EP4234883A1 - Pompe avec élément de fixation - Google Patents

Pompe avec élément de fixation Download PDF

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Publication number
EP4234883A1
EP4234883A1 EP23171945.1A EP23171945A EP4234883A1 EP 4234883 A1 EP4234883 A1 EP 4234883A1 EP 23171945 A EP23171945 A EP 23171945A EP 4234883 A1 EP4234883 A1 EP 4234883A1
Authority
EP
European Patent Office
Prior art keywords
housing part
pump
spring
ring
housing
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.)
Pending
Application number
EP23171945.1A
Other languages
German (de)
English (en)
Inventor
Claus Welte
Uwe 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=55754134&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP4234883(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Publication of EP4234883A1 publication Critical patent/EP4234883A1/fr
Pending legal-status Critical Current

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Classifications

    • 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
    • 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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • 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
    • 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
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2/3441—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 one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3445—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 one line or continuous surface substantially parallel to the axis of rotation the vanes having the form of rollers, slippers or the like
    • 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
    • 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
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/023—Piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/0238—Rotary pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0292—Sealings
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • 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. e.g. oil.
  • the pump can B. be designed as a vane pump or rotary vane pump, internal or external gear pump, pendulum vane pump or roller cell pump.
  • the pump is particularly suitable for installation in a vehicle such. B. a motor vehicle and / or to supply a consumer in a motor vehicle.
  • the consumer can B. an internal combustion engine, a transmission such. B. be a steering gear or automatic transmission.
  • a first aspect relates to the support of a spring which acts between a receiving housing and a pump insert inserted in the receiving housing.
  • a second aspect relates to the combination of a seal with a spring acting between the receiving housing and the pump insert.
  • a third aspect relates to the sealing off of the pressure chambers of a multi-stroke pump from one another.
  • a so-called cartridge pump which has a pump assembly or a pump insert, which consists essentially of a rotor, a stroke ring, a pressure plate, pressing pins and a spring element.
  • the rotor is rotatably received between the pressure plate and the side plate and surrounded by the cam ring, which is also arranged between the pressure plate and the side plate.
  • Several press pins which are axially pressed into the pressure plate and penetrate the side plate and the cam ring, secure the pressure plate, the side plate and the cam ring in a rotationally and axially fixed manner relative to one another.
  • the spring element is fastened to the pressure plate on the end face of the pressure plate pointing away from the rotor.
  • the pump insert is inserted into a pot-shaped housing, with the spring element being supported on the bottom or on an end wall of the pot-shaped housing.
  • the housing is closed by a housing cover that holds the pump insert in its installed position.
  • the spring element is supported by two spring tongues on one Cold start plate, which in turn is supported on the pressure plate 17.
  • the pump has a seal arranged between the end wall and the pressure plate, which seals off a first pressure chamber and a second pressure chamber from one another, the pressure chambers being arranged between the end wall and the pressure plate.
  • the seal is a separate part from the spring element.
  • the EP 0 415 089 A2 describes an axial seal having a locking ring and a sealing ring integrally attached thereto.
  • the locking ring consists of a thermoplastic with an extrusion-resistant core and a slightly flexible surface, which is pressed against the wall of the gap to be sealed due to the compressed sealing ring and the oil pressure.
  • a pump insert arranged in a cup-shaped pump housing part has a pressure plate, with the axial seal being arranged between the pressure plate and an end wall of the pump housing part.
  • a valve spring separate from the axial seal acts between an end wall of the pump housing part and the pressure plate. The valve spring is supported on the pressure plate via a valve.
  • the valve is supported centrically, ie in the area of an axis of rotation of a rotor of the pump insert on the pressure plate.
  • the EP 0 415 089 A2 shows designs with one axial seal or several axial seals, the axial seal or axial seals sealing off a suction-side area from a pressure-side area.
  • the suction-side area and the pressure-side area are arranged between the end wall and the pressure plate.
  • the first aspect is based on the task of avoiding, as far as possible, a disadvantageous deformation of the pump cover and/or the end wall of the receiving housing caused by the spring force.
  • the second aspect is based on the task of facilitating the mountability of the pump insert in the receiving housing.
  • the third aspect is based on the object of specifying a space-saving pump which can supply various fluid circuits with pressure fluid.
  • the invention relates to a pump, in particular positive displacement pump such.
  • the pump comprises a receiving housing, which forms a pot-shaped receiving space with an end wall and a peripheral wall, and a pump insert, which is arranged or used in the receiving space, in particular as a unit that can be handled separately from the receiving housing.
  • the pump insert can be supported or centered on the peripheral wall of the cup-shaped receiving space or can form at least one sealing gap running around the circumference with the peripheral wall. The pump insert can thus be guided by the peripheral wall.
  • the pump insert includes a housing which encloses a pump chamber.
  • a rotor can be arranged in the pump chamber so that it can rotate about an axis of rotation relative to the housing.
  • the pump can include the rotor and at least a 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 arranged such that it can rotate about an axis of rotation relative to the first and second housing parts.
  • the rotor can be directly or indirectly connected or connectable in a torque-transmitting manner to a pump shaft, e.g. B. via a shaft-hub connection. When the pump shaft is rotated relative to the first and second housing parts, the rotor rotates with it.
  • the rotor has recesses, in particular guides such. B. slot-shaped recesses or guides, in which conveying elements such. B. wings, slides or rollers, radially movable to the axis of rotation, in particular are slidably received.
  • the conveying elements are accommodated or mounted by the rotor in such a way that they rotate with the rotor about its axis of rotation.
  • each of the conveyor elements is slidably mounted in its guide with a single translatory degree of freedom.
  • the pump shaft may extend through the housing and be rotatably mounted on the housing about the axis of rotation, such as. B. 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 by means of a z. B. straight-toothed shaft-hub connection.
  • the shaft-hub connection has an internal toothing with a plurality of teeth and an external toothing with a plurality of teeth which meshes with the internal toothing.
  • a third housing part namely a cam ring
  • the cam ring surrounds the rotor over its circumference.
  • the cam ring may be a separate part from the first and second housing parts.
  • the cam ring can be a section of the first housing part formed by the first housing part or 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, such as. B. ring-shaped when the cam ring is part of the first or second housing part.
  • the first housing part, the second housing part and the cam ring enclose and delimit a pump chamber in which the rotor and the conveying elements are arranged. At least one pumping chamber is formed radially between the cam ring and the rotor, which is rotatably enclosed between the first and second housing parts, such as e.g. B. a first pumping chamber and a second pumping chamber in a double-stroke pump.
