channel 3b, which opens into the region of the delivery chamber 27, 28, in which the volume of the delivery cells 29 decreases during the rotation of the rotor 4. This causes fluid in the delivery cells, such as oil, to be displaced through the channel 3b, which serves as an outlet.
  • the pump 1 has an opening or a channel 2b which opens into the region of the delivery chamber 27, 28, in which the volume of the delivery cells 29 increases during the rotation of the rotor 4. As a result, fluid is conveyed or sucked through the channel 2b into the increasing delivery cell 29. Since the pump 1 is two-stroke in this example, it has two inlet channels 2b and two outlet channels 3b, wherein the first inlet channel 2b and the first outlet channel 3b into the first delivery chamber 27 and the second inlet channel 2b and the second outlet channel 3b in the second delivery chamber lead. A reverse configuration of the inlet and outlet channels 2b, 3b is also conceivable. That is, the passage 2b may be the outlet passage and the passage 3b may be the inlet passage.
  • the pump 1 comprises at least one positioning element 6, in the example shown two positioning elements 6.
  • the positioning elements 6 are pins or pin-shaped.
  • the positioning element 6 is firmly anchored in the first housing part 2.
  • the first housing part 2 has a blind bore 2a into which the pin-shaped positioning element 6 is pressed with a first end.
  • the pin-shaped positioning 6 positions the second housing part 3 and the third housing part 12 with respect to their angular positions about the axis of rotation relative to the first housing part 2.
  • the second housing part 3 and the third housing part 12 have recesses, openings, holes or slots, preferably with a radial extent , on, through which the positioning element 6 extends.
  • the third housing part 12 for this purpose has a recess.
  • the second housing part 3 has a through hole through which the positioning element 6 extends.
  • the positioning element 6 protrudes with its pin-shaped second end over the end face, which faces away from the pump chamber 26.
  • This protruding portion of the positioning member 6 has a recess, such as an annular groove 6 a, or at least a part thereof, which extends over the circumference of the positioning member 6.
  • a securing element or fastening element 5a is arranged, which is in particular non-positively and / or positively secured to the positioning element 6 and in the annular groove 6a.
  • the fastening element 5a prevents the first housing part 2, the second housing part 3 and the third housing part 12 from falling apart axially, or in other words pulling off the second and third housing parts 3, 12 from the positioning element.
  • the spring 5 may be configured, for example, as a plate spring, as a star wheel or with geometries of a star wheel or as a wave spring or with structures of a corrugated spring. In the example with a plate spring, this may have a main portion 5c, which is connected via an arm with the fastening element 5a. In the example shown, the (disk) spring 5 has two fastening elements 5a, which are each connected to the main section 5c via an arm 5b. The fastener 5 prevents for a, that the housing parts 2, 3, 12 detach from each other, and on the other hand allows attachment of the spring 5 to the pump unit or on the positioning element 6.
  • the main portion 5c of the spring 5 is offset along the axis of rotation of the rotor 4 or the pump shaft 10 to the fastener 5a or arranged to a support portion 5d.
  • the attachment portion 5a and / or the second housing part 3 facing support portion 5d are applied to the second housing part 3 or based on it.
  • the attachment portion and / or the support portion 5d lie as flat as possible on at least one correspondingly formed, preferably flat surface of the second housing part 3.
  • the main section 5c is spaced from the second housing part 3 with a gap or spring gap.
  • the main portion 5 c can thus spring to the second housing part 3, whereby the spring 5 is tensioned, and spring away from the second housing part 3, whereby the spring is relaxed.
  • the main section may preferably lie as flat as possible against at least one surface or flat surface formed by a substantially annular shoulder of the end wall 5c.
  • the spring 5 - taking into account the stiffness / stress or the spring diagram (force-displacement characteristic) of the spring 5 - as possible flat on the second housing part 3 and the receiving housing, in particular on the end wall or the at least one surface the substantially annular shoulder rests.
  • the main portion 5c of the spring 5 has a particular circular opening 5e, through which a portion of the second housing part 3 extends.
  • the spring 5 may comprise or be a metal spring, which may optionally be at least partially or completely coated, overmolded or provided with molded-on geometries, with a plastic material, in particular an elastomer or a material whose main component is an elastomer. Due to the coating, encapsulation or molded geometries, the spring 5 can take on an additional function as a seal.
  • the pump shaft 10 is rotatably mounted on the first and second housing part 2, 3, in particular by means of a respective sliding bearing.
  • an outer structure such as an external toothing on the pump shaft 10 is formed with a corresponding internal structure, in particular internal toothing of the rotor 4 in a form-locking engagement, in order to effect a shaft-hub connection 30.
  • the outer diameter of the outer structure of the pump shaft 10 is greater than the diameter of the portion of the pump shaft 10 which is mounted in the first housing part 2 and / or in the second housing part 3.
  • the pump shaft 10 is axially fixed between the first and second housing parts 2, 3, i. that a displacement of the pump shaft 10 along the axis of rotation in both directions is substantially not possible.
  • the inner diameter of the portions of the first housing part 2 and the second housing part 3, which support the pump shaft 10 smaller than the outer diameter of the outer structure of the pump shaft 10th
