EP3730792A1 - Pompe rotative à palettes à liaison d'équilibrage de pression - Google Patents

Pompe rotative à palettes à liaison d'équilibrage de pression Download PDF

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Publication number
EP3730792A1
EP3730792A1 EP20170948.2A EP20170948A EP3730792A1 EP 3730792 A1 EP3730792 A1 EP 3730792A1 EP 20170948 A EP20170948 A EP 20170948A EP 3730792 A1 EP3730792 A1 EP 3730792A1
Authority
EP
European Patent Office
Prior art keywords
rotor
end wall
vane pump
rotor body
groove
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
EP20170948.2A
Other languages
German (de)
English (en)
Inventor
Tobias Iser
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 EP3730792A1 publication Critical patent/EP3730792A1/fr
Pending legal-status Critical Current

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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
    • F04C2/3446—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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • 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
    • 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
    • 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
    • F04C15/0023—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
    • 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
    • F04C2/3442—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 surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0046—Internal leakage control
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • F04C2210/14—Lubricant
    • 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

Definitions

  • the invention relates to a vane pump.
  • the vane pump comprises a delivery chamber for a fluid, which has an inlet and an outlet, a rotor which is arranged in the delivery chamber and which has a rotor body and vanes which are received in a radially displaceable manner by the rotor body, an end wall which the delivery chamber on an axial End face limited, and a support element arranged axially between the end wall and the rotor body, which supports the blades at their radially inner blade ends, the rotor body, the support element and two blades adjacent in the circumferential direction of the rotor forming chambers, the volume of which changes when the rotor rotates .
  • the invention is based in particular on the object of providing an inexpensive vane pump with a long service life.
  • the invention relates to an adjustable vane pump with a delivery chamber which has an inlet and an outlet, a rotor arranged in the delivery chamber for delivering a fluid, which has a rotor body and vanes which are received radially displaceably by the rotor body, an end wall which the delivery chamber limited at an axial end face, and a support element arranged axially between the end wall and the rotor body, which supports the blades at their radially inner blade ends and presses or pushes the radially outer blade ends against a delivery chamber wall.
  • the rotor body, the support element and two circumferentially adjacent blades each form chambers, the volume of which changes when the rotor is rotating or driven.
  • the Vane pump has a pressure equalization connection which connects at least two of the chambers to one another fluidically or fluidically.
  • an axially outwardly directed surface of the rotor body Preferably, an axially outwardly directed surface of the rotor body, a radially inwardly directed surface of the rotor body, an axially inwardly directed surface of the end wall, a radially outwardly directed surface of the support element, a surface of a vane directed in the direction of rotation of the rotor and one against the direction of rotation of the rotor directed surface of an adjacent wing, wherein the surfaces of the wings are facing each other, a chamber which is formed between the rotor body, the support element and two adjacent blades in the circumferential direction.
  • the pressure equalization connection advantageously connects at least one chamber which decreases in size when the rotor is rotating with at least one chamber which increases in size when the rotor is rotating.
  • the pressure equalization connection preferably sets up a fluid exchange between at least two of the chambers which is larger, advantageously at least twice greater, than a fluid exchange in the absence of a pressure equalization connection, which results or can result only from component play.
  • the terms “radial” and “axial” relate in particular to an axis of rotation of the rotor, so that the term “axial” denotes a direction which runs on or parallel to the axis of rotation. Furthermore, the term “radial” denotes a direction which is perpendicular to the axis of rotation.
  • circumferential direction relates in particular to the axis of rotation of the rotor, so that the term “circumferential direction” denotes a direction that runs around the axis of rotation, advantageously in and / or against the direction of rotation of the rotor.
  • the pressure compensation connection allows a fluid enclosed or located in the chambers to be exchanged between the chambers in a targeted manner, whereby the fluid compressed in the decreasing chamber can escape into another chamber, advantageously into an enlarging chamber.
  • a pressure difference in particular between an expanding chamber and a shrinking chamber, can thereby be compensated for with one another.
  • high pressures in the chambers can be relieved, reduced or avoided, whereby the load on the support element, the blades, the rotor body and / or the conveying chamber wall can be reduced particularly easily.
