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EP4180665B1 - Pompe á engrenages internes avec poches de pression sur la roue creuse et/ou sur le boîtier - Google Patents

Pompe á engrenages internes avec poches de pression sur la roue creuse et/ou sur le boîtier

Info

Publication number
EP4180665B1
EP4180665B1 EP22205885.1A EP22205885A EP4180665B1 EP 4180665 B1 EP4180665 B1 EP 4180665B1 EP 22205885 A EP22205885 A EP 22205885A EP 4180665 B1 EP4180665 B1 EP 4180665B1
Authority
EP
European Patent Office
Prior art keywords
outer rotor
circumferential
bearing wall
rotor
rotary pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP22205885.1A
Other languages
German (de)
English (en)
Other versions
EP4180665C0 (fr
EP4180665A1 (fr
Inventor
Gerd Jäggle
Bernd Schobel
Holger Braasch
Thomas Wahl
Johannes Gnann
Michael Ehringer
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 EP4180665A1 publication Critical patent/EP4180665A1/fr
Application granted granted Critical
Publication of EP4180665C0 publication Critical patent/EP4180665C0/fr
Publication of EP4180665B1 publication Critical patent/EP4180665B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than 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
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors

Definitions

  • the invention relates to a rotary pump for conveying a fluid, in particular the rotary pump relates to an electrically driven rotary pump as in the documents JP2013-199850 A or DE10 2007 055 911 A1
  • the rotary pump is preferably an electric rotary pump for pumping oil to supply a machine unit.
  • the rotary pump is an oil pump for a motor vehicle for supplying an engine and/or transmission with oil, in particular lubricating oil.
  • the rotary pump comprises a housing with a pumping chamber, which the housing surrounds and axially delimits at the end faces.
  • the pumping chamber has at least one inlet for the fluid on a low-pressure side of the rotary pump and one outlet for the fluid on the high-pressure side of the rotary pump.
  • the pumping chamber of the rotary pump contains a rotatable inner rotor and an outer rotor that rotates around a pump rotation axis and forms pumping cells with the inner rotor.
  • the pump rotation axis of the inner rotor is eccentric to the pump rotation axis of the outer rotor.
  • a circumferential bearing wall formed by the housing or arranged within the housing, surrounds the outer rotor radially on the outside and supports it in sliding contact for rotation.
  • rotary pumps with a radially externally mounted outer rotor exhibit start-up problems, especially after extended downtimes. These problems are caused in particular by friction between the outer circumferential surface of the outer rotor and the inner circumferential surface of the peripheral bearing wall.
  • the adhesive and/or friction forces between the outer circumferential surface of the inner rotor and the inner circumferential surface of the peripheral bearing wall can be so great that initially no or very little fluid is pumped when the pump starts up. This can lead to Damage to the pump and/or to the units that are to be supplied with the fluid pumped by the pump.
  • the fluid in the lubrication gap between the outer peripheral surface of the outer rotor and the inner peripheral surface of the peripheral bearing wall can generate viscous friction, especially at high speeds, which negatively impacts the efficiency of the rotary pump. Since the viscous friction results primarily from the adhesion of the fluid to the stationary inner peripheral surface of the peripheral bearing wall and the moving outer peripheral wall of the outer rotor, and the resulting shearing of the fluid, the viscous friction forces can increase with the pump speed, which can cause the required drive power of the rotary pump to increase disproportionately to the speed.
  • both the outer circumferential surface of the outer rotor and the inner circumferential surface of the peripheral bearing wall are additionally machined to achieve a high surface quality and minimize adhesive and/or frictional forces.
  • Such machining steps require high precision to ensure tolerances are maintained and the lubrication gap between the outer rotor and the peripheral bearing wall does not become excessively large.
  • Such work steps are not only time-consuming but, above all, costly.
  • the invention proposes a rotary pump for conveying a fluid, comprising a housing with a conveying chamber.
  • the conveying chamber is surrounded by the housing and axially delimited at the end faces and has an inlet for the fluid on a low-pressure side of the rotary pump and an outlet for the fluid on a high-pressure side of the rotary pump.
  • the housing can be constructed in multiple pieces, in particular in two pieces.
  • the housing preferably comprises at least one housing cover and one housing pot.
  • the housing pot preferably delimits the delivery chamber radially outwardly and on one axial end face, while the housing cover axially delimits the delivery chamber on the end face of the delivery chamber facing away from the housing pot.
  • the delivery chamber of the rotary pump contains an inner rotor rotatable about a rotational axis, as well as an outer rotor rotatable about a pump rotational axis, which forms delivery cells with the inner rotor.
  • the pump rotational axis of the inner rotor is preferably eccentric to the pump rotational axis of the outer rotor, i.e., the pump rotational axis of the inner rotor and the pump rotational axis of the outer rotor are offset.
  • the eccentricity of the pump rotational axis of the outer rotor and the pump rotational axis of the inner rotor can be constant or variable during pump operation. If the eccentricity of the two pump rotational axes is variable, this can be controlled, in particular regulated, depending on the operating state of the rotary pump, for example.
  • the inner rotor of the rotary pump is driven by a drive means, in particular a drive shaft.
  • the inner rotor can drive the outer rotor.
  • the outer rotor can also be driven by a drive means, in particular a drive shaft.
  • the outer rotor can drive the inner rotor.
  • Both the inner rotor and the outer rotor can also be driven by a drive means.
  • the rotary pump is preferably designed as an electrically driven rotary pump.
  • the drive means for example a drive shaft
  • the inner rotor and/or the outer rotor can be driven by the unit to be supplied with fluid, in particular the engine of a motor vehicle.
  • the rotary pump is preferably designed as an internal gear pump, with the outer rotor being formed by an internally toothed ring gear and the inner rotor by an externally toothed gear.
  • the inner rotor preferably has at least one tooth fewer than the outer rotor.
  • the outer rotor can, for example, have five teeth and the inner rotor, for example, four teeth.
  • the delivery cells can be formed by the meshing of the teeth of the outer rotor with the teeth of the inner rotor.
  • the eccentricity of the two pump axes of rotation changes the size of the delivery cells in the circumferential direction of the outer rotor, in particular in the direction of rotation of the outer rotor.
  • Internal gear pumps are well known to those skilled in the art, which is why their structure will not be discussed further here.
  • the rotary pump can, for example, also be designed as a pendulum-vane pump.
  • a circumferential bearing wall formed by the housing or arranged in the housing surrounds the outer rotor and rotatably supports it in sliding contact.
  • the outer rotor can be supported by the circumferential bearing wall in radial sliding contact, in particular in circumferential sliding contact.