  • the first housing part 2 has on its front side facing away from the pump chamber an annular pocket in which a shaft seal 11 is arranged.
  • the shaft seal 11 is rotatably attached to the first housing part 2 and forms a sealing gap with the pump shaft 10.
  • the shaft seal 11 seals the pump chamber to the outside.
  • the end of the pump shaft 10, which is opposite to the end, which is arranged in the region of the spring 5, has an outer structure for a shaft-hub connection with a gear 21, in particular a sprocket.
  • the gear 21 is rotationally fixed on the pump shaft 10.
  • the gear 21 may be driven by a chain which in turn is driven by, for example, a crankshaft or other shaft which may be connected to, for example, an engine of the vehicle.
  • the gear 21 has for its attachment to the pump shaft 10 has an internal thread, with which it is screwed with an external thread of the pump shaft 10 against a shoulder of the pump shaft 10.
  • a non-rotating seated on the shaft 10 against rotation 22 secures the gear 21 against unintentional release.
  • the rotation lock 22 has an angled portion which engages positively in the gear 21, whereby a release of the gear 21 is prevented.
  • the pump unit off FIG. 1 is inserted into a cup-shaped receptacle housing 20, such as a housing pot, for example ( FIG. 2 ).
  • the receiving housing 20 has a peripheral wall 20 d, which the pump unit 1 from FIG. 1 surrounds circumferentially. Further, the receiving housing 20 has an end wall 20c, which is connected to the peripheral wall 20d, wherein the spring 5 is supported with its main portion 5c on the end wall 20c, in particular on an example annular projection 20a of the end wall 20c.
  • the pump unit off FIG. 1 is held between the end wall 20c and an axial securing element 9, in particular an axial securing ring, which is arranged in an annular groove 20b of the circumferential housing 20, so that the spring 5 is tensioned.
  • a first space 23 pressure space
  • the space 23 is in turn connected by means of a channel (not shown) to a fluid consumer, such as a lubricant consumer, in particular a transmission.
  • a second space 24 suction space
  • the space 24 may, for example, be connected by means of a channel to a reservoir for the fluid.
  • the pressure in the space 23 is increased with increasing speed, whereby the second housing part 3 in addition to the biasing force of the spring 5, the third housing part 12 firmly clamped between the first and second housing part 2, 3.
  • the first, the second and the third housing part 2, 3, 12 are sealed to each other.
  • the connection between the Axialommeselement 9 and the first housing part 2 is formed so strong that it can withstand the axial force on the axial securing element 9, which is caused by the pressure in the space 23, that is not solved.
  • a housing cover can be fastened to the receiving housing 20 be, on which the first housing part 2 is axially supported.
  • spring 5 is in FIG. 4 shown.
  • the spring off FIG. 8 resembles the spring FIG. 4 ,
  • the fastener 5a of the spring 5 from the FIGS. 4 and 8th has two legs, which are arranged in the recess 6a.
  • the spring 5 can be fixed to the positioning elements 6 by rotation about the axis of rotation of the rotor 4 by means of its fastening elements 5a.
  • the legs each have two mutually facing guideways 5g, which are arranged to each other so that the clear width formed between them increases towards the free end of the legs out.
  • the thickness of the limbs is smaller than the clear width between the groove flanks of the recess 6a of the positioning element 6.
  • the section of the reduced core diameter in the recess 6a ie the diameter of the positioning element 6 measured at the groove base, is frictionally enclosed between the two limbs of the fastening element 5a .
  • the legs widen elastically slightly by sliding the mutually facing sliding surfaces 5g at the reduced diameter portion of the recess 6a.
  • the legs then engage with the reduced diameter section.
  • In support of the legs may each have a concave curved recess surface 5h.
  • the depression surfaces 5h may preferably rest flatly on the reduced-diameter section when the fastening element 5a is completely arranged in the recess 6a.
  • the fixing member 5a has a projection which has a stopper surface which can abut against the reduced diameter portion of the positioning member 6 when the fixing member 5a is completely disposed in the recess 6a.
  • the in the FIGS. 5 and 6 illustrated fasteners 5a are similar.
  • the fastening element 5a is closed annularly and has on its inner circumference 3 projections which enclose a diameter which is larger than the section of reduced diameter in the recess 6a and smaller than the outer diameter of the pin-shaped positioning element 6.
  • the fastening element 5a FIG. 5 points to his three Abragened facets or bevels on which the embodiment of FIG. 6 does not have.
  • the fastening elements 5a are pushed axially over in each case one positioning element 6 until the three projections of the fastening element 5a engage in the recess 6a.
  • the thickness of the fastener 5a is smaller than the clear width between the groove flanks of the recess 6a.
  • FIG. 7 shows a fastener 5a, which outwardly, ie pointing away from the axis of rotation, a recess 5f.
  • the spring 5 off FIG. 7 can be fixed by means of rotation about the axis of rotation of the positioning elements 6.
  • the two fastening elements 5a each have a single free end, which is located farther than the recess 5f relative to the arm 5b.
  • the free end in particular a sliding surface 5g of the free end pointing away from the axis of rotation, which slides on the positioning element 6 during fastening of the spring 5, is farther removed than the depression 5f with respect to the axis of rotation, in particular a recess surface 5h of the depression facing away from the axis of rotation 5f, arranged.
  • this embodiment When fastening, this embodiment causes the free end of the positioning element 6 is deflected by the sliding surface 5g slides on the positioning member 6, and the recess in the recess 6a springs. This results in a positive connection.