  • a delivery cell is formed between adjacent delivery elements, which is delimited on the circumference by an inner peripheral surface of the cam ring and in the direction of the axis of rotation by the first housing part on one side and by the second housing part on the other side and whose volume changes depending on the rotational position of the rotor changed around its axis of rotation.
  • the pump has a multiplicity of conveying elements and thus, in particular, an identical multiplicity of conveying cells which are formed between the conveying elements.
  • the inner circumference of the cam ring has a contour along which the conveying elements slide when the rotor rotates.
  • the contour is designed in particular in such a way that the volumes of the delivery cells moving through the delivery chamber due to the rotation of the rotor initially increase and then decrease.
  • the pump can B. double stroke, d. H. be formed with a first pumping chamber and a second pumping chamber, which are traversed by the pumping elements or the pumping cells once in a full revolution. This means that the conveying elements are alternately moved twice away from the axis of rotation and twice towards the axis of rotation during a complete revolution.
  • the volume of a delivery cell first increases and then the volume of this delivery cell decreases.
  • the pump or the pump insert can have at least one inlet channel, which opens into the area of the pumping chamber in which the increase in volume of the pumping cell takes place, and have at least one outlet channel, which opens into the area of the pumping chamber in which the reduction in volume of this pumping cell takes place. Due to the increase in volume of the delivery cell, the at least one inlet channel acts as a suction channel. Due to the reduction in volume, the at least one outlet channel acts as a pressure channel.
  • a single-stroke pump can e.g. B. have an inlet port and an outlet port.
  • a double-stroke pump can e.g. B.
  • the pump insert can have a first inlet channel for the first delivery chamber and a second inlet channel separate therefrom for the second delivery chamber and a first outlet channel for the first delivery chamber and a second outlet channel separate therefrom for the second delivery chamber or a common outlet channel for the first and second Have pumping chamber.
  • the conveying elements and/or the rotor each form a pressure gap with the first housing part and the second housing part.
  • the at least one inlet channel can be connected to a fluid reservoir, such as a B. be connected to an oil tank or are, in particular in fluid communication.
  • the at least one suction channel can open into a suction chamber which, for. B. can be formed between the receiving housing and the pump insert, in particular between the peripheral wall of the receiving housing and the pump insert, such as. B. the lifting ring.
  • the at least one outlet channel can be connected to at least one fluid consumer, e.g. B. are in fluid communication with a transmission.
  • the pump insert can 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 can be formed by the first housing part, in particular in one piece or monolithically.
  • the at least one positioning element can be formed as a part that is separate from the first housing part and is anchored in the first housing part.
  • the positioning element can be screwed or pressed into the first housing part, ie anchored in a positive and/or non-positive manner.
  • the at least one positioning element can be anchored in the first housing part in a materially bonded manner, e.g. B. glued, 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. For example, two, three, four or even more positioning elements can be provided.
  • the at least one positioning element can in particular be pin-shaped or cylindrical.
  • the end of the positioning member opposite the anchored end may have the same outside diameter as the anchored end.
  • the second housing part and in particular also the cam ring can be mounted on the at least one positioning element, secured against rotation about the axis of rotation.
  • the at least one positioning element can be formed by a recess provided for each positioning element in the second housing part, e.g. B. through a hole or through hole extend.
  • the at least one positioning element can, for. B. extend through a recess of the cam ring, the z. B. can be formed as a bore, slot or the like.
  • the end of the at least one positioning element which is opposite the end anchored in the first housing part can protrude from the second housing part, in particular from the end face of the second housing part which is opposite the end face which points towards the rotor or which faces the end wall of the Recording housing has.
  • the pump or the pump insert can have a spring which, for. B. on the second housing part and on the bottom or the end wall of the receiving housing.
  • the receiving housing can as I said z. B. be pot-shaped.
  • the peripheral wall of the receiving case may extend around the axis of rotation of the rotor.
  • the front wall is arranged on the front side of the peripheral wall, so that the receiving housing is pot-shaped. The spring tensioned between the end wall and the pump insert tries to push the pump insert, in particular the second housing part, away from the end wall of the receiving housing.
  • Falling out of the pump insert from the receiving housing is z. B. prevented by a cover or an axial securing element, wherein the spring tensioned during insertion counteracts the pump insert, in particular the first housing part the axial securing element or the cover pushes, whereby the axial securing element or the cover prevents the spring from relaxing.
  • the axial securing element can, for. B. be annular and in an annular groove which is formed on the preferably cylindrical periphery of the receiving housing, be used.
  • the axial securing element can be formed by a cover which at least partially or completely closes the opening.
  • the spring tensioned between the pump insert and the end wall exerts a force pointing away from the end wall and acting in particular along, i.e. in the direction of the axis of rotation of the rotor, on the second housing part, which is thereby pressed against the cam ring, with the cam ring being pressed against the first housing part becomes.
  • the cover or the axial securing element forms the abutment for this.
  • the spring force seals the cam ring axially in relation to the first and second housing parts, as a result of which pressure can build up in the pumping chamber or pumping chambers when the pump starts up.
  • the spring can in particular be captively attached to the pump insert, in particular to the at least one positioning element or the second housing part.
  • the spring can B. with the positioning element or the second housing part positively, in particular snapped or non-positively connected, so that the spring is held on the at least one positioning element or the second housing part and is preferably supported or can be supported on the second housing part. It is preferred that the spring is secured against rotation about the axis of rotation, in particular in a positive and/or non-positive manner, on the at least one positioning element or the second housing part.
  • the spring can have or form at least one fastening element, in particular on or in the area of a support section with which the spring is supported on the second housing part or on a part which is supported directly or indirectly on the second housing part.
  • the at least one fastening element can serve as a support section or one fastening element can be provided for each support section.
  • the spring can be attached to the at least one positioning element by means of the fastening element or be fastened or fastened to the second housing part.
  • the fastener which z. B. is designed for a positive connection with the positioning element assigned to it, can be snapped to the positioning element.
  • the at least one positioning element can have a recess, e.g. B. have an annular groove over its circumference, in which engages the at least one fastener of the spring.
  • Such an annular groove can be designed as a recess.
  • the at least one fastening element can be designed in the shape of a lock washer or circlip, similar to lock washers for shafts according to DIN 6799 or circlips for shafts according to DIN 471, in particular with the difference that they are formed by the spring, namely can be molded onto the support section.
  • the fuse element in particular the z. B. designed according to DIN 6799 lock washer or designed according to DIN 471 Seeger ring actually be a disc or a ring, ie not be formed on the spring and z. B. only serve to ensure that the second housing part cannot be pulled off axially from the positioning element.
  • the spring can be fastened to the second housing part or to the securing element or can be sandwiched between the securing element and the second housing part, wherein the fastening element of the spring can be plugged onto the positioning element.