  • the circumferential bearing wall can be formed by the housing, in particular the housing pot, or by a separate component arranged in the housing, in particular a housing ring.
  • the circumferential bearing wall is part of the housing, in particular the housing pot, and surrounds the outer rotor radially on the outside.
  • the circumferential bearing wall can be joined to an end wall of the housing or can be primary formed, for example, cast or sintered, and together with the end wall form the housing pot.
  • the peripheral bearing wall has an inner peripheral surface, which is preferably cylindrical, in particular circular-cylindrical.
  • the outer rotor has an outer peripheral surface, which is preferably cylindrical, in particular circular-cylindrical.
  • the peripheral bearing wall, in particular the inner peripheral surface of the peripheral bearing wall, and the outer rotor, in particular the outer peripheral surface of the outer rotor, are preferably concentric with one another.
  • the peripheral bearing wall preferably surrounds the outer rotor with a clearance such that the inner diameter of the peripheral bearing wall is larger than the outer diameter of the outer rotor.
  • the inner diameter of the peripheral bearing wall can be at least 60 ⁇ m, in particular at least 70 ⁇ m, larger than the outer diameter of the outer rotor.
  • the inner diameter of the peripheral bearing wall is a maximum of 110 ⁇ m, preferably a maximum of 95 ⁇ m, larger than the outer diameter of the outer rotor.
  • the clearance between the outer rotor and the peripheral bearing wall should not be too large to prevent fluid flow through the gap between the outer rotor and the peripheral bearing wall.
  • the peripheral bearing wall and/or the outer rotor have a plurality of blind pockets that are radially open towards the outer rotor or the peripheral bearing wall.
  • the peripheral bearing wall has a plurality of blind pockets that are radially open towards the outer rotor.
  • the outer rotor can have a plurality of blind pockets that are radially open towards the peripheral bearing wall.
  • the blind pockets interrupt the cylindrical, in particular circular-cylindrical, inner peripheral surface of the peripheral bearing wall and/or the cylindrical, in particular circular-cylindrical, outer peripheral surface of the outer rotor. In this way, the outer rotor and the inner peripheral surface have no contact with one another in the region of the blind pockets.
  • the blind pockets are arranged in an asymmetrical distribution over the circumference of the outer rotor and/or over the circumference of the circumferential bearing wall with respect to the circumferential direction, so that at least two adjacent blind pockets over the circumference of the outer rotor and/or over the circumference of the circumferential bearing wall with respect to the circumferential direction have a distance from each other which, in comparison to the other distances between the blind pockets are different.
  • two adjacent blind pockets each delimit an arc length of the outer circumference of the outer rotor in the circumferential direction, wherein the individual arc lengths delimited by the blind pockets can be different or equal.
  • at least two adjacent blind pockets delimit an arc length of the outer circumference of the outer rotor in the circumferential direction, which is different from the other arc lengths delimited by the blind pockets.
  • At least one blind pocket preferably each of the blind pockets, overlaps either only with the inlet or only with the outlet over more than 80% or in particular more than 90% of its circumferential extent.
  • at least one of the blind pockets, in particular each of the blind pockets overlaps either only with the inlet or only with the outlet over its entire circumferential extent.
  • the rotary pump comprises at least three or four blind pockets and/or a maximum of five or six blind pockets.
  • the rotary pump comprises an even number of blind pockets, in particular four blind pockets.
  • the rotary pump comprises an even number of blind pockets, in particular four blind pockets, wherein a first half of the blind pockets, in particular two of the blind pockets, overlaps only the inlet over more than 80% or more than 90% of their circumferential extent, and a second half of the blind pockets, in particular the other two blind pockets, overlaps only the outlet over more than 80% or more than 90% of their circumferential extent.
  • the rotary pump has an even number of blind pockets, in particular four blind pockets, which are arranged mirror-symmetrically with respect to the inner diameter of the peripheral bearing wall and/or the outer diameter of the outer rotor.
  • the rotary pump comprises four blind pockets, wherein two of the blind pockets form a pair of pockets and the two pairs of pockets are arranged with respect to the inner diameter the peripheral bearing wall and/or the outer diameter of the outer rotor are mirror-symmetrical to each other.
  • the rotary pump comprises an even number of blind pockets, which can be combined into a first and a second half, wherein the blind pockets of the first half overlap only with the inlet over more than 80% or more than 90% of their circumferential extent, and the blind pockets of the second half overlap only with the outlet over more than 80% or more than 90% of their circumferential extent.
  • the two halves can be mirror-symmetrical to each other with respect to the inner diameter of the circumferential bearing wall and/or the outer diameter of the outer rotor.
  • the rotary pump comprises four blind pockets, which can be combined into two pairs of pockets, wherein the blind pockets of the first pair of pockets overlap only with the inlet over more than 80% or more than 90% of their circumferential extent, and the blind pockets of the second pair of pockets overlap only with the outlet over more than 80% or more than 90% of their circumferential extent.
  • the two pairs of pockets can be mirror-symmetrical to each other with respect to the inner diameter of the peripheral bearing wall and/or the outer diameter of the outer rotor.
  • one of the blind pockets in particular each of the blind pockets, extends at least twice as far, preferably at least three times as far, in the circumferential direction of the outer rotor as in the radial direction of the outer rotor.
  • the axial extent of one of the blind pockets, in particular each blind pocket, from a first pocket end to a second pocket end can correspond to at least 70%, preferably at least 80%, of the axial extent of the outer rotor from a first end face of the outer rotor to a second end face of the outer rotor.
  • One of the blind pockets in particular each of the blind pockets, can be in the form of a depression, in particular in the form of a recess, in the peripheral bearing wall and/or in the outer rotor, which extends in the axial direction from the second end face of the outer rotor toward the first end face of the outer rotor.
  • the base of the pocket preferably the base of each blind pocket, can have a radius.
  • the radius of the base of the individual pocket, in particular of each blind pocket is preferably smaller than the radius of the outer circumference of the outer rotor and/or the inner circumference of the peripheral bearing wall.
  • the blind pockets together have an extension in the circumferential direction of the outer rotor that corresponds to at least 20%, in particular at least 25%, of the circumference of the outer rotor. This means that at least 20% of the outer circumference of the outer rotor, in particular at least 25% of the outer circumference of the outer rotor, is preferably overlapped by the blind pockets.
  • the blind pockets together have an extension in the circumferential direction of the outer rotor that corresponds to a maximum of 50%, in particular a maximum of 60%, of the circumference of the outer rotor. This means that at most 50% of the outer circumference of the outer rotor, in particular a maximum of 60% of the outer circumference of the outer rotor, is preferably overlapped by the blind pockets.
