EP3957822B1 - Agencement de pompe - Google Patents

Agencement de pompe Download PDF

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Publication number
EP3957822B1
EP3957822B1 EP20191931.3A EP20191931A EP3957822B1 EP 3957822 B1 EP3957822 B1 EP 3957822B1 EP 20191931 A EP20191931 A EP 20191931A EP 3957822 B1 EP3957822 B1 EP 3957822B1
Authority
EP
European Patent Office
Prior art keywords
pump
rotor
fluid
face
pump arrangement
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
EP20191931.3A
Other languages
German (de)
English (en)
Other versions
EP3957822A1 (fr
Inventor
Tomasz MALOGOWSKI
Omar FRANCESCHI
Stefan TILLER
Hong Giang TO
Maurice ANDREE
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.)
GKN Powder Metallurgy Engineering GmbH
Original Assignee
GKN Sinter Metals Engineering 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 GKN Sinter Metals Engineering GmbH filed Critical GKN Sinter Metals Engineering GmbH
Priority to SI202030382T priority Critical patent/SI3957822T1/sl
Priority to EP20191931.3A priority patent/EP3957822B1/fr
Priority to PCT/EP2021/072836 priority patent/WO2022038137A1/fr
Priority to US18/022,109 priority patent/US20230304494A1/en
Priority to CN202180050927.4A priority patent/CN115943248A/zh
Publication of EP3957822A1 publication Critical patent/EP3957822A1/fr
Application granted granted Critical
Publication of EP3957822B1 publication Critical patent/EP3957822B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—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
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • 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
    • 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
    • F04C2240/56—Bearing bushings or details thereof
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/17—Tolerance; Play; Gap