  • the positioning element z. B.
  • the spring may be attached to the second body part or to the head, or sandwiched between the head and the second body part, wherein the fastening element of the spring may be clipped onto 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 is accommodated in the annular groove with play along the longitudinal axis. In this way it can be ensured that the supporting 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 second housing part can have on an inner peripheral surface or an outer peripheral surface a groove that runs at least partially or completely around the axis of rotation of the rotor and is open inwards or outwards, the spring , i.e. one or more sections of the tongue are fastened in the groove on the second housing part, in particular are bordered by the groove.
  • the groove width is slightly larger than the thickness of the portions of the tongue that are placed in the groove for attachment.
  • the tongue may be laterally elastically compressed for insertion into the groove, the tongue being placed in close proximity to the groove and then released.
  • the spring can, for example, have an oval shape in the relaxed state, or projections forming said sections, with the circumferential groove or annular groove extending in a circle around the axis of rotation.
  • the pump can have a pump shaft which is connected to the rotor in a rotationally fixed manner and can be rotated about the axis of rotation.
  • the pump shaft can be rotatably mounted at least in the first housing part.
  • the pump shaft can be rotatably mounted in the second housing part, in particular in a sack-shaped recess or in a continuous recess, in particular a bore, through the second housing part.
  • the bag-shaped recess has the advantage that the pump chamber is sealed off from the end face of the second housing part pointing away from the pump chamber.
  • the continuous recess has the The advantage is that it is easy to manufacture and ensures greater stability.
  • the bearing or bearings can be plain or roller bearings.
  • the pump shaft can have a structure, in particular external teeth, for a shaft-hub connection to the rotor.
  • the diameter of the structure may be larger than the inner diameter of the first housing part and/or the second housing part or the bearings.
  • the structure is thus sandwiched between the first housing part and the second housing part along, i.e. in the direction of the axis of rotation. This means that the shaft cannot be pulled out of the fully assembled pump insert.
  • the first housing part, the second housing part, the cam ring, the rotor, the conveying elements, the positioning elements, the spring and the pump shaft can essentially form the pump insert, which can be handled as a unit. Because the spring is fastened to the at least one positioning element, the pump insert can be prevented from falling apart. The fastening sections of the spring and/or the securing elements which are separate from the spring effect an axial securing of the shaft, so that the pump insert does not fall apart.
  • the easy handling of the pump insert this can in the receiving housing z. B. can be formed by a transmission housing for a motor vehicle, are included or used in the receiving housing, z. B. via one of the end wall opposite opening of the receiving housing.
  • a (second) seal in particular a sealing ring
  • a sealing ring can be arranged between the second housing part and the receiving housing, in particular the peripheral wall, which seals a pressure space, which is essentially formed between the end wall and the second housing part, with respect to a suction space, which is formed between the peripheral wall and the first housing part and / or the cam ring seals.
  • the The pressure chamber can be connected to the at least one pumping chamber by means of the at least one outlet channel.
  • a (first) seal in particular a sealing ring, can be arranged between the first housing part and the receiving housing, in particular the peripheral wall, with the suction space being arranged between the first and second seal.
  • the first seal can cause the suction chamber to be sealed off from the outside or from the opening of the receiving housing.
  • the second housing part acts like a piston which, when the pressure in the pressure chamber increases, increases the force along or in the direction of the axis of rotation on the axial securing element or the cover and thus also the parts of the pump insert, in particular the first housing part, the second housing part and the cam ring, sealingly presses against one another with an increasing force as the delivery pressure increases and in particular in addition to the force of the prestressed spring.
  • the spring arranged resiliently between the receiving housing and the second housing, in particular under tension, is supported towards the second housing part essentially in an area which is arranged in axial alignment with the cam ring in the direction of the axis of rotation of the rotor, and thereby ie by the support in alignment with the cam ring, the second housing part presses against the cam ring.
  • alignment means in an imaginary axial extension along the wall of the cam ring or in the direction of the axis of rotation.
  • the spring element is supported with its two spring tongues on a cold start plate and in an area that is outside of the axial alignment with the cam ring, namely within the inner contour of the cam ring.
  • the spring can have a spring structure made of metal, in particular steel or spring steel, the spring structure made of metal giving the spring its essential spring property along or in the direction of the axis of rotation.
  • the spring z. B. can be coated or encapsulated with another material, which also has a spring property, although this is negligible compared to the spring structure made of metal.
  • the spring can be supported directly or indirectly on the second housing part.
  • an intermediate part can be arranged between the second housing part and the spring, with the spring being supported on the intermediate part.
  • the intermediate part can be supported on the second housing part, preferably likewise in a region which is arranged in axial alignment with the cam ring in the direction of the axis of rotation.
  • the intermediate part can, for. B. a so-called cold start plate or a plate-shaped structure such. B. a perforated (metal) sheet or a screen structure, have or be.
  • the intermediate part can, for. B. be enclosed or arranged between the spring and the second housing part and / or be held or attached to the at least one positioning element, such as. B. each positioning element to which it is attached, have a recess or bore through which the positioning element in question extends.
  • the intermediate part can have at least one area with the sieve-like structure or at least one perforated area, e.g. B. a single, two or more such areas.
  • the intermediate part is arranged in such a way that the at least one region of the liquid conveyed from the at least one delivery chamber is flowed through. Due to the - albeit eg low - flow resistance caused by the at least one area during flow, the pressure increases on the inflow side, ie on the side of the intermediate part on which the liquid from the at least one delivery chamber flows.
  • the pump insert On the inflow side of the intermediate part, the pump insert, in particular the second housing part, has at least one connecting channel which connects the underwing chambers, i. H. the chambers, which are formed in the slots in which the vanes are guided and extend radially between an end of the respective vane and the base of the respective slot, are supplied with the liquid conveyed from the at least one conveying chamber.
  • the dynamic pressure generated by the area of the intermediate part through which flow occurs causes the wings to be extended more quickly during a cold start and thus generally causes the pump to build up pressure more quickly.
  • the intermediate part and/or the spring, on which the intermediate part can be resiliently supported can be designed so flexibly that the intermediate part lifts off the second housing part at least partially when a limit pressure is reached, as a result Liquid can flow from the pumping chamber through a gap formed thereby between the intermediate part and the second housing part.
  • the spring in particular with its end pointing towards the receiving housing or towards the end wall, can be supported essentially in a region on the receiving housing, in particular on the end wall, which is arranged in axial alignment with the cam ring in the direction of the axis of rotation.
  • An advantage here is that deformation of the end wall by the spring force can be avoided.
  • the cross-section, which the spring surrounds in particular in the form of a ring, has a relatively large diameter, in particular approximately at least the inner diameter or the smallest inner diameter of the cam ring.