  • all blind pockets preferably extend in the circumferential direction of the outer rotor over a total of more than 120°, in particular over a total of more than 150°, of the outer circumference of the outer rotor, and/or all blind pockets preferably extend in the circumferential direction of the outer rotor over a total of at most 210°, in particular over a total of at most 180°, of the outer circumference of the outer rotor.
  • one of the blind pockets, in particular each of the blind pockets extends in the circumferential direction over an arc angle that is at least as large as the arc angle of a tooth gap of the outer rotor on the pitch circle of the outer rotor.
  • the blind pockets have a radial extension which preferably corresponds to a maximum of 10% of the outer diameter of the outer rotor, in particular a maximum of 8% of the outer diameter of the outer rotor.
  • the blind pockets are preferably fluidically separated from one another in the region of the sliding contact between the outer rotor and the peripheral bearing wall.
  • the blind pockets are preferably fluidically separated from one another in the region of the sliding contact between the outer rotor and the peripheral bearing wall in every rotational position of the outer rotor.
  • the sliding contact can also be regarded as a sealed contact.
  • the outer rotor in sliding contact with the circumferential bearing wall, extends axially beyond at least one of the blind pockets, preferably axially beyond each of the blind pockets, in the direction of the first end face of the outer rotor.
  • the extension of the outer rotor in the axial direction can be greater than the axial extension of one of the blind pockets, in particular can be greater than the axial extension of each pocket.
  • the circumferential bearing wall, in sliding contact with the outer rotor can extend axially beyond at least one of the blind pockets, preferably axially beyond each of the blind pockets, in the direction of the first end face of the outer rotor. This means that the extension of the circumferential bearing wall in the axial direction can be greater than the axial extension of one of the blind pockets, in particular can be greater than the axial extension of each pocket.
  • the blind pocket in particular each blind pocket, ends in a sack-like manner in the region of the outer peripheral surface of the outer rotor in sliding contact or the inner peripheral surface of the peripheral bearing wall in sliding contact.
  • one blind pocket in particular each of the blind pockets, can be separated from the other or the other Blind pockets must be fluidically separated, particularly in the area of the first end face of the outer rotor.
  • the peripheral bearing wall surrounds the outer rotor in sliding contact in the region of the first end face of the outer rotor.
  • the outer peripheral surface of the outer rotor is in sliding contact with the inner peripheral surface of the peripheral bearing wall in the region of the first end face of the outer rotor over the entire outer circumference of the outer rotor or the entire inner circumference of the peripheral bearing wall.
  • the sliding contact between the outer circumferential surface of the outer rotor and the inner circumferential surface of the peripheral bearing wall extends over 360° in the region of the first end face of the outer rotor, so that a radial sealing gap is formed between the outer circumferential surface of the outer rotor and the inner circumferential surface of the peripheral bearing wall in the region of the first end face of the outer rotor.
  • the radial sealing gap extends in the axial direction of the outer rotor, preferably over at least 10%, in particular over at least 15%, of the axial dimension of the outer rotor, from its first end face to its second end face.
  • the radial sealing gap between the peripheral bearing wall and the outer rotor is preferably interrupted in the region of the first end face of the outer rotor by a maximum of one, in particular none, of the blind pockets.
  • the radial sealing gap preferably serves to prevent fluid communication between the blind pockets in the region of the first end face of the outer rotor.
  • one blind pocket preferably each of the blind pockets, runs axially open on the second end face of the outer rotor on the peripheral bearing wall and/or on the outer rotor.
  • one of the blind pockets preferably each of the blind pockets, has a second pocket end in the region of the second end face of the outer rotor, which second pocket end is preferably open.
  • the outer rotor and/or the peripheral bearing wall extend/extends in sliding contact towards the second Front side of the outer rotor preferably does not axially extend beyond at least one of the blind pockets, preferably each of the blind pockets.
  • the peripheral bearing wall and the outer rotor can fluidically separate the respective blind pocket, preferably each of the blind pockets, from the remaining blind pockets at the open end by sliding contact, particularly by radial sliding contact.
  • the outer peripheral surface of the outer rotor preferably has no contact with the inner peripheral surface of the peripheral bearing wall in the region of the blind pockets, while the outer peripheral surface of the outer rotor and the inner peripheral surface of the peripheral bearing wall have sliding contact, preferably sealing contact, in the region between the blind pockets.
  • the housing preferably comprises a housing cover which axially delimits the conveying chamber on the second end face of the outer rotor and bears against the peripheral bearing wall with axial sealing contact.
  • the housing cover can form an axial sealing gap with the peripheral bearing wall.
  • the axial sealing contact between the housing cover and the peripheral bearing wall is preferably formed in the circumferential direction of the peripheral bearing wall over the entire circumference of the peripheral bearing wall.
  • the axial sealing contact between the peripheral bearing wall and the housing cover, in particular between the end face of the peripheral bearing wall formed in the region of the second end face of the outer rotor and the end face of the housing cover facing the peripheral bearing wall, preferably extends in the region of the second end face of the outer rotor over 360° of the outer circumference of the peripheral bearing wall.
  • the blind pockets in the region of the second end face of the outer rotor can be fluidically separated from one another.
  • the blind pockets are fluidically separated from one another in the region of the second pocket end by the axial sealing contact, in particular by the axial sealing gap.
  • the housing cover can be in contact with the outer rotor with an axially sealing sliding contact.
  • the second end face of the outer rotor and the The housing cover in particular an end face of the housing cover facing the outer rotor, has an axial sealing gap.
  • the housing cover preferably bears against the outer rotor in axial sliding contact, in particular in axial sealing contact.
  • the axial sealing gap between the housing cover and the peripheral bearing wall can be smaller than the axial sealing gap between the housing cover and the outer rotor.
  • the axial sealing gap between the housing cover and the outer rotor is preferably formed over the entire circumference of the outer rotor in the circumferential direction of the outer rotor.
  • the axial sealing gap preferably extends between the second end face of the outer rotor and the housing cover, in particular between the second end face of the outer rotor and the end face of the housing cover facing the outer rotor, in the region of the second end face of the outer rotor over 360° of the outer circumference of the outer rotor.
  • the blind pockets can be fluidically separated from one another in the region of the second end face of the outer rotor. If the blind pockets have an open end in the region of the second end face of the outer rotor, the blind pockets are preferably fluidically separated from one another in the region of the second pocket end by the axial sealing gap.
  • the outer rotor can have an edge break on its first end face along its circumferential outer edge.
  • An edge break preferably involves the removal of edge material, i.e., the circumferential outer edge of the outer rotor is preferably not sharp-edged on the first end face.
  • the edge break can be rounded, i.e., have a radius.