  • the thickness of the fastener 6 is as in the other embodiments of the FIGS. 4 to 10 also smaller than the clear width between the groove flanks of the recess 6a.
  • FIG. 9 shows an embodiment with a closed annular fastener 5a.
  • the annular fastening element 5a forms on its inner ring side a contour with a first diameter section 5a 1 and a second diameter section 5a 2 , which are connected via a tapering section 5a 3 .
  • the first diameter section 5a 1 has an inner diameter that is larger than the outer diameter of the positioning element 6.
  • the second diameter section 5a 2 has an inner diameter which is smaller than the outer diameter of the positioning element 6 and larger than the diameter of the positioning element 6 in the recess 6a.
  • the clear dimension between the flanks of the tapering section 5a 3 is smaller, in particular only slightly smaller than the diameter of the positioning element 6a in the recess 6a.
  • the first Diameter section 5a 1 of the fastener 5a is placed on the positioning element 6.
  • the fastener 5a is pivoted with the second diameter portion 5a 2 in the recess 6a, thereby the tapered portion at the reduced diameter portion in the recess 6a resiliently widens and contracts again when it has been moved past the portion of reduced diameter ,
  • the spring 5 off FIG. 10 shows at least one fastening element 5a, which is designed hook-shaped, wherein a hook-shaped portion by a dimension greater than 180 ° to a receiving portion 5a 4 extends.
  • a taper portion 5a 3 whose clear distance is smaller than the diameter of the receiving portion 5a 4th
  • the diameter of the receiving portion 5a 4 is greater than the diameter of the positioning element 6 in the recess 6a and smaller than the outer diameter of the positioning element 6.
  • the clear dimension between the flanks of the taper portion 5a 3 is smaller, in particular slightly smaller than the diameter of the positioning element 6 in the recess 6a.
  • FIG. 11 a tooth 31 of an internal toothing formed on the rotor 4 is shown.
  • the features shown for the tooth 31 of the internal teeth may alternatively or additionally apply to the tooth or teeth of the external toothing (not shown in detail).
  • FIGS. 11 and 13 are similar to one another, the difference being that a head face 35 which is in FIG. 13 a single round curved surface is in FIG. 11 is formed by a plurality of surface portions 35a to 35c. Furthermore, there is the Difference in that the flank surface 34, the in FIG. 13 is curved around, in FIG. 11 is formed by a plurality of surface portions 34a to 34c.
  • the tooth 31 is formed by a tooth root on the rotor 4 and thus a part of the internal toothing.
  • the tooth 31 may - as stated - alternatively be part of an external toothing, wherein the tooth 31 may be formed on the pump shaft 10 via its tooth root.
  • the tooth 31 has a first end 32 and a second end 33.
  • the between the first end 32 and the second end 33 and between the first and second flank surfaces 34 of the tooth 31 is formed on the cantilevered end of the tooth 31 has a convexly curved head surface 35 which convexly outwardly, ie convexly curved away from the tooth root is.
  • the head surface 35 is formed of a plurality of surface portions 35a to 35c.
  • a straight first surface portion 35 a is formed, which is arranged parallel to the axis of rotation of the part on which the tooth 31 is formed. In the example off FIGS. 11 and 13 this is the axis of rotation of the rotor 4.
  • this may be the axis of rotation of the pump shaft 10.
  • a straight, slightly inclined second surface section 35b is formed with respect to the axis of rotation.
  • a straight third surface portion 35c slightly inclined with respect to the rotation axis.
  • the first, second and third surface sections are arranged relative to one another in such a way that they form a head surface convexly curved or convex away from the tooth root.
  • the head surface 35 is a single surface, one-dimensionally or alternatively two-dimensionally curved convexly away from the tooth root, between the first end 32 and the second end 33.
  • the tooth 31 off FIG. 11 has a first flank surface 34 and a second flank surface (on the hidden rear side). These flank surfaces can be formed the same.
  • the flank surface 34 has a first surface portion 34 a, which is approximately midway between the first end 32 and the second end 33 straight, in particular as a plane. Between the first end 32 and the first surface portion 34a is a second surface portion 34b and between the first surface portion 34a and the second end 33, a third surface portion 34c is formed.
  • the surface portions 34b, 34c are planes slightly angled with respect to the surface portion 34a, such as by a maximum of 3 ° or by a maximum of 1 °.
  • the tooth off FIG. 13 also has a first flank surface 34 and a second flank surface ( FIG. 14 ; in FIG. 13 hidden), which can be configured the same.
  • the flank surface 34 extends from the first end 32 to the second end 33 and is convexly outwardly curved.
  • the pump shaft 10 can be tilted about its axis of rotation with respect to the axis of rotation of the rotor 4 by a small angle, such as a maximum of 3 ° or a maximum of 1 °.
  • the tooth 31 has, in the region of the first surface section or centrally between the first end 32 and the second end 33, a tooth height h 1 which decreases towards the first end 32 and the second end 33 up to a height h 2 .
  • the tooth 31 may have a tooth width b 1 in the region of the first surface portion 34a or the flank surface 35, which decreases towards the first end 32, such as in the second surface portion 34b, up to a tooth width b 2 .
  • the tooth 31 may have the tooth width b 1 in the region of the first surface portion 34a or the flank surface 35, which decreases toward the second end 32, for example in the third surface portion 34c, up to the tooth width b 2 .
  • the decrease of the tooth widths and / or tooth heights is in the FIGS. 12a to 12c and 14a to 14c.
EP16164901.7A 2015-04-17 2016-04-12 Pompe Active EP3081744B1 (fr)