Definitions

  • the invention relates to a pump arrangement, at least comprising a pump and a drive unit for the pump, which are arranged in a common housing.
  • the drive unit is an axial flux electric drive, which includes a stator connected to the housing in a rotationally fixed manner and a rotor arranged rotatably relative to the housing.
  • the rotor forms an external conveying means of the pump and has a first conveying profile (e.g. a first toothing or vane of a vane pump) on an inner circumferential surface, with an inner conveying means of the pump being arranged in a radial direction within the rotor, which is on a Outer circumferential surface has a second conveying profile (e.g. a second toothing or a cylindrical outer circumferential surface), which interacts with the first conveying profile to convey a fluid and possibly (in the case of the toothings) to drive the inner conveying means through the rotor.
  • a first conveying profile e.g. a first toothing
  • a rotor of the pump is arranged on an axis which is led out of a housing of the pump arrangement.
  • a pump arrangement is e.g. B. from the DE 10 2015 207 748 A1 known.
  • a fluid pump is described there that is driven by an electric motor.
  • a pump rotor of the fluid pump is coupled to the electric motor.
  • the electric motor is an axial flow electric motor, the electric motor rotor of which is also the pump rotor or drives a pump rotor.
  • the pump rotor and the electric motor rotor are accommodated in a common housing in which the pump rotor and the electric motor rotor rotate in a disk-shaped manner integrated as a combination rotor, the common housing having a fluid inlet and a fluid outlet to the combination rotor.
  • Fluid delivery space is arranged in a closed manner in the common housing and fluid inflow and fluid outflow to the pump space occurs axially along the axis of rotation.
  • the DE 10 2017 222 754 A1 is aimed at a gerotor pump.
  • the inner gerotor forms the rotor.
  • the DE 10 2011 103 493 A1 is aimed at an electrical machine with two stator units and two rotor units.
  • a vane cell pump in which a device for building up a pressure between the end faces is provided on an end face of the rotor or the pump housing.
  • the EP 2 075 469 A2 A vane cell pump is known in which a device for building up a pressure between the end faces is provided on an end face of the rotor or the pump housing.
  • a pump arrangement with the features according to claim 1 contributes to solving these tasks.
  • Advantageous further training is the subject of the dependent patent claims.
  • the features listed individually in the patent claims can be combined with one another in a technologically sensible manner and can be supplemented by explanatory facts from the description and/or details from the figures, with further embodiment variants of the invention being shown.
  • a pump arrangement at least comprising a pump with a pressure side and a suction side and a drive unit for the pump, which are arranged in a common housing.
  • the drive unit is an axial flux electric drive, which (precisely) comprises a stator connected to the housing in a rotationally fixed manner and (precisely) a rotor arranged rotatably relative to the housing.
  • the rotor is arranged with a first end face opposite the stator or a stator-side housing (i.e. a housing comprising the stator) along an axial direction and forms an external conveying means the pump.
  • the outer conveying means has a first conveying profile on an inner circumferential surface.
  • an inner conveying means of the pump In a radial direction within the rotor, an inner conveying means of the pump is arranged, which has a second conveying profile on an outer peripheral surface, which interacts with the first conveying profile to convey a fluid.
  • the inner conveying means is mounted on a centering element that is non-rotatably connected to the housing. At least the rotor and the external conveying means are designed to be mounted exclusively via the fluid conveyed by the pump (rotatable relative to other components of the pump arrangement).
  • Electric drives regularly include a stator and a rotor, which are arranged coaxially to one another.
  • the rotor is referred to here as the carrier of permanent magnets, while the stator has a coil arrangement.
  • the rotor and stator are arranged one behind the other, particularly along the axial direction. Differently magnetized magnets are arranged alternately on the rotor along the circumferential direction.
  • the coil arrangement of a stator has cores, e.g. B. made of SMC, which are surrounded by current-carrying windings.
  • Each core may be an element arranged to be magnetized when a current is passed through current-carrying windings around the core.
  • the current-carrying windings can be designed as coils.
  • SMC is in particular formed from iron powder particles that are electrically insulated from each other. Iron losses in SMC parts in an alternating electric field are generally low. In this regard, it therefore appears desirable to use SMC in electrical machines, at least partially, instead of the most commonly used steel lamination (steel sheets or electrical steel).
  • the particles are compacted and hardened. The SMC material is not sintered. Rather, the temperature is controlled below a melting temperature, which is, however, sufficient for the material to permanently maintain the intended geometry.
  • the rotor of the electric drive can have permanent magnets or soft magnetic elements, for example in recesses.
  • a permanently excited synchronous or brushless direct current motor, abbreviated BLDC can be formed using permanent magnets as an electric drive, while, for example, a reluctance motor can be created as an electric motor in an axial, radial or transversal design using soft magnetic elements.
  • the rotor and stator together form, in particular, the drive unit of the pump arrangement.
  • the rotor has a first conveying profile (e.g. the first toothing) on the inner circumferential surface, via which the inner conveying means communicates with the second conveying profile (e.g. a second toothing) arranged on the outer circumferential surface of the inner conveying means for conveying the fluid interacts.
  • first conveying profile e.g. the first toothing
  • second conveying profile e.g. a second toothing
  • a separate drive for the internal conveyor, e.g. B. via an axis of the internal conveyor is not necessary.