  • the edge break is formed over the entire length of the circumferential outer edge.
  • the edge break measures at least 200 ⁇ m or at least 300 ⁇ m in the radial direction and/or a maximum of 400 ⁇ m or a maximum of 500 ⁇ m.
  • the edge break measures at least 200 ⁇ m or at least 300 ⁇ m in the axial direction and/or a maximum of 400 ⁇ m or a maximum of 500 ⁇ m.
  • the edge break in particular the rotor chamfer, can be produced during the manufacture of the outer rotor, in particular during the primary forming of the outer rotor.
  • the outer rotor is manufactured using a primary forming process, for example, by sintering or casting.
  • the edge break, in particular the rotor chamfer can be subsequently formed in alternative designs by deburring the outer peripheral edge, for example, by brushing, grinding, or filing.
  • the outer rotor has a rotor chamfer on its first end face along its outer peripheral edge.
  • a chamfer as defined in the application, is preferably understood to be an edge break in the form of a beveled, in particular flat, surface dimensionally defined in width and angle.
  • the beveled surface is preferably curved exclusively in the circumferential direction of the outer rotor.
  • the beveled surface, in particular the rotor chamfer can preferably be formed at an angle of 45° to the axial direction of the outer rotor.
  • the beveled surface, in particular the rotor chamfer can also be formed at an angle of 60° to the axial direction of the outer rotor.
  • the rotor chamfer can be formed at any other angle greater than 0° and less than 90° to the axial direction of the outer rotor.
  • the rotor chamfer preferably measures at least 200 ⁇ m or at least 300 ⁇ m and/or a maximum of 400 ⁇ m or a maximum of 500 ⁇ m in the radial direction.
  • the rotor chamfer preferably measures at least 200 ⁇ m or at least 300 ⁇ m and/or a maximum of 400 ⁇ m or a maximum of 500 ⁇ m in the axial direction.
  • the rotor chamfer measures at least 300 ⁇ m in the radial and axial directions at an angle of 45° to the axial direction of the outer rotor.
  • the circumferential bearing wall can have an inner edge transition along its circumferential inner edge on the first end face of the outer rotor, i.e. on the axial side of the first end face of the outer rotor.
  • An inner edge transition is preferably an overhang of material, i.e. the circumferential inner edge of the circumferential bearing wall is preferably not sharp-edged on the first end face of the outer rotor.
  • the inner edge transition can be rounded, i.e. have a radius.
  • the inner edge transition is formed over the entire length of the circumferential inner edge.
  • the circumferential bearing wall is formed integrally with an end wall of the housing, the Inner edge transition formed along the inner edge between the end wall and the peripheral bearing wall.
  • the peripheral bearing wall on the first end face of the outer rotor has an inner edge ridge along its circumferential inner edge.
  • An inner edge ridge within the meaning of the application is preferably understood to mean an inner edge transition in the form of a beveled, in particular flat, surface dimensionally defined in width and angle.
  • the beveled surface is preferably curved exclusively in the circumferential direction of the peripheral bearing wall.
  • the inner edge transition in particular the inner edge burr, can be produced during the manufacture of the peripheral bearing wall, in particular during the primary forming of the peripheral bearing wall.
  • the peripheral bearing wall is preferably produced as part of the housing pot in a primary forming process, for example, by sintering or casting.
  • the inner edge transition, in particular the inner edge burr is preferably formed in a subsequent manufacturing step during the post-processing of the inner peripheral surface of the peripheral bearing wall, for example, by milling, grinding, or honing.
  • the beveled surface, in particular the inner edge burr can preferably be formed at an angle of 45° to the axial direction of the outer rotor or the peripheral bearing wall.
  • the beveled surface, in particular the inner edge burr can also be formed at an angle of 60° to the axial direction of the outer rotor or the peripheral bearing wall.
  • the inner edge burr can be formed at any other angle greater than 0° and less than 90° to the axial direction of the outer rotor or the peripheral bearing wall.
  • the inner edge burr preferably measures at least 200 ⁇ m or at least 300 ⁇ m and/or a maximum of 400 ⁇ m or 500 ⁇ m in the radial direction.
  • the inner edge burr preferably measures at least 200 ⁇ m or at least 300 ⁇ m and/or a maximum of 400 ⁇ m or 500 ⁇ m in the axial direction.
  • the inner edge burr measures at least 300 ⁇ m in the radial and axial directions at an angle of 45° to the axial direction of the outer rotor.
  • the outer rotor has a broken edge and the peripheral bearing wall has an inner edge transition, and the broken edge of the outer rotor overlaps with the inner edge transition of the peripheral bearing wall.
  • the inner edge transition is particularly preferably designed to correspond to the broken edge.
  • the inner edge transition forms, so to speak, an imprint or negative of the broken edge.
  • the inner edge transition preferably has the same radius or angle as the broken edge.
  • the broken edge is preferably designed in the form of a rotor chamfer, wherein the angle to the axial direction of the outer rotor and the extension in the axial direction of the inner edge burr are equal to the angle to the axial direction of the outer rotor and the extension in the axial direction of the rotor chamfer.
  • the edge break is a rotor chamfer which measures at least 300 ⁇ m in the radial direction and at least 300 ⁇ m in the axial direction at an angle of 45° to the axial direction of the outer rotor
  • the inner edge transition is an inner edge burr which measures at least 300 ⁇ m in the radial direction and at least 300 ⁇ m in the axial direction at an angle of 45° to the axial direction of the outer rotor.
  • the peripheral bearing wall on the second end face of the outer rotor has no edge break along its circumferential inner edge and/or the outer rotor has only a small second edge break along its circumferential outer edge.
  • the edge along the circumferential inner edge of the peripheral bearing wall and/or along the circumferential outer edge of the outer rotor is sharp-edged.
  • At least one of the blind pockets can terminate axially open on the second end face of the outer rotor on the circumferential bearing wall and/or on the outer rotor.
  • the missing edge break or the small second edge break along the inner circumferential edge of the circumferential bearing wall and/or along the outer circumferential edge of the outer rotor ensures that the blind pockets in the region of the second end face of the outer rotor along the inner circumferential edge of the circumferential bearing wall and/or along the outer circumferential edge of the outer rotor have no fluidic connection, in particular in the form of a fluid flow.
  • the small second edge break, if present, along the inner circumferential edge of the circumferential bearing wall and/or along the outer circumferential edge of the outer rotor is preferably so small that no fluid flow can form between the individual blind pockets.
  • a very small second edge break is understood in particular to mean deburring along the inner circumferential edge of the circumferential bearing wall and/or along the outer circumferential edge of the outer rotor, in particular deburring by brushing, filing or grinding.