  • the wear on the support element, the vanes, the rotor and / or the delivery chamber wall can be reduced, as a result of which an inexpensive vane pump with a long service life can be provided.
  • the rotor body forms an axial sealing gap with the upper side of the end wall facing it.
  • the top of the end wall facing the rotor body is an inner side of the axial end wall facing the delivery chamber.
  • the support element forms a further axial sealing gap with the end wall, the axial sealing gap formed between the support element and the end wall being arranged radially inside the axial sealing gap formed between the rotor body and the end wall.
  • the axial sealing gap and the further axial sealing gap are preferably annular, for example circular.
  • a diameter of the axial sealing gap which is formed between the end wall and the rotor body is greater than a diameter of the axial sealing gap which is formed between the end wall and the support element.
  • the axial sealing gap which is formed between the rotor body and the end wall, preferably separates the chambers that the rotor body, the support element and two circumferentially adjacent blades of the rotor form, and the delivery cells that form the rotor body, the delivery chamber wall and two in each case Circumferentially adjacent blades of the rotor form, in particular fluidically, from one another.
  • the chambers which are formed by the rotor body, the support element and two blades that are adjacent in the circumferential direction, are formed radially inside the axial sealing gap that is formed between the rotor body and the end wall.
  • the vanes delimit the chambers, which are formed by the rotor body, the support element and two vanes that are adjacent in the circumferential direction, in the circumferential direction radially inside the rotor body.
  • the rotor body that The conveying chamber wall and two wings that are adjacent in the circumferential direction form the conveying cells.
  • the delivery cells which form the rotor body, the delivery chamber wall and two blades that are adjacent in the circumferential direction, are formed radially outside the axial sealing gap that is formed between the rotor body and the end wall.
  • the vanes delimit the delivery cells, which are formed by the rotor body, the delivery chamber wall and two vanes that are adjacent in the circumferential direction, in the circumferential direction radially outside the rotor body.
  • the fluid is transported from the inlet to the outlet.
  • the pressure equalization connection according to the invention is preferably formed radially within the axial sealing gap which is formed between the rotor body and the end wall.
  • the vane pump can in particular have a base and a cover, the base and the cover each having or forming an end wall as described above.
  • the vane pump preferably has an adjusting ring for adjusting an eccentricity between the rotor and the delivery chamber and thus for adjusting the delivery volume which has or forms the delivery chamber wall which radially delimits the delivery chamber.
  • the support element advantageously presses or pushes the wings against the delivery chamber wall of the adjusting ring.
  • the delivery chamber wall preferably forms a running surface for the radially outer wing ends of the wings.
  • the delivery chamber wall is preferably designed as an inner circumferential wall of the adjusting ring.
  • the adjusting ring can be mounted displaceably, rotatably or pivotably.
  • the pressure compensation connection can have at least one groove in the end wall and / or a groove in at least one of the wings and / or at least one through hole in one of the wings and / or an enlarged sealing gap between the support element and the end wall and / or an enlarged sealing gap between at least one the wing and the end wall.
  • the pressure equalization connection fluidly connects at least two chambers with one another in such a way that different fluid pressures in the chambers, which can occur, for example, due to the different chamber volume, are advantageously equalized.
  • a groove has a depth or an axial extent that is greater, advantageously at least 50% and is particularly advantageously at least 100% larger than the axial sealing gap which is formed between the rotor body and the end wall, and / or is larger than the axial sealing gap which is formed between the support element and the end wall.
  • an enlarged axial sealing gap is larger, advantageously at least 50% and particularly advantageously at least 100% larger, than the axial sealing gap that is formed between the rotor body and the end wall, and / or larger than an axial sealing gap that is formed between a wing and the end wall, in particular radially outside of the rotor body.
  • the enlarged axial sealing gap in a region of the chambers, which is formed between a wing and the end wall within the rotor body can be realized by reducing the axial extent of the wing, the reduction of the axial extent only on the radially inner wing end and thus on the conveyor chamber wall or the radial side of the wing facing away from the adjusting ring takes place.
  • the wing thus has different axial extensions when viewed along its radial extension.
  • the wing has a step, a bevel, a bevel, a rounding, etc. on its radially inner wing end.