  • the rotor and the inner conveying means together form the pump of the pump arrangement, which supplies a fluid from a Suction side or low-pressure side (fluid inlet) promotes to a pressure side or high-pressure side (fluid outlet).
  • Gerotor pumps and internal gear pumps are suitable. Both pump types are characterized by parallel rotors, which are spaced apart in the radial direction and have axes of rotation of the teeth (inner conveyor and outer conveyor). Due to the meshing teeth, one conveyor is driven by the drive of the other conveyor.
  • the rotor and the conveying means are arranged in particular with sliding bearings.
  • a fluid film builds up in the sliding bearing, in particular in the bearing acting opposite the axial direction, which reduces the friction between components that move differently.
  • a first fluid guide structure is arranged between the first end face of the rotor and the stator or the stator-side housing and is connected to the pressure side, so that during operation of the pump arrangement there is a gap between the first end face and the stator or the stator-side Housing can be produced by the fluid.
  • the pressure of the fluid set by the pump arrangement on the pressure side is used here to adjust and maintain the distance along the axial direction between the first end face and the stator or the housing.
  • the distance between the electromagnetic rotor part (the magnets) and the electromagnetic stator part is in particular approximately 0.5 mm and becomes in particular not significantly influenced by the fluid.
  • the distance that arises during operation of the pump arrangement between the rotor and the stator or the stator-side housing as a result of the fluid and forms the gap is intended in particular exclusively to prevent friction between the components and thus wear.
  • the gap i.e. the distance formed by the fluid, is in particular significantly smaller than the distance between the electromagnetic components of the rotor and stator.
  • the first fluid guiding structure includes in particular a channel structure which is formed on at least one of the surfaces forming the gap. These surfaces are formed at least by the first end face of the rotor and by the wall of the stator or the housing opposite the first end face. In particular, there is no gap with a constant gap size, but rather the gap size varies locally as a result of the channel structure implemented on at least one surface.
  • the fluid can be conveyed through the gap (and across the gap) in particular at least along the radial direction via the channel structure. In particular, at least one flow channel is provided for the fluid, along which the fluid is conveyed through the gap (and across the gap).
  • the fluid should essentially be conveyed into the gap in order to reduce the friction between components there.
  • conveying the fluid beyond the gap is only a technically necessary evil in order to convey the fluid into the gap.
  • the fluid should not be specifically conveyed beyond the gap, but rather this internal leakage should be kept as low as possible.
  • a substantially constant pressure of the Fluids provided along the extent of the first fluid guide structure or along the channel structure in the gap.
  • the pump arrangement is designed in such a way that the axial forces acting between the stator and rotor are (just) compensated for by the pressure of the fluid on the pressure side generated during operation of the pump arrangement. If necessary, the pressure of the fluid in the gap between the rotor and stator can be adjusted via a (controllable or constant) throttle.
  • the rotor extends between a first end face facing the stator and an oppositely arranged second end face along the axial direction over a width, with the first conveyor profile and the second conveyor profile each extending over the (same) width.
  • the conveyor profiles in particular have the same width, so that the end faces of the inner conveyor and outer conveyor can be arranged in alignment with one another along the radial direction.
  • the second conveying profile cooperates with the first conveying profile to drive the inner conveying means, the inner conveying means being rotatably mounted on the centering element.
  • the internal conveying means is also stored exclusively via the fluid conveyed by the pump.
  • the first fluid guide structure is also formed on the inner conveying means, so that here too a gap between the inner conveying means and the centering element can be ensured by the fluid during operation of the pump arrangement.
  • the first fluid guiding structure is designed differently here between rotor and stator, since the axial forces essentially act between rotor and stator and are only transferred to the inner conveyor via contact friction of the conveyor profiles starting from the rotor or from the outer conveyor.
  • the housing has a pressure line connected to the pressure side of the pump arrangement on a second end face of the rotor arranged opposite the first end face.
  • the first fluid guide structure is connected to the pressure line (exclusively) via the centering element and/or via the conveying profiles.
  • the fluid is conveyed from the pressure line (exclusively) via the centering element to the first fluid guide structure.
  • the inner conveying means is rotatably mounted on a first outer peripheral surface of the centering element, with a second fluid-conducting structure for connecting the pressure line to the first fluid-conducting structure being formed at least partially on the first outer peripheral surface.
  • a hydrodynamic or hydrostatic mounting of the inner conveying means on the centering element can be realized.
  • the second fluid-conducting structure can in particular be designed in the manner of the first fluid-conducting structure, wherein the second fluid-conducting structure is provided to produce a gap between the centering element and the inner conveying means that runs parallel to the axis of rotation.
  • the fluid is conveyed starting from the pressure line via the centering element and via the second fluid guide structure to the first end face of the rotor.
  • the fluid (then, but in particular only as a leak) is conveyed outwards along the gap between the first end face and the stator and at least along the radial direction across the gap.
  • the fluid (then) flows over the second outer peripheral surface of the rotor (i.e. between the housing and rotor) towards the second end face and the suction side arranged there.
  • At least the rotor is manufactured using powder metallurgy.
  • at least the stator is manufactured using powder metallurgy.
  • the rotor is also manufactured using sintering technology.
  • the gap between the first end face of the rotor (in particular not in the area of the magnets) and the housing or the stator, i.e. in particular the gap forming the plain bearing or the gap formed by the first fluid guide structure, is in particular at least 0.003 millimeters during operation of the pump arrangement , preferably at most 0.1 millimeters, particularly preferably at most 0.05 millimeters or even at most 0.01 millimeters.
  • the gap between the magnets and the housing or the stator is at least 0.2 millimeters, preferably at least 0.3 millimeters.
  • Preferred the gap in this area is at most 1.5 mm, particularly preferably at most 1.0 mm, in particular 0.3 to 0.7 mm millimeters.
  • Fig. 7 shows a part of the pump arrangement 1 in a perspective view with the part of the flow path 34 Fig. 3 and another part of the flow path 34, which follows the flow path 34 Fig. 5 connects.
  • Fig. 8 shows the pump arrangement 1 Fig. 2 in a perspective view in section. The Fig. 1 to 8 are described together below.
  • the pump arrangement 1 comprises a pump 2 with a pressure side 3 and a suction side 4 and a drive unit 5 for the pump 2, which are arranged in a common housing 6.
  • the drive unit 5 is an axial flux electric drive, which includes exactly one stator 7, which is connected to the housing 6 in a rotationally fixed manner, and exactly one rotor 8, which is rotatably arranged relative to the housing 6.
  • the rotor 8 is arranged with a first end face 9 opposite the stator 7 along an axial direction 10 and forms an outer conveying means 11 of the pump 2.
  • the outer conveying means 11 has a first conveying profile 13 on an inner peripheral surface 12.
  • an inner conveying means 15 of the pump 2 is arranged, which has a second conveying profile 17 on an outer peripheral surface 16, which cooperates with the first conveying profile 13 to convey a fluid 18.
  • the inner conveying means 15 is mounted on a centering element 19 which is non-rotatably connected to the housing 6.
  • the rotor 8 and the external conveying means 11 are rotatably mounted relative to other components of the pump arrangement 1 exclusively via the fluid 18 conveyed by the pump 2.
  • a first fluid guide structure 20 is arranged between the first end face 9 and the stator 7 and is connected to the pressure side 3, so that a gap 21 between the first end face 9 and the stator 7 can be produced by the fluid 18 during operation of the electric drive.
  • the coil arrangement of the stator 7 has cores 32, e.g. B. from SMC, which are surrounded by current-carrying windings 31.
  • the rotor 8 has a first conveying profile 13 (here a first toothing) on the inner circumferential surface 12, via which the inner conveying means 15 is connected to the second conveying profile 17 (here a second toothing) arranged on the outer circumferential surface 16 of the inner conveying means 15 for conveying the Fluids 18 interact.
  • the conveyor profiles 13, 17 are designed as toothing
  • the inner conveyor 15 is driven via the outer conveyor 11.
  • a first axis of rotation 29 of the rotor 8 (and of the outer conveying means 11) and a second axis of rotation 30 of the inner conveying means 15 are arranged parallel to one another and spaced apart from one another in the radial direction 14.
  • the pump 2 is designed as a gerotor pump.
  • the rotor 8 extends between a first end face 9 facing the stator 7 and an oppositely arranged second end face 22 along the axial direction 10 over a width 23, with the first conveyor profile 13 and the second conveyor profile 17 each extending over the same width 23, the according to Fig. 2 According to the invention, extend over the width 23 of the rotor 8 and according to Fig. 1 and 3 to 8 (not according to the invention) only over part of the width 23 of the rotor 8.
  • the fluid 18 is conveyed starting from the pressure line 24 via the centering element 19 and/or the conveying profiles 13, 17 to the first fluid guide structure 20 along a flow path 34 (see Fig. 2 to 8 ).
  • the inner conveying means 15 is rotatably mounted on a first outer peripheral surface 25 of the centering element 19, with a second fluid-conducting structure 26 for connecting the pressure line 24 to the first fluid-conducting structure 20 being formed on the first outer peripheral surface 25.
  • the housing 6 has, on a second end face 22 of the rotor 8 arranged opposite the first end face 9, a suction line 27 connected to the suction side 4, with a leakage of the fluid from the first fluid guide structure 20 via a second outer peripheral surface 28 of the rotor 8 towards the Suction line 27 takes place.
  • the fluid 18 is conveyed starting from the pressure line 24 via the centering element 19 and via the second fluid guide structure 26 and possibly via the conveying profiles 13, 17 towards the first end face 9 of the rotor 8 (see Fig. 2 to 8 ). Then the fluid 18 is conveyed along the gap 21 between the first end face 9 and the stator 7 and at least along the radial direction 14 through the gap 21 and outwards as a leak across the gap 21 (see Fig. 2 , 3 , 7 and 8 ). The fluid 18 then flows as a leak over the second outer peripheral surface 28 of the rotor 8 (i.e. between the housing 6 and the rotor 8) to the second end face 22 and to the suction side 4 arranged there (see Fig. 2 and Fig. 8 ).
  • the rotor 8 comprises two components which are connected to one another via a connection which acts in a form-fitting manner relative to a circumferential direction 35.
  • the one component of the rotor 8 forms the first end face 9 and includes the magnets 33, the other component includes the outer conveying means 11.
  • rotating components (rotor 8, comprising the outer conveying means 11, inner conveying means 15) of the pump arrangement 1 are arranged in a contact-free manner relative to fixed components (housing 6, stator 7, centering element 19) of the pump arrangement 1. All rotating components are thus moved in the fluid 18.
  • the fluid 18 prevents contact between rotating components of the pump arrangement 1 and stationary components of the pump arrangement 1 or ensures a contact-free arrangement.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (10)