  • the small second edge break, if present, is not a chamfer with a bevel dimensionally defined in width and angle.
  • the small second edge break has a maximum extension of 100 ⁇ m in the axial direction.
  • the small second edge break has a maximum extension of 100 ⁇ m in the radial direction.
  • the outer rotor can have an edge break, in particular a rotor chamfer, on its first end face along its peripheral outer edge, and a small second edge break on its second end face along its peripheral outer edge, wherein the edge break, in particular the rotor chamfer, is at least three times as large, in particular four times as large, in the axial direction as the second edge break.
  • the circumferential bearing wall can have an inner edge transition, in particular an inner edge ridge, on the first end face of the outer rotor along its circumferential inner edge, and a small edge break on the second end face of the outer rotor along its circumferential inner edge, wherein the inner edge transition, in particular the inner edge ridge, is at least three times as large, in particular four times as large, in the radial direction as the edge break of the outer circumferential edge of the outer rotor on its first end face.
  • Figure 1 shows a top view of the discharge chamber of the rotary pump, while Figure 2 a section through the rotary pump after Figure 1 in the axial direction of the rotary pump.
  • Figure 3 shows a detailed view of the Figure 2 .
  • the Figures 6-8 show the rotary pump of the Figure 1 , only without the funding element 3, 4.
  • the rotary pump comprises a housing 1 with a delivery chamber 5, which surrounds the housing 1 and is axially delimited at the end faces.
  • the housing 1 comprises a housing pot 11 and a housing cover 12.
  • the housing cover 12 delimits the delivery chamber in the axial direction, while the housing pot 11 surrounds the delivery chamber in the radial direction and axially delimits it on the side facing away from the housing cover 12.
  • the delivery chamber 5 has an inlet 6 for a fluid on a low-pressure side of the rotary pump and an outlet 7 for the fluid on the high-pressure side of the pump.
  • a conveying element is formed in the conveying chamber 5, which conveys the fluid from the low-pressure side of the rotary pump, in particular from the inlet 6, to the high-pressure side of the rotary pump, in particular the outlet 7.
  • the rotary pump is designed as an internal gear pump or gerotor pump.
  • the conveying element comprises an outer rotor 3 and an inner rotor 4, wherein the outer rotor 3 is formed by an internally toothed ring gear and the inner rotor 4 by an externally toothed gear, and the teeth of the inner rotor 4 can engage with the teeth of the outer rotor 3 through the rotation of the two rotors.
  • the inner rotor 4 preferably has one fewer tooth than the outer rotor 3.
  • the outer rotor 3 has five teeth and the inner rotor 4 has four teeth, wherein the number of individual teeth is only exemplary and can vary.
  • the two rotors form conveying cells, which can change their volume in the circumferential direction of the outer rotor 3 with the rotation of the two rotors.
  • the inner rotor 4 as shown in Figure 2 is disclosed, driven by a drive means, in particular a drive shaft.
  • the inner rotor 4 is rotatably mounted about the pump rotation axis R 4 and drives the outer rotor 3, in particular through the engagement of the individual teeth with one another.
  • the inner rotor 4 is driven by an electric motor.
  • the inner rotor 4 can also be driven, for example, by the unit to be supplied.
  • the outer rotor 3 can also be driven by a drive means, wherein the inner rotor 4 is driven via the outer rotor 3.
  • the pump rotation axis R 4 of the inner rotor 4 is eccentric to the pump rotation axis R 3 of the outer rotor 3, i.e., the pump rotation axis R 4 of the inner rotor 4 and the pump rotation axis R 3 of the outer rotor 3 are offset.
  • the eccentricity of the pump rotation axis R 3 of the outer rotor 3 and the pump rotation axis R 4 of the inner rotor 4 is constant in the present embodiment, but can also be variable in alternative designs. With a variable eccentricity of the two pump rotation axes, this can be changed, in particular controlled, for example, depending on the operating state of the rotary pump.
  • the housing pot 11 forms a peripheral bearing wall 2, which surrounds the outer rotor 3 and supports it in a sliding contact so that it can rotate around the pump rotation axis R 3.
  • the peripheral bearing wall 2 can also be formed, for example, by a separate ring inserted into the pumping chamber 5.
  • the peripheral bearing wall 2 is formed integrally with the housing pot 11, in particular an end wall of the housing pot 11, in particular in a primary forming process.
  • the circumferential bearing wall 2 has a plurality of blind pockets 21, 22, 23, 24 which are radially open towards the outer rotor 3 and which are fluidically separated from one another in the region of the sliding contact between the outer rotor 3 and the circumferential bearing wall 2.
  • the rotary pump comprises four blind pockets 21, 22, 23, 24 which are formed in the circumferential bearing wall 2.
  • the number of blind pockets can vary and should not be limited to four blind pockets.
  • the blind pockets are fluidically separated from one another in every rotational position of the outer rotor 3. This means that regardless of the rotational angular position of the outer rotor 3, the blind pockets 21, 22, 23, 24 are fluidically separated from one another in the region of the radial sliding contact between the outer rotor 3 and the circumferential bearing wall 2.
  • the blind pockets 21, 22, 23, 24 are formed in the outer rotor 3 and are radially open in the direction of the peripheral bearing wall 2. Even if the blind pockets 21, 22, 23, 24 are formed in the outer rotor 3, the Blind pockets 21, 22, 23, 24 in the area of the radial sliding contact between outer rotor 3 and peripheral bearing wall 2 are fluidically separated from each other regardless of the rotational angle position of the outer rotor 3.
  • the peripheral bearing wall 2 surrounds the outer rotor 3 in the region of a first end face 31 of the outer rotor 3 in radial sliding contact.
  • the outer peripheral surface of the outer rotor 3 is in sliding contact with the inner peripheral surface of the peripheral bearing wall 2 in the region of the first end face 31 of the outer rotor 3 over the entire outer circumference of the outer rotor 3 or the entire inner circumference of the peripheral bearing wall 2 to form a radial sealing gap.
  • the radial sealing gap extends in the axial direction of the outer rotor 3 over at least 10%, in particular over at least 15%, of the axial dimension of the outer rotor 3 from its first end face 31 to its second end face 32.
  • the blind pockets 21, 22, 23, 24 are arranged in an asymmetrical distribution around the circumference of the outer rotor 3 with respect to the circumferential direction.
  • the blind pockets 22 and 23 are spaced apart from one another around the circumference of the outer rotor 3 with respect to the circumferential direction, which is greater than the other distances between the individual blind pockets.
  • the distance between the blind pocket 23 and the blind pocket 24 is smaller than the distance between the blind pockets 22 and 23.