  • the reduced axial extension or the step, incline, etc. is preferably not located in any rotational position of the rotor and / or in any setting position of the adjusting ring radially outside the axial sealing gap that is formed between the rotor body and the end wall.
  • At least one axial end of the rotor body can be cup-shaped or can have a receiving space for the support element which is open towards the end wall.
  • the axial end of the rotor body has an axially protruding edge which faces the end wall.
  • the axially protruding edge radially surrounds the receiving space and thus the support element.
  • the support element is arranged radially inside the axially protruding edge.
  • the axially protruding edge forms with its axially outwardly directed surface an annular contact surface of the rotor body which, together with the end wall, forms the axial sealing gap which is formed between the rotor body and the end wall.
  • the groove can be formed in the side of the end wall facing the rotor body.
  • the support element is preferably arranged in the receiving space which is delimited by the cup-shaped axial end or the axially protruding edge of the rotor body and the end wall.
  • a groove has a depth or an axial extent that is smaller than a depth or axial extent of the receiving space and / or the support element, advantageously half, preferably less than half the depth or axial extent of the receiving space and / or the support element.
  • the rotor can be mounted in a bearing in the cover and / or in the base.
  • the vane pump can include a drive shaft for driving the rotor, which is rotatably mounted in at least one bearing, such as a plain bearing, in the cover and / or the base.
  • the groove in the end wall is open to the receiving space.
  • the groove in the end wall can be formed by a circle, a segment of a circle or several separate segments of a circle.
  • the groove preferably runs concentrically to the axis of rotation of the rotor, the groove in the end wall running radially at least substantially outside the support element, preferably outside the area surrounded by the support element.
  • the separate circular segments can lie on a circular line or on different circular lines that are spaced differently from the rotor axis / drive shaft.
  • a groove or annular groove designed as a circle preferably has a uniform width and depth. If the groove consists of several separate circular segments, each circular segment preferably has a uniform width and depth, wherein the width and / or the depth of a first separate circular segment can differ from the width and / or the depth of a further separate circular segment. Individual or all of the separate circle segments can have a width and / or depth which varies over the extent of the separate circle segment. The transition of the separate circle segment into the surface surrounding it at the beginning and at the end in the longitudinal direction of the circle segment can be abrupt, step-shaped or gentle. Individual of the separate circle segments, especially when the separate circle segments different circular lines can be connected to one another via a channel.
  • the end wall preferably has at least two sealing webs axially facing the rotor, each of which separates the inlet from the outlet or a low-pressure area from a high-pressure area of the delivery chamber.
  • the sealing webs are each arranged between the inlet and the outlet, viewed along the direction of rotation of the rotor.
  • the sealing webs are preferably arranged opposite one another.
  • One of the sealing webs is formed in the area of the largest conveying cell volume, in particular with full delivery and thus with the greatest eccentricity.
  • the other sealing web is formed in an area of the smallest delivery cell volume, especially with full delivery and thus with the greatest eccentricity, and is also referred to as the drive web.
  • the pressure equalization connection in particular the groove in the end wall, preferably connects at least one chamber on the one sealing web and at least one chamber on the other sealing web to one another.
  • the pressure equalization connection does not connect the delivery cells to one another. It connects only the chambers with one another which are formed radially inside the axially protruding edge of the rotor body between the rotor body, two blades which are adjacent in the circumferential direction and the support element. The axially protruding edge of the rotor seals the chambers and the delivery cells from one another.
  • the groove in the end wall formed by the cover and / or the base is preferably separated or sealed from the inlet formed in the cover and / or in the base.
  • the groove in the end wall formed by the cover and / or the base is preferably separated or sealed from the outlet formed in the cover and / or in the base.
  • the groove in the end wall formed by the cover and / or the base is preferably separated or sealed from the bearing of the rotor and / or the drive shaft in the cover and / or base.
  • the groove in the end wall does not open into the inlet, not into the outlet and not into the bearing; neither in the lid nor in the bottom.
  • the groove in the end wall runs radially inside the inlet and outlet and radially outside the bearing.
  • the groove advantageously runs radially between the inlet / outlet and the bearing.
  • the groove in the end wall advantageously runs at a radial distance from the inlet, the outlet and the bearing.
  • the rotor body can have blade mounts which each include a slot area in which the blade is guided and a bottom area, preferably radially adjoining the slot area, in which the blade is not guided.