  • a sealing element can be arranged between the second housing part and the end wall of the receiving housing, which in particular surrounds the pressure chamber in a ring shape.
  • the spring can be ring-shaped and at least partially surround a pressure chamber, in particular a first pressure chamber, which is connected to the delivery chamber, in particular the first delivery chamber, via the outlet channel formed by the second housing part, in particular the first outlet channel.
  • the spring can be arranged in the first pressure chamber.
  • the seal which is also referred to herein as a sealing element, can surround the second pressure chamber in a ring shape, with the first pressure chamber formed between the end wall of the receiving housing and the second housing part being sealed off from the second pressure chamber by means of the sealing element.
  • the first pressure chamber can be connected to other fluid consumers via a first supply branch than the second pressure chamber, which is connected to fluid consumers via a second supply branch that is separate from the first supply branch.
  • the spring arranged between the end wall and the second housing part can e.g. B. a corrugated ring spring, a multi-corrugated spring washer, a hose or bow spring, a U-ring spring, a (metal) C-ring or a (metal) O-ring.
  • a multi-corrugated spring washer can have or consist of a spring structure made of metal, in particular steel, the spring structure being formed from a flat or round material, which forms a closed ring in particular.
  • the spring is at least in the unloaded state on the Circumferential direction of the ring corrugated, ie configured wavy or with several waves, in particular with several crests and troughs.
  • the wave height extends along or in the direction of the axis of rotation or substantially perpendicular or normal to the plane spanned by the annular spring structure.
  • the multi-corrugated spring has the advantage that it can be used in a very space-saving manner.
  • a corrugated spring can have or consist of a spring structure formed from a flat or round material, which winds helically around a longitudinal axis of the spring along a circumferential direction, the spring structure being corrugated in the circumferential direction or having a plurality of waves, i. H. has several crests and troughs.
  • the spring structure can wind partially, completely or multiple times around the longitudinal axis of the spring, in particular in an approximately wavy, helical manner. Adjacent turns may crest and trough abut or may be fastened together. This means that the wave crest of a winding rests against the trough of the next winding.
  • the spring structure can have an initial coil and/or an end coil, with the initial coil and/or the end coil extending substantially planarly around the longitudinal axis of the spring.
  • the spring With the initial turn and/or the end turn, the spring can be supported on the end wall and/or directly or indirectly on the second housing part. Through the initial coil and the final coil, a better fit, i.e. H. causes the spring force to be distributed over a larger area on the parts on which the spring is supported.
  • the longitudinal axis of the spring is parallel or lies on the axis of rotation.
  • the initial turn may include the fastener for attachment to the positioning member.
  • a (metal) C-ring or a (metal) O-ring is ring-shaped.
  • the spring structure extends at least in sections over the circumference of the longitudinal axis of the spring.
  • the longitudinal axis of the spring is vertical or is normal to the surface spanned by the ring.
  • the longitudinal axis of the spring is essentially parallel to or lies on the axis of rotation of the rotor.
  • the ring can be flat or in its circumference Essentially not be wavy.
  • the spring structure is C-shaped in cross-section which is transverse to the circumferential direction, ie with an open contour, and in the case of the (metal) O-ring it is O-shaped, ie with a closed contour.
  • a fastening element for fastening to the positioning element can be formed in each case between adjacent sections which have a C- or O-ring-shaped spring structure.
  • the springs referred to herein may have multiple fasteners for multiple positioning members.
  • annular sealing element (seal or axial seal) is arranged between the end wall and the second housing part, in particular the sealing element described in general and/or for the first aspect, which forms a pressure chamber between the end wall and the second housing part, in particular the second pressure chamber, wherein the pressure chamber is connected via an outlet channel to a pumping chamber formed between the rotor and the cam ring.
  • the spring has a spring structure made of metal, in particular spring steel, which gives the spring its essential spring property, the annular sealing element being fastened to the spring structure, in particular being fastened captively.
  • the spring and the sealing element can form a unit or an integral unit that can be handled as a unit.
  • the sealing element when fastening the spring to the second housing part or the at least one positioning element, can also be arranged at the point provided for the sealing element on the second housing part.
  • the advantage here is that the spring and the sealing element can be attached to the pump insert in one work step. Furthermore, it is advantageously achieved that the sealing element is fixed when the pump insert is inserted into the receiving housing and cannot slip or fall out. This makes it easier to fit the pump insert into the receiving housing.
  • the sealing element can on the spring element z. B. be attached to the spring or the spring structure by molding or molding of the sealing element.
  • the seal referred to as the sealing element can be attached to the spring structure in a form-fitting manner, e.g. B. by plugging, or non-positively, such as. B. by clamping.
  • the spring structure can, for. B. have an additional annular portion which is part of the sealing element and with a sealing material such. B. a polymer or elastomer is molded or coated.
  • the additional ring-shaped section acts as a support structure, which counteracts an extrusion out or a gap extrusion of the sealing material of the sealing element due to the pressure difference between the first pressure chamber and the second pressure chamber.
  • the spring structure can have a further annular section, which is also overmoulded or coated with the sealing material.
  • This further additional annular section can annularly surround the axis of rotation of the rotor, in particular the pump shaft if it extends through the second housing part, in order to seal off the first pressure chamber and/or the second pressure chamber with respect to the pump shaft.
  • the seal or the sealing element, which surrounds the second pressure chamber is preferably arranged eccentrically to the axis of rotation of the rotor, in particular in an area between the annular spring, which at least partially surrounds the first pressure chamber, and the pump shaft or an area that extends in the direction of the Axis of rotation is arranged in an axial alignment with the pump shaft.
  • a first pressure chamber and a second pressure chamber are formed between the end wall and the second housing part, as has already been described above.
  • An annular sealing element as already described, is arranged between the end wall and the second housing part, which encloses the second pressure chamber and seals it off with respect to the first pressure chamber.
  • the first pressure chamber is connected via a first outlet channel to a first pumping chamber formed between the rotor and the cam ring
  • the second pressure chamber is connected via a second outlet channel to a second pumping chamber formed between the rotor and the cam ring.
  • the figures 2 , 3 , 17 and 18 show pump inserts that can be inserted into a receiving housing, as in figure 1 shown.
  • the pump in particular the pump insert 1, comprises a spring 5, which is shown here in various embodiments.
  • the pump or the pump insert 1 can have a seal 9 , in particular an axial seal, arranged between an end wall 20c of a receiving housing 20 and a second housing part 3 .
  • the seal 9 is shown partially combined with the spring 5 in various embodiments.
  • the pump or the pump insert 1 has a rotor 4 which is connected in a torque-proof manner to a pump shaft 10 via a shaft-hub connection 30 .
  • the rotor 4 has recesses, in particular slot-shaped recesses, which serve as guides.
  • a conveying element 13, in particular a vane, is assigned to each recess.
  • the vane 13 can be moved radially at its recess or away from the axis of rotation D of the rotor 4 and towards the axis of rotation D of the rotor 4, in particular with a single translational degree of freedom, can be moved back and forth, such as e.g figure 20 is recognizable.