  • the blind pockets 23 and 24 can overlap only with the outlet 7 over more than 90% of their circumferential extension in the circumferential direction of the outer rotor 3 or in the circumferential direction of the circumferential bearing wall 2. In particular, the blind pockets 23 and 24 completely overlap with the outlet 7 in the circumferential direction of the circumferential bearing wall 2. Furthermore, the blind pockets 21 and 22 can overlap only with the inlet 6 over more than 90% of their circumferential extension in the circumferential direction of the outer rotor 3 or in the circumferential direction of the circumferential bearing wall 2. In particular, the blind pockets 21 and 22 completely overlap with the inlet 6 in the circumferential direction of the circumferential bearing wall 2.
  • the rotary pump has four blind pockets 21, 22, 23, 24, which are arranged mirror-symmetrically with respect to the inner diameter d of the peripheral bearing wall 2 and/or the outer diameter D of the outer rotor 3.
  • the blind pockets 21 and 22 form a first pair of pockets
  • the blind pockets 23 and 24 form a second pair of pockets, wherein the two pairs of pockets are mirror-symmetrical to one another with respect to the inner diameter d of the peripheral bearing wall 2 and/or the outer diameter D of the outer rotor 3.
  • the axis of symmetry or the inner diameter d of the peripheral bearing wall 2 and/or the outer diameter D of the outer rotor 3 are Figure 6 indicated by a dashed double arrow.
  • the blind pockets 21, 22 of the first pair of pockets overlap only with the inlet 6 by more than 80% or more than 90% of their circumferential extent
  • the blind pockets 23, 24 of the second pair of pockets overlap only with the outlet 7 by more than 80% or more than 90% of their circumferential extent.
  • the blind pockets 21, 22, 23, 24 extend in the circumferential direction of the outer rotor 3 at least twice as far, preferably at least three times as far, as in the radial direction of the outer rotor 3.
  • the axial extension of the blind pockets 21, 22, 23, 24 from a first pocket end 24a to a second pocket end 24b can correspond to at least 70%, preferably at least 80%, of the axial extension of the outer rotor 3 from a first end face 31 to a second end face 32.
  • the blind pockets 21, 22, 23, 24 together have an extension in the circumferential direction of the outer rotor 3 which corresponds to at least 20%, in particular at least 25%, of the circumference of the outer rotor 3.
  • the blind pockets 21, 22, 23, 24 have a radial extension which preferably corresponds to a maximum of 10% of the outer diameter D of the outer rotor 3, in particular a maximum of 8% of the outer diameter D of the outer rotor 3.
  • the outer rotor 3 extends axially beyond the blind pocket 24 in sliding contact in the direction of its first end face 31.
  • the outer rotor 3 extends axially beyond each of the blind pockets 21, 22, 23, 24 in sliding contact in the direction of its first end face 31.
  • the outer rotor 3 extends further in the axial direction than the blind pockets 21, 22, 23, 24.
  • the peripheral bearing wall 2 also extends in sliding contact in the direction of the first end face 31 of the outer rotor 3 axially beyond the blind pocket 24.
  • the peripheral bearing wall 2 extends in sliding contact in the direction of the first end face 31 of the outer rotor 3 axially beyond each of the blind pockets 21, 22, 23, 24.
  • the peripheral bearing wall 2 and the outer rotor 3 have the same axial extent.
  • the blind pocket 24, however, has an axial extent that is smaller than the axial extent of the peripheral bearing wall 2 and the outer rotor 3.
  • the blind pockets 21, 22, 23, 24 end in a sack-like manner in the region of the outer peripheral surface of the outer rotor 3 in sliding contact and the inner peripheral surface of the peripheral bearing wall 2 in sliding contact. Furthermore, the outer rotor 3 and the peripheral bearing wall 2 form a radial sealing gap in the region of the first end face 31 of the outer rotor 3. The radial sealing gap is not penetrated by any of the blind pockets 21, 22, 23, 24. In this way, the blind pockets 21, 22, 23, 24 are fluidically separated from one another in the region of the first end face 31 of the outer rotor 3.
  • the blind pocket 24, preferably each of the blind pockets 21, 22, 23, 24, extends axially open on the peripheral bearing wall 2.
  • the blind pocket 24, preferably each of the blind pockets 21, 22, 23, 24, has a second pocket end 24b in the region of the second end face 32 of the outer rotor 3, which is open.
  • the outer rotor 3 and the peripheral bearing wall 2 extend in sliding contact toward the second end face 32 of the outer rotor 3, not extending axially beyond the blind pocket 24, preferably each of the blind pockets 21, 22, 23, 24.
  • the peripheral bearing wall 2 and the outer rotor 3 fluidically separate the blind pockets 21, 22, 23, 24 at the open end 24b in sliding contact between the individual blind pockets 21, 22, 23, 24.
  • the housing cover 12 which axially delimits the delivery chamber 5 at the second end face 32 of the outer rotor 3, bears against the peripheral bearing wall 2 with an axial sealing contact and forms an axial sealing gap with the peripheral bearing wall 2.
  • the housing cover 12 bears against the outer rotor 3 in an axial sliding contact.
  • the second end face 32 of the outer rotor 3 and the housing cover 12 have an axial sealing gap.
  • the housing cover 12 bears against the outer rotor 3 in an axial sliding contact, in particular an axial sealing contact.
  • the axial sealing gap between the housing cover 12 and the peripheral bearing wall 2 is smaller than the axial sealing gap between the housing cover 12 and the outer rotor 3.
  • the axial sealing gap between the housing cover 12 and the peripheral bearing wall 2 is formed in the circumferential direction of the outer rotor 3 over the entire circumference of the peripheral bearing wall 2.
  • the blind pockets 21, 22, 23, 24 in the region of the second end face 32 of the outer rotor 3 are fluidically separated from one another by the peripheral bearing wall 2 and the housing cover 12.
  • the axial sealing gap between the housing cover 12 and the outer rotor 3 is formed in the circumferential direction of the outer rotor 3 over the entire circumference of the outer rotor 3.
  • the axial sealing gap extends between the second end face 32 of the Outer rotor 3 and the housing cover 12.
  • the blind pockets 21, 22, 23, 24 are fluidically separated from one another in the region of the second end face 32 of the outer rotor 3.
  • the blind pockets 21, 22, 23, 24 have an open pocket end 24b in the region of the second end face 32 of the outer rotor 3
  • the blind pockets 21, 22, 23, 24 are fluidically separated from one another in the region of the second pocket end 24b by the axial sealing gap.
  • blind pockets 21, 22, 23, 24 are fluidically separated from one another in the region of the second pocket end 24b by the axial sealing gap between the housing cover 12 and the peripheral bearing wall 2 and the axial sealing gap between the housing cover 12 and the outer rotor 3 in the region of the second end face 32 of the outer rotor 3.