  • the bottom area forms a radially inner area of the wing receptacle and can have a shape that deviates from the slot shape of the slot area, for example be round.
  • the bottom area is arranged radially inside the axial sealing gap which is formed between the rotor body and the end wall. It is formed radially between the axial sealing gap, which is formed between the rotor body and the end wall, and the bearing.
  • the groove in the end wall is separated or sealed from the base area of the wing mounts.
  • the groove preferably does not open into any of the bottom areas of the wing receptacles.
  • the groove in the end wall preferably runs radially outside the base area of the wing receptacles.
  • the groove in the end wall advantageously runs radially between the bottom area of the wing mounts and the axial sealing gap which is formed between the rotor body and the end wall.
  • the bottom areas of the wing receptacles each have a bottom which forms a radially inner end of the respective wing receptacle.
  • the groove in the end wall is preferably radially spaced from the bottom of the wing receptacles.
  • the groove in the end wall advantageously extends radially outside the base of the wing receptacles.
  • the groove in the end wall advantageously runs radially between the bottom of the wing receptacles and the axial sealing gap which is formed between the rotor body and the end wall.
  • the delivery cell pump can comprise an adjusting ring with which the delivery rate of the vane pump can be changed.
  • the adjusting ring can form the delivery chamber. If the vane pump comprises an adjusting ring, the adjusting ring can preferably at least partially form the delivery chamber wall against which the blades are tensioned by the support element.
  • the collar can be act any known device with which the delivery volume of a vane pump can be changed, this device does not have to have a ring shape.
  • the vane pump is intended in particular for use in a motor vehicle. It is designed as a motor vehicle pump.
  • the vane pump is preferably provided for pumping a liquid, in particular a lubricant, coolant and / or actuator. It is designed as a liquid pump.
  • the vane pump is preferably provided for the supply, lubrication and / or cooling of a motor vehicle drive engine or a motor vehicle transmission.
  • the liquid is preferably designed as an oil, in particular as an engine lubricating oil or gear oil.
  • the vane pump can be designed as an engine lubricant pump for a motor vehicle or as a gear pump for a motor vehicle.
  • the Figure 1 shows a longitudinal section of a tandem pump of a motor vehicle with a vane pump 1 and a further pump 22, which are driven via a common drive shaft 12.
  • the vane pump 1 can be designed as an engine lubricating oil pump and the further pump 22 as a vacuum pump.
  • the invention is not limited to an arrangement of the vane pump 1 in a tandem pump.
  • the design as a tandem pump and the design of the further pump 22 are not relevant for the implementation of the invention.
  • the vane pump 1 can easily be designed as a stand-alone or independent pump, for example as an engine lubricating oil pump.
  • the vane pump 1 has a rotor 3, 4 with a rotor body 3 and vanes 4, which are received in a radially displaceable manner by the rotor body 3.
  • the rotor 3, 4 is arranged in a delivery chamber 2.
  • the delivery chamber 2 comprises a delivery chamber wall 21 which forms a running surface for the radially outer wing ends of the wings 4.
  • the vane pump 1 comprises a drive shaft 12 which is non-rotatably connected to the rotor 3, 4 and to a drive not shown in detail.
  • the rotor 3, 4 can be driven about its axis of rotation by the drive.
  • the vane pump 1 has a first end wall 5 and a second end wall 6, each of which axially delimits the delivery chamber 2 on one end face.
  • the first end wall 5 is formed by a base or a base plate.
  • the second end wall 6 is formed by a cover or a cover plate.
  • the axial ends of the rotor body 3 are cup-shaped, so that the rotor body 3 forms an annular, axially protruding edge 33 at each of its axial ends, which runs off on a contact surface 51 of the bottom end wall 5 or a contact surface 61 of the cover-side end wall 6, if the rotor 3, 4 is driven.
  • the axially protruding edge 33 of the first axial end of the rotor body 3 forms an axial sealing gap 31 with the running surface 51 of the bottom end wall 5.
  • the axially protruding edge 33 of the second axial end of the rotor body 3 forms an axial sealing gap with the running surface 61 of the cover-side end wall 6 32.
  • the rotor body 3 has one at each of its axial ends Receiving space 34, which is surrounded by the axially protruding edge 33 of the respective end.
  • the receiving space 34 is provided for receiving or arranging a support element 8 for supporting the wings 4.
  • the vane pump 1 comprises a pressure equalization connection 10 which, in the exemplary embodiment shown, has a groove 9 which is formed in the upper side of the end wall 5 and the end wall 6 facing the rotor body 3.
  • the axial sealing gaps 31, 32 seal off the respective receiving space 34 in which the support element 8 is arranged.
  • the support element 8 forms an axial sealing gap 81 with the bottom-side end wall 5 or a sealing gap 82 with the cover-side end wall 6.