  • the wings 13 are rotated with the rotor 4.
  • the pump 1 has an annular housing part, namely a cam ring 12 .
  • the cam ring 12 is sandwiched between a first housing part 2 and a second housing part 3 and is non-rotatable with respect to the first and second housing parts 2, 3.
  • the second and third housing part 2, 3 is limited, can also be referred to as the pump chamber 26 become.
  • the rotor 4 and the vanes 13 are arranged in the pump chamber 26 .
  • At least one pumping chamber 27, 28 is formed radially between the rotor 4 and the cam ring 12.
  • the embodiment shown here comprises two delivery chambers 27, 28, namely a first delivery chamber 27 and a second delivery chamber 28 ( figure 20 ).
  • a delivery cell 29 is formed between adjacent vanes 13, the volume of which changes depending on the rotational position of the rotor 4 about its axis of rotation D. Since the pump has a plurality of vanes 13, it also has a corresponding number of delivery cells 29. Several delivery cells 29 are located in each of the delivery chambers 27, 28.
  • 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 cam ring 12 and/or the vanes 13 can be magnetized, so that the vanes 13 bear against the inner peripheral surface of the cam ring 12 due to magnetic force, in particular even when the rotor 4 is not rotating. This allows pressure to build up early when starting or cold starting, i. i.e. when the pump shaft 10 begins to rotate.
  • the vanes 13 can rotate outwards, i. H. are pressed away from the axis of rotation of the rotor 4 against the inner peripheral surface of the cam ring 12.
  • the wings 13 or each of the wings 13 forms a third sealing gap with the inner peripheral surface of the cam ring 12 .
  • the inner peripheral surface of cam ring 12 has a contour that causes vanes 13 to extend at least once (increase in volume of delivery cell 29) and retract (decrease in volume of delivery cell 29) during a full revolution of rotor 4.
  • the pump shown in the example is double stroke, ie with two pumping chambers 27, 28, the wings 13 each Conveying chamber 27, 28 extend once and retract once when they are moved through the conveying chamber 27, 28 by rotation of the rotor 4.
  • the blades 13 are caused to extend, retract, extend and retract again for one full revolution of the rotor 4, or in other words extend twice and retract twice.
  • a delivery cell 29 is formed between adjacent wings 13, the volume of which increases or decreases as a result of the extension and retraction of the wings 13 delimiting this delivery cell 29, namely depending on the contour of the inner peripheral surface of the cam ring 12.
  • the pump insert 1 has a first outlet channel 3b and a second outlet channel 3c, the first outlet channel 3b dividing into a first pressure chamber 23b and a first pumping chamber 27 ( figure 20 ) opens out and thus connects the first pumping chamber 27 and the first pressure chamber 23b with one another in a fluid-carrying manner.
  • the second outlet channel 3c opens into a second delivery chamber 28 and the second pressure chamber 23c, as a result of which it forms the second delivery chamber 28 ( figure 20 ) and the second pressure chamber 23c connects fluid-carrying.
  • the first and second outlet channel 3b, 3c each opens into the region of its respective delivery chamber 27, 28, in which the volume of the delivery cells 29 decreases during the rotation of the rotor 4. This has the effect that fluid located in the delivery cells 29, e.g. B. oil, are displaced through the outlet channels 3b, 3c.
  • the pump insert 1 has a first inlet channel 2b and a second inlet channel 2c, with the first inlet channel 2b opening into the first delivery chamber 27 and a suction chamber 24 and thus connecting the first delivery chamber 27 and the suction chamber 24 in a fluid-conducting manner, and with the second inlet channel 2c in the second pumping chamber 28 and the suction chamber 24 opens and thus the second pumping chamber 28 and the suction chamber 24 fluid-carrying connection.
  • the first and second inlet channel 2b, 2c each opens into the area of its respective delivery chamber 27, 28, in which the volume of the delivery cells 29 increases during the rotation of the rotor 4. This causes fluid to flow through the first and second inlet channel 2b, 2c is conveyed or sucked into the enlarging conveying cell 29.
  • the pump insert 1 comprises at least one positioning element 6, in the example shown two positioned 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 hole 2a, into which the pin-shaped positioning element 6 is pressed with a first end.
  • the pin-shaped positioning element 6 positions the second housing part 3 and the cam ring 12 with respect to their angular positions about the axis of rotation D relative to the first housing part 2.
  • the second housing part 3 and the cam ring 12 have recesses, openings, bores or elongated holes, preferably with a radial extension. through which the positioning element 6 extends.
  • the cam ring 12 has a bore 12a for the first positioning element 6 and a further bore 12a for the second positioning element 6 for this purpose.
  • the second housing part 3 has a through hole through which the positioning element 6 extends.
  • the pin-shaped second end of the positioning element 6 protrudes beyond the end face that points away from the pump chamber 26 .
  • This protruding portion of the positioning element 6 has a recess, such as. B. an annular groove 6a, or at least a part thereof, which extends over the circumference of the positioning element 6.
  • a securing element or fastening element 5a of the spring 5 is arranged in the recess 6a and is fastened in particular in a non-positive and/or positive manner to the positioning element 6 or in the annular groove 6a.
  • the fastening element 5a prevents the first housing part 2, the second housing part 3 and the Stroke ring 12, or in other words, pulling off the second housing part 3 and the stroke ring 12 from the positioning element 6.
  • the spring 5 is also captively attached to the pump insert 1, in particular the positioning elements 6.
  • the pump shaft 10 is rotatably mounted on the first and second housing part 2, 3, in particular by means of a slide bearing in each case.
  • this can do without the support in the second housing part 3 or only with the support in the first housing part 2, particularly when the pump insert 1 is double-stroke, d. H. has two, e.g. The forces caused by the pressures in the pumping chambers 27, 28 transverse to the axis of rotation D can cancel each other out as a result.
  • an external structure such as. B. formed an external toothing on the pump shaft 10, which is in a form-fitting engagement with a corresponding internal structure, in particular internal toothing of the rotor 4, to form a shaft-hub connection 30.
  • the outer diameter of the outer structure of the pump shaft 10 is larger than the diameter of the section of the pump shaft 10 that 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.
  • the outer diameter of the sections of the first housing part 2 and the second housing part 3, which support the pump shaft 10 is smaller than the outer diameter of the outer structure of the pump shaft 10.
  • the first housing part 2 has an annular pocket on its front side facing away from the pump chamber 26, in which a shaft seal 11 is arranged. which is fixed in a rotationally fixed manner to the first housing part 2 and forms a sealing gap with the pump shaft 10 .
  • the shaft seal 11 seals off the pump chamber 26 from the outside.
  • the end of the pump shaft 10 which is opposite the end which is arranged in the area of the spring 5 has an outer contour for a shaft-hub connection 30 with a drive wheel, in particular gear wheel 21, in particular a chain wheel.
  • the gear 21 is non-rotatably seated on the pump shaft 10.
  • the gear 21 can be driven by a chain, which in turn can be driven by z. B. a crankshaft or other shaft connected to z. B. may be connected to an engine of the vehicle is driven.
  • the gear 21 has for its attachment to the pump shaft 10 z. B. has an internal thread with which it is screwed to an external thread of the pump shaft 10 against a shoulder of the pump shaft 10 .
  • An anti-rotation lock seated on the shaft 10 secures the gear wheel 21 against unintentional loosening.
  • the impeller 21 may be joined or attached to the pump shaft 10 by means of an interference fit or other type of connection.
  • the pump insert 1 is in the examples shown in a z. B. cup-shaped receiving housing 20, such as. B. used a housing pot ( figure 1 ).
  • the receiving housing 20 has a peripheral wall 20d which surrounds one of the pump inserts 1 shown here on the peripheral side. Furthermore, the receiving housing 20 has an end wall 20c which is monolithically connected to the peripheral wall 20d, the spring 5 being supported on the end wall 20c in particular axially, ie in the direction of the axis of rotation D.