  • the outer rotor 3 has an edge break 31a on its first end face 31 along its outer peripheral edge.
  • the edge break 31a according to the present embodiment is designed in the form of a rotor chamfer.
  • the rotor chamfer preferably has an angle of 45° and extends at least 300 ⁇ m in the radial and axial directions.
  • the rotor chamfer can also have a different angle, for example, an angle of 60°.
  • the outer rotor 3 has no sharp-edged transition between the first end face 31 and the circumferential outer surface on its first end face 31 along its outer circumferential edge.
  • the circumferential bearing wall 2 has an inner edge transition 2a on the first end face 32 of the outer rotor 3, i.e. on the axial side of the first end face 31 of the outer rotor 3, along its circumferential inner edge.
  • the inner edge transition 2a can be rounded, i.e. have a radius.
  • the inner edge transition 2a is designed in the form of an inner edge ridge over the entire length of the circumferential inner edge.
  • the circumferential bearing wall 2 is formed integrally with the end wall of the housing 1, in particular of the housing pot 11, facing the first end face 31 of the outer rotor 3, and the inner edge transition 2a is formed along the inner edge between the end wall and the circumferential bearing wall 2.
  • the inner edge transition is preferably an inner edge burr measuring at least 300 ⁇ m in the radial and axial directions.
  • the inner edge burr has an angle of 45° to the axial direction of the outer rotor 3.
  • the inner edge burr and the rotor chamfer 31a overlap each other when the outer rotor 3 is installed.
  • the inner edge burr is configured to correspond to the rotor chamfer in terms of dimensions and angle
  • the rotor chamfer 31a is configured to correspond to the inner edge burr in terms of dimensions and angle.
  • the outer rotor 3 preferably forms a sliding contact with the peripheral bearing wall 2 in the area of the rotor chamfer 31a.
  • the outer rotor 3 has no edge break on its second end face 32 or only a small second edge break 32a.
  • the small second edge break 32a extends a maximum of 100 ⁇ m in the radial and axial directions.
  • the outer peripheral edge 32a of the outer rotor 3 is sharp-edged on its second end face 32.
  • the outer rotor 3 has a second small edge break 32a on its outer peripheral edge of the second end face 32, this corresponds to a maximum of one third of the first edge break 31a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (15)

  1. Pompe rotative pour refouler un fluide, la pompe rotative comprenant :
    - un boîtier (1) comportant un espace de refoulement (5) que le boîtier (1) entoure et délimite axialement aux faces frontales et qui présente une entrée (6) pour le fluide sur un côté basse pression de la pompe rotative et une sortie (7) pour le fluide sur un côté haute pression de la pompe rotative ;
    - un rotor intérieur (4) rotatif dans l'espace de refoulement (5) ;
    - un rotor extérieur (3) rotatif dans l'espace de refoulement (5) autour d'un axe de rotation de pompe (R3) et formant des cellules de refoulement avec le rotor intérieur (4) ; et
    - une paroi de palier circonférentielle (2) formée par le boîtier (1) ou disposée dans le boîtier (1) et entourant le rotor extérieur (3) et le montant en contact coulissant radial de manière rotative autour de l'axe de rotation de pompe (R3),
    - la paroi de palier circonférentielle (2) présentant plusieurs poches borgnes (21, 22, 23, 24) ouvertes radialement vers le rotor extérieur (3) et / ou le rotor extérieur (3) présentant plusieurs poches borgnes (21, 22, 23, 24) ouvertes radialement vers la paroi de palier circonférentielle (2), les poches borgnes (21, 22, 23, 24) étant séparées fluidiquement les unes des autres dans la zone du contact coulissant entre le rotor extérieur (3) et la paroi de palier circonférentielle (2),
    caractérisée en ce que
    - les poches borgnes (21, 22, 23, 24) sont disposées en distribution asymétrique sur la circonférence du rotor extérieur (3) et / ou sur la circonférence de la paroi de palier circonférentielle (2) par rapport à la direction circonférentielle, de sorte qu'au moins deux poches borgnes adjacentes sont à une distance l'une de l'autre sur la circonférence du rotor extérieur et / ou sur la circonférence de la paroi de palier circonférentielle par rapport à la direction circonférentielle, ladite distance étant différente des autres distances entre les poches borgnes.
  2. Pompe rotative selon la revendication précédente, dans laquelle le rotor extérieur (3) et / ou la paroi de palier circonférentielle (2) s'étendent ou s'étend axialement au-delà d'au moins une des poches borgnes (21, 22, 23, 24), de préférence au-delà de chacune des poches borgnes (21, 22, 23, 24) vers une première face frontale (31) du rotor extérieur (3) en contact coulissant, de sorte que la poche respective (21, 22, 23, 24) se termine en forme de sac à une première extrémité de poche (24a) dans la zone de la surface circonférentielle extérieure du rotor extérieur (3) située en contact coulissant ou dans la zone de la surface circonférentielle intérieure de la paroi de palier circonférentielle (2) située en contact coulissant et est ainsi séparée fluidiquement de l'autre poche borgne ou des autres poches borgnes à la première face frontale (31) du rotor extérieur (3).
  3. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle au moins une des poches borgnes (21, 22, 23, 24), de préférence chacune des poches borgnes (21, 22, 23, 24), débouche axialement sur la paroi de palier circonférentielle (2) et / ou sur le rotor extérieur (3) à une seconde face frontale (32) du rotor extérieur (3).
  4. Pompe rotative selon la revendication précédente, dans laquelle la paroi de palier circonférentielle (2) et / ou le rotor extérieur (3) séparent ou sépare fluidiquement la poche borgne respective (21, 22, 23, 24), de préférence chaque poche borgne (21, 22, 23, 24), de l'autre poche borgne ou des autres poches borgnes à l'extrémité débouchante en contact coulissant.
  5. Pompe rotative selon l'une quelconque des deux revendications immédiatement précédentes, dans laquelle le boîtier (1) présente un couvercle de boîtier (12) délimitant axialement la chambre de refoulement (5) à la seconde face frontale (32) du rotor extérieur (3), le couvercle de boîtier (12) s'appliquant contre la paroi de palier circonférentielle (2) en contact d'étanchéité axial et / ou le couvercle de boîtier (12) s'appliquant contre le rotor extérieur (3) en contact coulissant étanche axial.