  • the support element 8, the rotor body 3, two blades 4 adjacent in the circumferential direction of the rotor 3, 4 and the respective end wall 5, 6 form chambers 18 or rotor interior chambers in the receiving space 34, the volume of which changes periodically when the rotor 3, 4 is driven.
  • the groove 9 of the pressure equalization connection 10 connects at least two adjacent chambers 18 to one another, so that pressure equalization takes place between these chambers 18.
  • the groove 9 is designed as a closed annular groove. It fluidically connects all the chambers 18 to one another permanently.
  • the groove 9 can, however, also be formed as one or more circular segments, so that only selected chambers 18 are connected to one another.
  • the vane pump 1 further comprises an inlet E, which is assigned to a low-pressure side of the vane pump 1, through which fluid can flow into the delivery chamber 2.
  • the fluid can leave the delivery chamber 2 again through an outlet A, which is assigned to a high-pressure side of the vane pump 1.
  • the Figure 2 shows in a longitudinal section and in a top view the end wall 6 on the cover side, respectively the upper side of the end wall 6 facing the rotor 3, 4
  • Figure 2 the running surface 61 for the rotor body 3, the inlet E, the outlet A and the bearing 11 for the drive shaft 12 can be seen.
  • the groove 9 can be seen, which is formed in the upper side of the end wall 6 facing the rotor 3, 4.
  • a first sealing web 13 with an apex 14 and a second sealing web 15 with an apex 16 can also be seen.
  • the groove 9 is designed as a continuous annular groove which opens neither into the inlet E, the outlet A nor into the bearing 11.
  • the pressure equalization connection 10, here the groove 9 connects all the chambers 18 to one another in the exemplary embodiment shown.
  • the groove 9 can, however, also be formed as one or more separate circular segments. A segment of a circle can then, for example, only extend from the apex 16 of the sealing web 15 to the apex 14 of the sealing web 13. As a result, not all of the chambers 18 are connected to one another, but the smallest chamber 18 and the largest chamber 18, whereby the pressure in the smallest chamber 18 and thus the most heavily loaded chamber 18 can be relieved.
  • FIG. 3 shows essentially the same thing as that Figure 2 , this time carried out on the bottom end wall 5. It is therefore referred to the description for Figure 2 which shows the same characteristics as the Figure 3 .
  • the Figure 4 shows the vane pump of the Figure 1 with the adjusting ring 19, with which the delivery rate of the vane pump 1 can be adjusted.
  • the adjusting ring 19 forms the delivery chamber wall 21.
  • the delivery chamber wall 21 forms a running surface for the radially outer vane ends of the vanes 4.
  • the vane pump 1 comprises an end wall 6 on which the axially protruding edge 33 of the rotor body 3 runs at the first axial end along the running surface 61 , and an axially opposite end wall 5 on which the axially opposite, axially protruding edge 33 of the rotor body 3 runs at the second axial end along the running surface 51.
  • the axial sealing gap 31 which the edge 33 of the rotor body 3 forms with the upper side of the end wall 5 facing it is shown in detail.
  • the support element 8 is arranged, which together with the rotor body 3 and two blades 4 adjacent in the circumferential direction of the rotor 3, 4 forms the chambers 18, which are fluidically connected to one another via the pressure compensation connection 10, here the groove 9, see above that a pressure equalization takes place between the chambers 18.
  • the Figure 5 shows in a view into a vane pump 1 the adjusting ring 19, which is pretensioned by a spring element 20 in the direction of greatest eccentricity between the rotor 3, 4 and the adjusting ring 19 and thus full delivery.
  • the adjusting ring 19 can be adjusted hydraulically against the spring force of the spring element 20 by an adjusting pressure in an adjusting chamber.
  • the rotor 3, 4 can be seen with the axially protruding edge 33 which, together with the end wall 5 on the bottom side, forms the axial sealing gap 31 along the running surface 51.
  • the rotor 3, 4 comprises vanes 4 which are pressed or pushed by the support element 8 against the conveying chamber wall 21 of the conveying chamber 2 in each setting position of the adjusting ring 19.
  • the vanes 4 divide the delivery chamber 2 into delivery cells 7 in which fluid can be transported from inlet E to outlet A.
  • the rotor body 3 further comprises wing receptacles 41, which comprise a slot area 42 and a base area 43 with a base 17.
  • the support element 8, two blades 4 adjacent in the circumferential direction of the rotor 3, 4, and the rotor body 3 form the chambers 18, the volume of which changes when the rotor 3, 4 rotates.
  • dashed lines is in the Figure 5 the pressure equalization connection 10 indicated in the form of the groove 9.
  • the groove 9 lies in the receiving space 34, which is radially delimited by the axially protruding edge 33 of the rotor body 3, and outside the bottom areas 43 of the wing mounts 41.
  • the groove 9 does not open into any of the bottom areas 43 of the wing mounts 41 axially protruding edge 33 and the bottom area 43.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP20170948.2A 2019-04-26 2020-04-22 Pompe rotative à palettes à liaison d'équilibrage de pression Pending EP3730792A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102019110905.1A DE102019110905A1 (de) 2019-04-26 2019-04-26 Flügelzellenpumpe mit Druckausgleichsverbindung