  1. Agencement de pompe (1), au moins comprenant une pompe (2) dotée d'un côté refoulement (3) et d'un côté aspiration (4) et une unité d'entraînement (5) pour la pompe (2), lesquelles sont disposées dans un carter (6) commun, l'unité d'entraînement (5) étant un entraînement électrique à flux axial qui comprend un stator (7) relié de manière bloquée en rotation au carter (6) ainsi qu'un rotor (8) disposé à rotation par rapport au carter (6), le rotor (8) étant disposé, par une première face frontale (9), de manière tournée vers le stator (7) le long d'une direction axiale (10) et formant un moyen de refoulement extérieur (11) de la pompe (2) et présentant un premier profil de refoulement (13) sur une surface périphérique intérieure (12), un moyen de refoulement intérieur (15) de la pompe (2) étant disposé à l'intérieur du rotor (8) dans une direction radiale (14), lequel moyen de refoulement intérieur présente un deuxième profilé de refoulement (17) sur une surface périphérique extérieure (16), lequel deuxième profilé de refoulement coopère avec le premier profilé de refoulement (13) pour le refoulement d'un fluide (18) ; caractérisé en ce que le moyen de refoulement intérieur (15) est supporté sur un élément de centrage (19) relié au carter (6) de manière bloquée en rotation ; au moins le rotor (8) et le moyen de refoulement extérieur (11) étant conçus pour être supportés exclusivement par le biais du fluide (18) refoulé par la pompe (2) ; une première structure de guidage de fluide (20) étant disposée au moins entre le premier côté frontal (9) et le stator (7) et étant reliée au côté refoulement (3), de sorte qu'un interstice (21) puisse être produit par le fluide (18) entre le premier côté frontal (9) et le stator (7) lors du fonctionnement de l'entraînement électrique.
  2. Agencement de pompe (1) selon la revendication 1, le rotor (8) s'étendant sur une largeur (23) entre le premier côté frontal (9) orienté vers le stator (7) et un deuxième côté frontal (22) disposé de manière opposée le long de la direction axiale (10), le premier profilé de refoulement (13) et le deuxième profilé de refoulement (17) s'étendent respectivement sur la largeur (23).
  3. Agencement de pompe (1) selon l'une des revendications précédentes, le deuxième profilé de refoulement (17) coopérant avec le premier profilé de refoulement (13) pour l'entraînement du moyen de refoulement intérieur (15), le moyen de refoulement intérieur (15) étant supporté à rotation sur l'élément de centrage (19) ; le moyen de refoulement intérieur (15) également étant supporté exclusivement par le biais du fluide (18) refoulé par la pompe (2).
  4. Agencement de pompe (1) selon l'une des revendications précédentes, le carter (6) présentant, au niveau d'un deuxième côté frontal (22) du rotor (8) disposé de manière opposée au premier côté frontal (9), une conduite de refoulement (24) reliée au côté refoulement (3), la première structure de guidage de fluide (20) étant reliée à la conduite de refoulement (24) par le biais de l'élément de centrage (19).
  5. Agencement de pompe (1) selon la revendication 4, le moyen de refoulement intérieur (15) étant supporté à rotation sur une première surface périphérique extérieure (25) de l'élément de centrage (19), une deuxième structure de guidage de fluide (26) servant à la liaison de la conduite de refoulement (24) à la première structure de guidage de fluide (20) étant formée au moins partiellement sur la première surface périphérique extérieure (25).
  6. Agencement de pompe (1) selon l'une des revendications précédentes, le carter (6) présentant, au niveau d'un deuxième côté frontal (22) du rotor (8) disposé de manière opposée au premier côté frontal (9), une conduite d'aspiration (27) reliée au côté aspiration (4), une fuite du fluide hors de la première structure de guidage de fluide (20) s'effectuant par le biais d'une deuxième surface périphérique extérieure (28) du rotor (8) en direction de la conduite d'aspiration (27).
  7. Agencement de pompe (1) selon l'une des revendications précédentes, le rotor (8) et le moyen de refoulement extérieur (11) étant réalisés d'une seule pièce.
  8. Agencement de pompe (1) selon l'une des revendications précédentes, au moins des composants (8, 11, 15) de l'agencement de pompe (1) qui tournent lors du fonctionnement de l'agencement de pompe (1) étant disposés sans contact par rapport à des composants fixes (6, 7, 19) de l'agencement de pompe (1).
  9. Agencement de pompe (1) selon l'une des revendications précédentes, au moins le rotor (8) étant produit par métallurgie des poudres.
  10. Agencement de pompe (1) selon l'une des revendications précédentes, la pompe (2) étant
    - une pompe gérotor ou une pompe à engrenages intérieurs et le premier profilé de refoulement (13) étant une première denture et le deuxième profilé de refoulement (17) étant une deuxième denture, les dentures présentant des nombres de dents différents l'un de l'autre ; ou
    - une pompe cellulaire à palettes ou une pompe cellulaire à rouleaux ;
    et un premier axe de rotation (29) du rotor (8) et un deuxième axe de rotation (30) du moyen de refoulement intérieur (15) étant disposés parallèlement l'un à l'autre et espacés l'un de l'autre dans la direction radiale (14).
EP20191931.3A 2020-08-20 2020-08-20 Agencement de pompe Active EP3957822B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
SI202030382T SI3957822T1 (sl) 2020-08-20 2020-08-20 Ureditev črpalke
EP20191931.3A EP3957822B1 (fr) 2020-08-20 2020-08-20 Agencement de pompe
PCT/EP2021/072836 WO2022038137A1 (fr) 2020-08-20 2021-08-17 Ensemble pompe
US18/022,109 US20230304494A1 (en) 2020-08-20 2021-08-17 Pump Assembly
CN202180050927.4A CN115943248A (zh) 2020-08-20 2021-08-17 泵组件

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20191931.3A EP3957822B1 (fr) 2020-08-20 2020-08-20 Agencement de pompe

Publications (2)

Publication Number Publication Date
EP3957822A1 EP3957822A1 (fr) 2022-02-23
EP3957822B1 true EP3957822B1 (fr) 2023-12-13

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EP20191931.3A Active EP3957822B1 (fr) 2020-08-20 2020-08-20 Agencement de pompe

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US (1) US20230304494A1 (fr)
EP (1) EP3957822B1 (fr)
CN (1) CN115943248A (fr)
SI (1) SI3957822T1 (fr)
WO (1) WO2022038137A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SI3957823T1 (sl) * 2020-08-20 2024-05-31 Gkn Sinter Metals Engineering Gmbh Ureditev črpalke

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2075469A2 (fr) * 2007-12-25 2009-07-01 Panasonic Electric Works Co., Ltd. Pompe à palettes
DE102010028061A1 (de) * 2010-04-22 2011-10-27 Robert Bosch Gmbh Flügelzellenpumpe
DE102011103493A1 (de) * 2011-06-03 2012-12-06 Linde Material Handling Gmbh Elektrische Maschine mit zwei Statoreinheiten und zwei Rotoreinheiten
DE102015207748A1 (de) 2015-04-28 2016-11-03 Gkn Sinter Metals Engineering Gmbh Fluidpumpe
DE102017113825B4 (de) 2017-06-22 2021-11-11 Lisa Dräxlmaier GmbH Verfahren zum Befeuchten von Klebstoff und System mit einer Kleberauftragsanlage
DE102017222754A1 (de) * 2017-12-14 2019-06-19 Magna Powertrain Bad Homburg GmbH Gerotor Pumpe
DE102018105136A1 (de) * 2018-03-06 2019-09-12 Gkn Sinter Metals Engineering Gmbh Verfahren zum Betreiben einer Pumpenanordnung

Also Published As

Publication number Publication date
SI3957822T1 (sl) 2024-05-31
EP3957822A1 (fr) 2022-02-23
US20230304494A1 (en) 2023-09-28
WO2022038137A1 (fr) 2022-02-24
CN115943248A (zh) 2023-04-07

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