  6. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle le boîtier (1) présente un couvercle de boîtier (12) délimitant axialement la chambre de refoulement (5) à la seconde face frontale (32) du rotor extérieur (3) et formant une fente d'étanchéité axiale avec la paroi de palier circonférentielle (2) et le rotor extérieur (3), la fente d'étanchéité axiale entre le couvercle de boîtier (12) et la paroi de palier circonférentielle (2) étant plus petite que la fente d'étanchéité axiale entre le couvercle de boîtier (12) et le rotor extérieur (3).
  7. Pompe rotative selon l'une quelconque des revendications 1 à 5, dans laquelle le rotor extérieur (3) présente un cassage d'angle (31a), en particulier un chanfrein de rotor, le long de son bord extérieur circonférentiel à sa première face frontale (31), et / ou la paroi de palier circonférentielle (2) présente une transition de bord intérieur (2a), en particulier une bavure de bord intérieur, le long de son bord intérieur circonférentiel à la première face frontale (31) du rotor extérieur (3).
  8. Pompe rotative selon la revendication précédente, dans laquelle le cassage d'angle (31a) sur le rotor extérieur (3) chevauche la transition de bord intérieur (2a) sur la paroi de palier circonférentielle (2).
  9. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle la paroi de palier circonférentielle (2) ne présente pas de cassage d'angle ou ne présente qu'un petit second cassage d'angle (32a) le long de son bord intérieur circonférentiel à la seconde face frontale (32) du rotor extérieur (3) et / ou le rotor extérieur (3) ne présente pas de cassage d'angle ou ne présente qu'un petit second cassage d'angle (32a) le long de son bord extérieur circonférentiel à sa seconde face frontale (32), le petit second cassage d'angle (32a) s'étendant au plus 100 µm en direction axiale et / ou radiale.
  10. Pompe rotative selon l'une quelconque des trois revendications précédentes, dans laquelle le rotor extérieur (3) présente un second cassage d'angle (32a) le long de son bord extérieur circonférentiel à sa seconde face frontale (32), le premier cassage d'angle (31a) étant au moins trois fois plus grande ou quatre fois plus grande en direction radiale et / ou axiale que le second cassage d'angle (32a).
  11. Pompe rotative selon l'une quelconque des quatre revendications précédentes, dans laquelle le rotor extérieur (3) présente un cassage d'angle (31a), en particulier un chanfrein de rotor, le long de son bord extérieur circonférentiel à sa première face frontale (31), et le cassage d'angle (31a) mesure au moins 200 µm ou au moins 300 µm et / ou au plus 400 µm ou 500 µm en direction radiale et / ou le cassage d'angle (31a) mesure au moins 200 µm ou au moins 300 µm et / ou au plus 400 µm ou au plus 500 µm en direction axiale.
  12. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle la poche borgne respective (21, 22, 23, 24) chevauche sur plus de 80 % ou plus de 90 % de son étendue circonférentielle, de préférence sur toute l'étendue circonférentielle, soit uniquement l'entrée (6), soit uniquement la sortie (7).
  13. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle la pompe rotative comprend quatre poches borgnes (21, 22, 23, 24), les poches borgnes (21, 22, 23, 24) étant disposées selon une symétrie en miroir par rapport à un diamètre intérieur (d) de la paroi de palier circonférentielle (2) et / ou à un diamètre extérieur (D) du rotor extérieur (3).
  14. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle les poches borgnes (21, 22, 23, 24) s'étendent en direction circonférentielle du rotor extérieur (3) au moins deux fois plus loin, de préférence au moins trois fois plus loin, qu'en direction radiale du rotor extérieur (3).
  15. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle l'étendue axiale des poches borgnes (21, 22, 23, 24) depuis la première extrémité de poche (24a) jusqu'à la seconde extrémité de poche (24b) correspond à au moins 70 %, de préférence au moins 80 %, de l'étendue axiale du rotor extérieur (3) depuis la première face frontale (31) jusqu'à la seconde face frontale (32).
EP22205885.1A 2021-11-11 2022-11-07 Pompe á engrenages internes avec poches de pression sur la roue creuse et/ou sur le boîtier Active EP4180665B1 (fr)

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DE102021129445.2A DE102021129445A1 (de) 2021-11-11 2021-11-11 Drucktaschen am Hohlrad

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EP4180665C0 EP4180665C0 (fr) 2025-10-22
EP4180665B1 true EP4180665B1 (fr) 2025-10-22

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US (1) US12104595B2 (fr)
EP (1) EP4180665B1 (fr)
CN (1) CN116104754B (fr)
DE (1) DE102021129445A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE27228E (en) * 1970-01-21 1971-11-09 Pressure balanced bearing loads in hydraulic devices
US3680989A (en) * 1970-09-21 1972-08-01 Emerson Electric Co Hydraulic pump or motor
GB2085969B (en) * 1980-10-17 1984-04-26 Hobourn Eaton Ltd Rotary positive-displacement pumps
JPS63195390A (ja) * 1987-02-10 1988-08-12 Sumitomo Electric Ind Ltd トロコイド式ギヤ−ポンプ
JPH0419375A (ja) * 1990-05-11 1992-01-23 Mitsubishi Materials Corp 内接型オイルモータ及び内接型オイルポンプ
JPH0599117A (ja) * 1991-10-11 1993-04-20 Mitsubishi Materials Corp 内接ギア型油圧回転装置
US5472329A (en) * 1993-07-15 1995-12-05 Alliedsignal Inc. Gerotor pump with ceramic ring
JP2007023975A (ja) * 2005-07-20 2007-02-01 Equos Research Co Ltd ギヤ式のオイルポンプ
JP2008157175A (ja) * 2006-12-26 2008-07-10 Denso Corp 回転式ポンプ
JP2009293561A (ja) * 2008-06-06 2009-12-17 Aisin Seiki Co Ltd オイルポンプ
DE102011083425A1 (de) * 2011-09-26 2013-03-28 Robert Bosch Gmbh Innenzahnradpumpe
JP5911744B2 (ja) * 2012-03-23 2016-04-27 日立オートモティブシステムズ株式会社 内接歯車ポンプ
JP6836922B2 (ja) * 2017-02-02 2021-03-03 本田技研工業株式会社 オイルポンプ
DE102018105121A1 (de) * 2018-03-06 2019-09-12 Schwäbische Hüttenwerke Automotive GmbH Unterstützungstaschen
DE102019001466B4 (de) 2019-03-04 2020-10-15 Alexander Leonhardt Dosiermesssensor

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EP4180665C0 (fr) 2025-10-22
US12104595B2 (en) 2024-10-01
EP4180665A1 (fr) 2023-05-17
CN116104754B (zh) 2025-08-12
CN116104754A (zh) 2023-05-12
US20230141341A1 (en) 2023-05-11
DE102021129445A1 (de) 2023-05-11

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