  • the pump insert 1 is between the end wall 20c and an axial securing element, such as. B. a screw, an axial locking ring or a cover so that the spring 5 is tensioned or remains, in particular is tensioned or remains under pressure.
  • an axial securing element such as. B. a screw, an axial locking ring or a cover so that the spring 5 is tensioned or remains, in particular is tensioned or remains under pressure.
  • the axial securing element can rest against the first housing part 2 and/or along the first housing part 2 or hold it on the receiving housing 20 so that it cannot move in the direction of the axis of rotation D.
  • the first pressure chamber 23b into which the fluid (liquid ) is promoted.
  • the pressure chamber 23b is in turn connected by means of a channel (not shown) to a fluid consumer, such as. B. a lubricant consumer, in particular connected to a transmission.
  • An annular seal 9 is arranged between the end wall 20c and the second housing part 3, which annularly surrounds the second pressure chamber 23c and seals it in relation to the first pressure chamber 23b.
  • the seal 9 thus forms a wall of the first pressure chamber 23b and the second pressure chamber 23c.
  • the fluid delivered by the pump is delivered into the second pressure chamber 23c.
  • the second pressure chamber 23c is in turn connected by means of a channel (not shown) to a fluid consumer, such as. B. a lubricant consumer connected.
  • the seal 9 is arranged in a sealing groove or a sealing pocket of the second housing part 3 which annularly surrounds one end of the second outlet channel 3c, the bottom of the groove or the bottom of the pocket forming a sealing surface for the seal 9 .
  • the wall of the groove or pocket, which annularly surrounds the seal is at a distance from the end wall 20c which is less than the height of the seal 9, in particular than the height of the first ring 9a, which will be described further below.
  • a gap extrusion of the seal 9 is prevented by the first ring 9a, in particular its material, and/or the smaller gap width between wall and end wall 20c.
  • a gap extrusion can also be avoided by a support structure in the seal 9 .
  • a suction chamber 24 is formed between the second seal 8 and the first seal 7, which is arranged in an annular groove on the outer circumference of the first housing part 2 and which forms a sealing gap with the circumferential wall, from which fluid flows via the first delivery chamber 27 and the second Delivery chamber 28 in the first Pressure chamber 23b and the second pressure chamber 23c is funded.
  • the suction chamber 24 can, for. B. be connected by a channel with a reservoir for the fluid in which z. B. can flow back the fluid consumed by the consumer.
  • the pressure in the pressure chambers 23b, 23c increases with increasing speed, whereby the second housing part 3 clamps the cam ring 12 firmly between the first and second housing parts 2, 3 in addition to the prestressing force of the spring.
  • the first and second housing parts 2, 3 and the cam ring 12 are sealed off from one another.
  • the connection between the axial securing element and the first housing part 2 is made so strong that it can withstand the axial force on the axial securing element, as caused by the pressure in the pressure chambers 23b, 23c, ie it cannot be released.
  • the axial securing element is a housing cover which is fastened to the receiving housing 20 and on which the first housing part 2 is supported axially.
  • a spring 5 z. B a suitably designed corrugated ring spring, a multi-corrugated spring washer, a hose or arc spring, a grooved ring spring, a metal O-ring or a metal C-ring in question. If the spring 5 is to be fastened to the positioning elements 6, the spring can have fastening elements 5a for fastening them to the positioning elements 6.
  • a first embodiment of a spring 5 is shown, which is designed as a corrugated ring spring.
  • the corrugated annular spring 5 has an annular spring structure 5b which is corrugated over its circumference, ie has a plurality of waves, ie wave crests and wave troughs.
  • the crests can z. B. on the end wall 20c and the troughs on the second housing part 3 abut.
  • the wave height extends approximately parallel to the axis of rotation D.
  • the spring 5 is made from a flat material, in particular stamped out.
  • the spring 5 On its circumference, the spring 5 has several, here two, fastening elements 5a in the form of recesses which are open towards the inner circumference and which can be arranged in the annular groove 6a of a positioning element 6 .
  • the thickness of the flat material of the spring 5 is less than the groove width of the annular groove 6a.
  • the spring 5 off figure 5 is so far identical to the spring 5 from figure 4 .
  • the spring 5 off figure 4 also points to its inner circumference several protrusions protruding inwards. As a result, the stress curve in the spring during deformation can be compared or the spring preload and spring rate can be adapted to the requirements.
  • the spring 5 off figure 6 essentially corresponds to the design figure 5 , wherein the spring structure 5b from figure 6 more waves than the embodiment figure 5 has, ie is more corrugated.
  • the spring structure 5b has a positioning element 5e, which can engage in a corresponding recess in the second housing part 3 in order to fasten the spring 5 to the fastening elements 6 in the correct position.
  • FIG 7 shows an annular spring 5, which has several tubular sections 5f over its circumference, in this example two tubular sections 5f. Between adjacent tubular portions 5f there is arranged a fastener 5a and in particular a flat portion 5g in which the fastener 5a is formed.
  • the fastening element 5a is a recess open towards the inner circumference of the ring.
  • the thickness of the flat portion 5g is smaller than the groove width of the annular groove 6a of the positioning member 6.
  • the flat portion 5g can be formed by compressing and plastically deforming a previously continuous tubular portion 5f. In the example shown there are two fasteners 5a and thus two flat portions 5g.
  • the spring 5 has two tubular sections 5f, which are connected at their ends respectively via a flat section 5g, which is provided with a fastening element 5a.
  • the embodiment off figure 8 shows a spring 5 identical to the spring from figure 7 is, with the exception of the configuration of the tubular portions 5f.
  • the execution off figure 8 namely has C-shaped sections 5h instead of a tubular section 5f. Otherwise, execution will depend on it figure 7 referred.
  • the C-shaped sections 5h each have a contour that is open in cross section, namely a slot that extends over the circumference, in particular the inner circumference, of the ring-shaped spring structure.
  • the springs 5 or spring structures 5b from the Figures 4 to 8 are preferably made of metal, in particular spring steel.
  • the springs 5 can be coated or encapsulated, in particular with a plastic, such as. B. a polymer or elastomeric or thermoplastic material or z. B. with a paint.
  • FIG 9 shows an annular seal 9, which comprises a first sealing ring 9a made of a first material and a second sealing ring 9b made of a second material.
  • the first ring 9a and the second ring 9b can be connected to one another integrally or in one piece, in particular with a material connection.
  • the first ring 9a serves to ensure the stability of the ring-shaped seal 9, with the second ring 9b primarily serving to ensure the sealing function.
  • Plastic is suitable as the material for the first ring 9a, in particular a thermoplastic plastic or thermoplastics, which can be selected with the necessary properties.
  • Polytetrafluoroethylene is particularly suitable, the core strength of which can be increased by inserted fibers, for example glass fibers, so that the axial seal can withstand considerable pressure.
  • ethylene-tetrafluoroethylene copolymer ETFE
  • Polyterephthalate is also well suited for the intended purpose, since it can be easily vulcanized with the sealing ring.
  • Polyamides, with or without a glass fiber insert, are also suitable for the intended purpose.
  • the second ring 9b is preferably made of a plastic, in particular an elastomeric or rubber-elastic material or elastomer, which is preferably readily vulcanizable, does not tear and is not highly sensitive to notches.
  • a plastic in particular an elastomeric or rubber-elastic material or elastomer, which is preferably readily vulcanizable, does not tear and is not highly sensitive to notches.
  • the listed materials and materials also apply in particular, but not only to the statements from the figures 10 , 11 , 15 and 16 , but can be used, for example, for all embodiments shown or described in the present application.
  • the first ring 9a has a V-shaped groove over its circumference.