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DE102015105928.2A DE102015105928B4 (de) 2015-04-17 2015-04-17 Pumpe

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016109335A1 (de) * 2016-05-20 2017-11-23 Robert Bosch Automotive Steering Gmbh Verdrängerpumpe und getriebe für ein kraftfahrzeug
EP4166752A1 (fr) * 2021-10-12 2023-04-19 Schwäbische Hüttenwerke Automotive GmbH Pompe avec dispositif de retenue axiale

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016204098B4 (de) * 2016-03-11 2019-09-12 Magna Powertrain Bad Homburg GmbH Flügelzellenpumpe
DE102016211913A1 (de) 2016-06-30 2018-01-18 Schwäbische Hüttenwerke Automotive GmbH Flügelzellenpumpe mit druckbeaufschlagbarem Unterflügelbereich
JP7021866B2 (ja) * 2017-05-11 2022-02-17 Ｋｙｂ株式会社 カートリッジ式ベーンポンプ及びこれを備えるポンプ装置
DE102018208068A1 (de) * 2018-05-23 2019-11-28 Robert Bosch Gmbh Anschlussbaugruppe mit Speisepumpe und elastischem Element
DE102018133679A1 (de) * 2018-12-28 2020-07-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit axialer Kompensation, Auslassdichtung für eine Pumpe sowie vormontierte Pumpeneinheit
DE102018133681A1 (de) * 2018-12-28 2020-07-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit axialer Kompensation, Auslassdichtung für eine Pumpe sowie vormontierte Pumpeneinheit
JP2020169577A (ja) * 2019-04-01 2020-10-15 Ｋｙｂ株式会社 ベーンポンプ
DE102019215933A1 (de) * 2019-07-26 2021-01-28 Hanon Systems Efp Deutschland Gmbh Flügelzellenpumpe
DE102020116731A1 (de) * 2020-06-25 2021-12-30 Schwäbische Hüttenwerke Automotive GmbH Pumpe mit befestigter Dichtung
DE102020122867A1 (de) * 2020-09-01 2022-03-03 Schwäbische Hüttenwerke Automotive GmbH Pumpen-Motor-Einheit mit integrativem Gehäusedeckel
DE102022122261A1 (de) 2022-09-02 2024-03-07 BigRep GmbH Zahnradpumpenwellenanordnung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3207077A (en) * 1963-05-27 1965-09-21 Gen Motors Corp Pump
DE2423773A1 (de) * 1974-05-16 1975-11-27 Daimler Benz Ag Geraeuscharme fluegelzelleneinrichtung, insbesondere -pumpe
WO2013185751A1 (fr) 2012-06-12 2013-12-19 Ixetic Bad Homburg Gmbh Pompe
EP2754896A1 (fr) * 2013-01-14 2014-07-16 Schwäbische Hüttenwerke Automotive GmbH Pompe à gaz avec détente pour la réduction du couple de démarrage
DE102013209877A1 (de) * 2013-05-28 2014-12-04 Mahle International Gmbh Pendelschieberpumpe

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6126638Y2 (fr) 1980-12-27 1986-08-09
JPH08210400A (ja) * 1995-02-06 1996-08-20 Nitsupatsu Seimitsu Kogyo Kk ディスクブレーキにおけるディスクとブラケットの連結構造
DE20302535U1 (de) 2003-02-17 2003-06-18 Trw Fahrwerksyst Gmbh & Co Hydraulikpumpe für ein Servolenksystem
CN201202640Y (zh) * 2008-05-09 2009-03-04 长治液压有限公司 叶片式转向泵主轴传动机构
DE112009002350A5 (de) * 2008-10-22 2011-06-30 ixetic Bad Homburg GmbH, 61352 Pumpe, insbesondere Flügelzellenpumpe
CN103671037A (zh) * 2014-01-07 2014-03-26 广西玉林市威科汽车空压机有限公司 汽车空压机的阀板组件

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3207077A (en) * 1963-05-27 1965-09-21 Gen Motors Corp Pump
DE2423773A1 (de) * 1974-05-16 1975-11-27 Daimler Benz Ag Geraeuscharme fluegelzelleneinrichtung, insbesondere -pumpe
WO2013185751A1 (fr) 2012-06-12 2013-12-19 Ixetic Bad Homburg Gmbh Pompe
EP2754896A1 (fr) * 2013-01-14 2014-07-16 Schwäbische Hüttenwerke Automotive GmbH Pompe à gaz avec détente pour la réduction du couple de démarrage
DE102013209877A1 (de) * 2013-05-28 2014-12-04 Mahle International Gmbh Pendelschieberpumpe

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016109335A1 (de) * 2016-05-20 2017-11-23 Robert Bosch Automotive Steering Gmbh Verdrängerpumpe und getriebe für ein kraftfahrzeug
DE102016109335B4 (de) * 2016-05-20 2020-09-03 Robert Bosch Gmbh Verdrängerpumpe und getriebe für ein kraftfahrzeug
EP4166752A1 (fr) * 2021-10-12 2023-04-19 Schwäbische Hüttenwerke Automotive GmbH Pompe avec dispositif de retenue axiale

Also Published As

Publication number Publication date
CN106050646B (zh) 2019-12-06
US20160305427A1 (en) 2016-10-20
EP3081744B1 (fr) 2021-08-11
DE102015105928A1 (de) 2016-10-20
US10087929B2 (en) 2018-10-02
DE102015105928B4 (de) 2018-05-17
CN106050646A (zh) 2016-10-26

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