Publications (1)

Publication Number Publication Date
EP3730792A1 true EP3730792A1 (fr) 2020-10-28

Family

ID=70417367

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20170948.2A Pending EP3730792A1 (fr) 2019-04-26 2020-04-22 Pompe rotative à palettes à liaison d'équilibrage de pression

Country Status (4)

Country Link
US (1) US11434906B2 (fr)
EP (1) EP3730792A1 (fr)
CN (1) CN111852849B (fr)
DE (1) DE102019110905A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB190914424A (en) * 1909-06-19 1910-02-10 Lentz Getriebe G M B H Improvements in Rotary Pumps or Motors.
DE112016003646T5 (de) * 2015-08-10 2018-05-09 Hitachi Automotive Systems, Ltd. Ölregelpumpe

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191514424A (en) 1915-10-12 1916-11-13 William Henry Bagley Improvements in Machines for Making Wrapped Rims for Jewel Cases and the like.
US3565558A (en) * 1969-01-31 1971-02-23 Airborne Mfg Co Rotary pump with sliding vanes
JPH1089266A (ja) * 1996-09-17 1998-04-07 Toyoda Mach Works Ltd ベーンポンプ
DE10027990A1 (de) 2000-06-08 2001-12-20 Luk Fahrzeug Hydraulik Pumpe
DE102005040702B4 (de) 2005-08-27 2013-06-06 Zf Lenksysteme Gmbh Rotationspumpe
DE102006036439A1 (de) * 2006-08-04 2008-02-07 Robert Bosch Gmbh Förderaggregat
CN102072150B (zh) 2011-01-28 2012-08-15 浙江德克玛液压制造有限公司 叶片泵
JP2015169156A (ja) * 2014-03-10 2015-09-28 日立オートモティブシステムズステアリング株式会社 可変容量形ベーンポンプ
DE102016205686A1 (de) * 2016-04-06 2017-10-12 Zf Friedrichshafen Ag Flügelzellenpumpe
CN106122001A (zh) 2016-07-29 2016-11-16 李钢 径向力平衡的叶片泵

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB190914424A (en) * 1909-06-19 1910-02-10 Lentz Getriebe G M B H Improvements in Rotary Pumps or Motors.
DE112016003646T5 (de) * 2015-08-10 2018-05-09 Hitachi Automotive Systems, Ltd. Ölregelpumpe

Also Published As

Publication number Publication date
CN111852849B (zh) 2022-11-04
CN111852849A (zh) 2020-10-30
US20200340474A1 (en) 2020-10-29
US11434906B2 (en) 2022-09-06
DE102019110905A1 (de) 2020-10-29

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