  • a counterpart formed by the second ring and adapted to this shape of the groove is arranged in the groove and is connected, in particular vulcanized or glued, to the first ring 9a in the groove.
  • the first ring 9a also has a V-shaped groove extending over the circumference of the first ring 9a
  • the second ring 9b is an O-ring which has a circular cross-section.
  • the second ring 9b is also arranged in the V-shaped groove and is in particular connected to the first ring 9a in a materially bonded manner.
  • the first ring 9a has a flat surface facing the second ring 9b, on which the O-ring-shaped second ring 9b rests and on which the second ring 9b is integrally attached.
  • figure 15 shows a first ring 9a, which has a step running around its annular circumference, in which the second ring 9b, which is designed as an O-ring, is accommodated.
  • the second ring 9b is integrally connected to the first ring 9a.
  • the second ring 9b is loosely inserted into the first ring 9a, in particular into the stepped shoulder.
  • the front end of the seal which is opposite the front end formed by the second ring 9b, has at least one groove running around the annular circumference of the first ring 9a.
  • the groove is bordered by a first circumferential, in particular inner groove wall 9c and a second circumferential, in particular outer groove wall 9d.
  • the first groove wall 9c is continuous over the circumference and is supported on its sealing surface in a sealing manner, as a result of which the first pressure chamber 23b is sealed off from the second pressure chamber 23c.
  • the second groove wall 9d is provided with a plurality of recesses over its circumference, which make the second groove wall 9d liquid-permeable, as a result of which only the first groove wall 9c is sealed.
  • the second groove wall 9d serves to support the seal on the sealing surface so that the seal 9 does not tilt.
  • the second groove wall 9d can be continuous over the circumference and the first groove wall 9c can be provided with the plurality of recesses, with the above-described being transferable to this embodiment.
  • the second groove wall 9d can primarily serve for sealing and the first groove wall 9c primarily for support.
  • FIG 16 shows a seal 9, which consists of only one ring, such as. B. from the material for the above first ring 9a or the above second ring 9b, depending on the expected pressure difference between the first pressure chamber 23b and the second pressure chamber 23c.
  • a front end of the seal is designed with a sealing lip, which has an inclined inner surface, which is inclined in such a way that internal pressure in the second pressure chamber 23c exerts a force on the sealing lip, which at least partially acts against the sealing surface of the second housing part 3 or the end wall 20c presses.
  • On the inner circumference is a variety of z. B. arranged along the height of the seal 5 or in the direction of the axis of rotation D extended recesses z. B.
  • sealing lip is open towards the inner circumference to ensure that the sealing lip, even if it is deformed in the assembled state of the pump insert 1 in the receiving housing 20, is subjected to pressure fluid from the second pressure chamber 23c in order to press it against its sealing surface, e.g second housing part 3 is formed to press.
  • the face of the seal 9 opposite the sealing lip can be flat or even or as shown in figure 15 be designed.
  • figure 12 shows an annular seal 9, which has a first ring 9a made of the above-mentioned first material, alternatively made of metal, in particular steel, which is essentially completely coated or encapsulated over its surface with plastic, in particular the elastomeric or rubber-elastic or thermoplastic material, whereby a second ring 9b is formed.
  • first ring 9a made of the above-mentioned first material, alternatively made of metal, in particular steel, which is essentially completely coated or encapsulated over its surface with plastic, in particular the elastomeric or rubber-elastic or thermoplastic material, whereby a second ring 9b is formed.
  • FIG 13 shows an annular seal 9, which has a first ring 9a, which is designed as a ring-shaped circumferential tube.
  • the ring 9a can e.g. B. alternative to the materials mentioned for the first ring 9a consist of a metallic spring material, in particular spring steel.
  • the ring-shaped circumferential tube 9a can have a closed wall or z. B. be wound from a helical spring.
  • the first ring 9a is coated or encapsulated over its outer circumference with plastic, in particular the elastomeric or rubber-elastic or thermoplastic material, as a result of which a second ring 9b is formed which surrounds the first ring 9a.
  • the pipe 9a out figure 13 can thus act as a spring and the coating or encapsulation 9b as a seal 9. The same applies mutatis mutandis to the execution figure 14 .
  • the execution off figure 14 shows a first ring 9a, which is formed from a slotted tube or a C-shaped profile, which runs around a closed ring.
  • the slit of the C-shaped profile or the slit tube 9a faces inwards and thus to the second pressure chamber.
  • the first ring 9a is coated or encapsulated with plastic, in particular the elastomeric or rubber-elastic or thermoplastic material, over its outer circumference, resulting in a second ring 9b which at least partially surrounds the first ring 9a.
  • the spring 5 off figure 19 has an annular spring structure 5b with a first spring structure ring 5k, which in particular extends concentrically around the axis of rotation D.
  • the spring structure 5b is made of metal, in particular steel, which gives the spring 5 its essential spring property in the direction of the axis of rotation D.
  • the ring-shaped spring structure 5b has a plurality of arms 5d projecting inwards from the first spring structure ring 5k and distributed over its circumference, the ends of which projecting inwards are freely projecting.
  • the arms 5c each have a contact surface 5d with which they rest against the end wall 20c.
  • the bottom of the The first spring structure ring 5k of the spring structure 5b bears against the second housing part 3 in the area which is arranged in axial alignment with the cam ring 12 in the direction of the axis of rotation D.
  • the first spring structure ring 5k has two fastening elements 5a, which are designed as continuous recesses, such as e.g. B. holes or slots are formed.
  • the bore or the elongated hole is surrounded at least over part of its circumference by a wall which has a thickness extending along or in the direction of the axis of rotation D that is smaller than the groove width of the annular groove 6a of the positioning element 6.
  • the spring structure ring 5k can be elastically compressed or pushed apart along an imaginary connecting line between the two fastening elements 5a in order to enable it to be slipped onto the positioning elements 6 and, by releasing, a part of the wall to snap into place to allow in the annular groove 6a.
  • the spring structure 5b has a second spring structure ring 5j, which annularly surrounds the second pressure chamber 23c. Furthermore, the spring structure 5b has a third spring structure ring 5i, which extends around the axis of rotation D and is arranged inside the first spring structure ring 5k, from which the arms 5d protrude.
  • At least the second spring structure ring 5j, preferably and if present also the third spring structure ring 5i and optionally also the first spring structure ring 5k are coated or overmoulded with plastic, in particular the elastomeric or rubber-elastic or thermoplastic material, at least partially or completely, so that at least the in the direction of the Axis of rotation D pointing ends of the second ring, which includes the second spring structure ring 5j, and the third ring, which includes the third spring structure ring 5i, are formed with a surface made of plastic, in particular the elastomeric or rubber-elastic or thermoplastic material. Furthermore, the elastomeric or rubber-elastic or thermoplastic material separates the second pressure chamber 23c from the first pressure chamber 23b.
  • the second ring with its overmolding or coating can thus be defined as seal 9.
  • the third ring with its coating or encapsulation seals the bore of the second housing part 3, in which a section of the pump shaft 10 is arranged, with respect to the first pressure chamber 23b and the second pressure chamber 23c.
  • the encapsulation or coating of the third ring is supported on the second housing part 3 and on the opposite side on the housing wall 20c.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
EP23171945.1A 2015-04-17 2016-04-12 Pompe avec élément de fixation Pending EP4234883A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102015105933.9A DE102015105933B4 (de) 2015-04-17 2015-04-17 Pumpe
EP16164888.6A EP3081741B1 (fr) 2015-04-17 2016-04-12 Pompe
EP19202347.1A EP3617447B1 (fr) 2015-04-17 2016-04-12 Pompe

Related Parent Applications (3)

Application Number Title Priority Date Filing Date
EP16164888.6A Division EP3081741B1 (fr) 2015-04-17 2016-04-12 Pompe
EP19202347.1A Division EP3617447B1 (fr) 2015-04-17 2016-04-12 Pompe
EP19202347.1A Division-Into EP3617447B1 (fr) 2015-04-17 2016-04-12 Pompe

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Publication Number Publication Date
EP4234883A1 true EP4234883A1 (fr) 2023-08-30

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EP16164888.6A Active EP3081741B1 (fr) 2015-04-17 2016-04-12 Pompe
EP19162589.6A Active EP3521560B1 (fr) 2015-04-17 2016-04-12 Pompe
EP19202347.1A Active EP3617447B1 (fr) 2015-04-17 2016-04-12 Pompe
EP23174113.3A Pending EP4234931A3 (fr) 2015-04-17 2016-04-12 Pompe
EP23171945.1A Pending EP4234883A1 (fr) 2015-04-17 2016-04-12 Pompe avec élément de fixation

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EP16164888.6A Active EP3081741B1 (fr) 2015-04-17 2016-04-12 Pompe
EP19162589.6A Active EP3521560B1 (fr) 2015-04-17 2016-04-12 Pompe
EP19202347.1A Active EP3617447B1 (fr) 2015-04-17 2016-04-12 Pompe
EP23174113.3A Pending EP4234931A3 (fr) 2015-04-17 2016-04-12 Pompe

Country Status (4)

Country Link
US (2) US10082139B2 (fr)
EP (5) EP3081741B1 (fr)
CN (2) CN106050647B (fr)
DE (4) DE102015105933B4 (fr)

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DE102017213320A1 (de) * 2017-08-02 2019-02-07 Robert Bosch Gmbh Dichtring einer Kolbenpumpe, insbesondere für eine Fahrzeugbremsanlage
DE102018133681A1 (de) * 2018-12-28 2020-07-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit axialer Kompensation, Auslassdichtung für eine Pumpe sowie vormontierte Pumpeneinheit
DE102018133680A1 (de) 2018-12-28 2020-07-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit axialer Kompensation, Auslassdichtung für eine Pumpe sowie vormontierte Pumpeneinheit
DE102018133679A1 (de) 2018-12-28 2020-07-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit axialer Kompensation, Auslassdichtung für eine Pumpe sowie vormontierte Pumpeneinheit
DE102019103675A1 (de) * 2019-02-13 2020-08-27 Schwäbische Hüttenwerke Automotive GmbH Feder-Dichtungs-Einheit
DE102019215933A1 (de) 2019-07-26 2021-01-28 Hanon Systems Efp Deutschland Gmbh Flügelzellenpumpe
DE102019132729A1 (de) * 2019-12-02 2021-07-01 Schwäbische Hüttenwerke Automotive GmbH Sickendichtung
DE102020106796A1 (de) 2020-03-12 2021-09-16 Schwäbische Hüttenwerke Automotive GmbH Pumpeneinsatz und Pumpenanordnung mit einem solchen Pumpeneinsatz
DE102020116748A1 (de) 2020-06-25 2022-02-17 Schwäbische Hüttenwerke Automotive GmbH Pumpe mit axial wirksamer Federdichtung
DE102020116822A1 (de) * 2020-06-25 2021-12-30 Schwäbische Hüttenwerke Automotive GmbH Axiale Druckentlastung in Gleitlagern von Pumpen
DE102020133200A1 (de) 2020-12-11 2022-06-15 Schwäbische Hüttenwerke Automotive GmbH Sickendichtung
WO2022137706A1 (fr) * 2020-12-21 2022-06-30 株式会社Ihi Structure de palier pour engrenage dans une pompe à engrenages externes
JP7141481B2 (ja) * 2021-02-26 2022-09-22 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
DE102021204072A1 (de) 2021-04-23 2022-10-27 Hanon Systems Efp Deutschland Gmbh Cartridgepumpe
DE102021126416A1 (de) * 2021-10-12 2023-04-13 Schwäbische Hüttenwerke Automotive GmbH Axialsicherung einer Pumpe
WO2024079543A1 (fr) * 2022-10-11 2024-04-18 Ceme S.P.A. Pompes à palettes

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Also Published As

Publication number Publication date
EP3617447A3 (fr) 2020-06-03
US11143181B2 (en) 2021-10-12
EP3081741A2 (fr) 2016-10-19
EP3521560A2 (fr) 2019-08-07
CN110043461B (zh) 2021-12-31
EP3081741B1 (fr) 2019-11-13
EP4234931A3 (fr) 2023-09-06
CN106050647A (zh) 2016-10-26
DE102015105933A1 (de) 2016-10-20
DE202016009179U1 (de) 2023-06-26
US20160305428A1 (en) 2016-10-20
EP3617447B1 (fr) 2023-06-14
CN106050647B (zh) 2019-02-12
DE102015105933B4 (de) 2018-04-26
EP3617447C0 (fr) 2023-06-14
EP3521560A3 (fr) 2019-08-21
DE202016009178U1 (de) 2023-06-26
US10082139B2 (en) 2018-09-25
EP3081741A3 (fr) 2017-01-04
CN110043461A (zh) 2019-07-23
EP4234931A2 (fr) 2023-08-30
EP3617447A2 (fr) 2020-03-04
DE202016009177U1 (de) 2023-06-14
EP3521560B1 (fr) 2022-12-28
US20180372097A1 (en) 2018-12-27

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RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR