EP3957822A1 - Agencement de pompe - Google Patents

Agencement de pompe Download PDF

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Publication number
EP3957822A1
EP3957822A1 EP20191931.3A EP20191931A EP3957822A1 EP 3957822 A1 EP3957822 A1 EP 3957822A1 EP 20191931 A EP20191931 A EP 20191931A EP 3957822 A1 EP3957822 A1 EP 3957822A1
Authority
EP
European Patent Office
Prior art keywords
pump
rotor
fluid
conveying means
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.)
Granted
Application number
EP20191931.3A
Other languages
German (de)
English (en)
Other versions
EP3957822B1 (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 EP20191931.3A priority Critical patent/EP3957822B1/fr
Priority to SI202030382T priority patent/SI3957822T1/sl
Priority to CN202180050927.4A priority patent/CN115943248A/zh
Priority to PCT/EP2021/072836 priority patent/WO2022038137A1/fr
Priority to US18/022,109 priority patent/US20230304494A1/en
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 flow electric drive, which comprises a stator which is non-rotatably connected to the housing and a rotor which is arranged such that it can rotate with respect to the housing.
  • the rotor forms an outer 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 peripheral surface, with an inner conveying means of the pump being arranged in a radial direction inside the rotor, which is on a Outer peripheral surface has a second conveying profile (e.g. a second toothing or a cylindrical outer peripheral surface), which interacts with the first conveying profile for conveying a fluid and optionally (in the case of the teeth) for driving the inner conveying means through the rotor.
  • a first conveying profile e.g. a first toothing or van
  • a rotor of the pump is arranged on an axle that is led out of a housing of the pump arrangement.
  • a pump assembly is z. B. from the DE 10 2015 207 748 A1 famous.
  • a fluid pump is described, which 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 whose electric motor rotor 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 integrated in a disk shape as a combination rotor, the common housing having a fluid inlet and a fluid outlet to the combination rotor.
  • a pump room or fluid delivery chamber is closed off in the common housing and a fluid inflow and a fluid outflow to the pump chamber takes place axially along the axis of rotation.
  • a pump arrangement which comprises at least one pump and a drive unit for the pump, which are arranged in a common housing.
  • the drive unit is an axial flow electric drive, which comprises a stator which is non-rotatably connected to the housing and a rotor which is arranged such that it can rotate with respect to the housing.
  • the rotor forms an outer conveying means of the pump, with an inner conveying means of the pump being arranged in a radial direction inside the rotor, which is connected to the first conveying profile for conveying a fluid and, if necessary (in the case of the teeth) for driving the inner conveying means by the rotor interacts.
  • the inner conveyor is arranged on a sleeve. A mechanical bearing of the outer conveyor and the rotor is not provided. In order to set an operation that is as leak-free as possible, the side walls surrounding the rotor are set at a certain distance from one another by means of a traction mechanism.
  • 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 flow electric drive, which (precisely) comprises a stator non-rotatably connected to the housing and (precisely) a rotor arranged rotatably relative to the housing.
  • the rotor is arranged with a first end side opposite the stator or a stator-side housing (ie a housing enclosing the stator) along an axial direction and forms an external conveying means of the pump.
  • the outer conveying means has a first conveying profile on an inner peripheral surface.
  • An inner conveying means of the pump is arranged in a radial direction inside the rotor and has a second conveying profile on an outer peripheral surface, which interacts with the first conveying profile for conveying a fluid.
  • the inner conveying means is mounted on a centering element which is non-rotatably connected to the housing. At least the rotor and the outer conveying means are set up to be mounted exclusively on the fluid conveyed by the pump (rotatable in relation to other components of the pump arrangement).
  • a first fluid conducting structure is arranged at least between the first end face (of the rotor/outer conveying means) and the stator (or the housing on the stator side) and is connected to the pressure side, so that when the pump arrangement is in operation, there is a gap between the first end face and the stator (or the stator-side housing) can be produced by the fluid.
  • Electrical drives regularly include a stator and a rotor, which are arranged coaxially to one another.
  • the rotor is referred to herein as the carrier of permanent magnets, while the stator comprises a coil assembly.
  • the rotor and stator are particularly along the axial arranged one behind the other. Differently magnetized magnets are alternately arranged on the rotor along the circumferential direction.
  • the coil assembly of a stator has cores, e.g. B. from SMC, which are surrounded by current-carrying windings.
  • Each core may be an element arranged to become magnetized when a current is passed through live windings around the core.
  • the current-carrying windings can be designed as coils.
  • SMC is formed from iron powder particles which are electrically insulated from one another. Iron losses in SMC parts in an alternating electric field are generally small. In this regard, it therefore seems desirable to use SMC in electrical machines, at least in part, instead of the most commonly used steel lamination (steel sheets or electrical steel). To form a component from SMC, the particles are compacted and hardened. The SMC material is not sintered here. Rather, tempering takes place below a melting temperature, which is however sufficient for the material to permanently retain the intended geometry.
  • the rotor of the electric drive can have permanent magnets or else soft-magnetic elements, for example in recesses.
  • a permanently excited synchronous or brushless DC motor, abbreviated BLDC can be formed with permanent magnets as an electric drive, while a reluctance motor can be created as an electric motor in an axial, radial or transverse design with soft magnetic elements, for example.
  • the rotor has a first conveying profile (e.g. the first toothing) on the inner peripheral surface, via which the inner conveying means is connected to the second conveying profile (e.g. a second toothing) arranged on the outer peripheral surface of the inner conveying means for conveying the fluid works together.
  • first conveying profile e.g. the first toothing
  • second conveying profile e.g. a second toothing
  • the inner conveying means is driven by the outer conveying means.
  • the rotor and inner conveying means together form the pump of the pump arrangement, which conveys a fluid from a suction side or low-pressure side (fluid inlet) to a pressure side or high-pressure side (fluid outlet).
  • Gerotor pumps and internal gear pumps are suitable. Both pump types are characterized by rotors that are parallel but spaced apart from one another in the radial direction and have axes of rotation of the toothing (inner conveying means and outer conveying means). Due to the meshing teeth, one conveyor is driven by the drive of the other conveyor.
  • Vane cell pumps and roller cell pumps can also be used as the pump arrangement, with the outer conveying means comprising the vanes or rollers, which can be displaced in a radial direction relative to the axis of rotation, as the first conveying profile.
  • the second funding profile is z. B. formed by a cylindrical outer peripheral surface of the inner conveyor, which cooperates with the wings or the rollers.
  • the rotor and the conveying means are arranged in particular with plain bearings.
  • a fluid film builds up in the sliding bearing, in particular in the bearing acting opposite to the axial direction, which reduces the friction between components that move differently.
  • the rotor in particular together with the outer conveying means, is in particular designed without a shaft or is arranged without bearings or only with sliding bearings in relation to the radial direction.
  • tilting of the rotor is prevented or reduced, among other things, in particular by the largest possible diameters of the surfaces of the rotor acting as bearings in relation to the axial direction.
  • a first fluid conducting 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 set 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, in particular, is not appreciably influenced by the fluid.
  • the distance that occurs during operation of the pump arrangement between the rotor and stator or stator-side housing as a result of the fluid and forms the gap is in particular intended exclusively to prevent friction between the components and thus wear.
  • the gap, ie 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 guide structure comprises in particular a channel structure which is formed at least on 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 housing lying opposite the first end face. In particular, therefore, there is no gap with a constant gap size, 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.
  • at least one flow channel is used 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 conveyed in a targeted manner beyond the gap, but this internal leakage should be kept as small as possible.
  • a substantially constant pressure of the fluid is provided in the gap along the extension of the first fluid guide structure or along the channel structure.
  • a throttled pressure can definitely be present between different flow channels of a channel structure.
  • the pump arrangement is designed in such a way that the pressure of the fluid on the pressure side generated during operation of the pump arrangement compensates for the axial forces acting between the stator and the rotor (straightforward). If necessary, the pressure of the fluid in the gap between the rotor and the stator can be adjusted via a (controllable or constant) throttle.
  • the rotor extends over a width between a first end face facing the stator and an oppositely arranged second end face along the axial direction, with the first conveying profile and the second conveying profile each extending over the (same) width.
  • the conveyor profiles have in particular the same width, so that the end faces of inner conveying means and outer conveying means can be arranged in alignment with one another along the radial direction.
  • the second conveying profile interacts with the first conveying profile to drive the inner conveying means, with the inner conveying means being rotatably mounted on the centering element.
  • the inner conveying means is also supported exclusively by the fluid conveyed by the pump.
  • the first fluid guide structure is also formed on the inner conveying means, so that a gap between the inner conveying means and the centering element can also be ensured here by the fluid during operation of the pump arrangement.
  • the first fluid guide structure is designed differently here than between the rotor and stator, since the axial forces act essentially between the rotor and stator and are only transmitted via contact friction of the conveying profiles starting from the rotor or from the outer conveying means to the inner conveying means.
  • the housing has a pressure line connected to the pressure side of the pump arrangement.
  • the first fluid guide structure is (exclusively) connected to the pressure line 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 conducting structure.
  • the inner conveyor 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 storage of the inner funding can be realized on the centering.
  • the second fluid conducting structure can in particular be designed in the manner of the first fluid conducting structure, the second fluid conducting structure being provided for generating a gap running parallel to the axis of rotation between the centering element and the inner conveying means.
  • the housing has a suction line connected to the suction side.
  • a transfer of the fluid from the first fluid guide structure which can be described as leakage, takes place in particular via a second outer peripheral surface of the rotor to the suction line. This leakage serves in particular to lubricate the opposing surfaces of the rotor and housing.
  • a fluid can be conveyed through the conveying profiles, starting from the suction line to the pressure line.
  • the amount of fluid used to lubricate and support the components and to ensure the gap can flow (back) at least partially (as leakage) from the pressure side across the gap to the suction side.
  • 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 via the second outer peripheral surface of the rotor (ie between the housing and the rotor) towards the second end face and to the suction side arranged there.
  • the rotor and the outer conveying means are designed in one piece, preferably in one piece, ie manufactured together.
  • rotating components rotor, outer conveying means, inner conveying means, the pump arrangement relative to stationary components (housing, stator, centering element) of the pump arrangement are arranged without contact.
  • stationary components housing, stator, centering element
  • all rotating components run in the fluid.
  • the fluid prevents contact between rotating components of the pump arrangement and stationary components of the pump arrangement, or ensures a non-contact arrangement.
  • tolerances of the components that would otherwise have to be produced with high precision can be softened, so that costs for the production of the pump arrangement can be reduced.
  • the perpendicularity that is otherwise required between the axis of rotation and the first end face is to be implemented here in particular with less accuracy, since the gap between the rotor and the housing or stator is ensured by the fluid.
  • At least the rotor is manufactured using powder metallurgy.
  • at least the stator is manufactured by powder metallurgy.
  • the rotor is also manufactured by sintering.
  • the pump arrangement has exclusively static seals, that is to say seals which are only arranged between components which are arranged in a rotationally fixed manner. In this way, a secure and permanent seal can be guaranteed using exclusively static seals.
  • the gap between the first end face of the rotor (especially 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.
  • the gap in this area is preferably at most 1.5 mm, particularly preferably at most 1.0 mm, in particular 0.3 to 0.7 mm.
  • first primarily (only) serve to distinguish between several similar objects, sizes or processes, i.e. in particular no dependency and/or sequence of these objects, sizes or make processes mandatory for each other. Should a dependency and/or order be necessary, this is explicitly stated here or it is obvious to the person skilled in the art when studying the specifically described embodiment. If a component can occur more than once (“at least one"), the description of one of these components can apply equally to all or part of the majority of these components, but this is not mandatory.
  • the 1 shows a pump assembly 1 in an exploded view, in a perspective view.
  • 2 shows a pump arrangement 1 in a side view in section with an illustration of the flow path 34 of the fluid 18 from a pressure side 3 to a suction side 4.
  • 3 shows the pump arrangement 1 in a side view in section with the flow path 34 from the pressure side 3 to the first end face 9.
  • 4 1 shows part of the pump arrangement 1 in a perspective view with part of the flow path 34 3 .
  • figure 5 1 shows a part of the pump arrangement 1 in a perspective view with a further part of the flow path 34 3 , Which follows the course of flow 34 4 connects.
  • 6 shows a part of the pump arrangement 1 after 3 in a perspective view.
  • FIG. 7 12 shows a part of the pump arrangement 1 in a perspective view with the part of the flow path 34 after 3 and another part of the flow path 34, which follows the flow path 34 figure 5 connects.
  • 8 shows the pump arrangement 1 after 2 in a perspective view in section. the Figures 1 to 8 are described together below.
  • the 1 and 3 to 8 are not shown according to the invention only in relation to the rotor 8, the outer conveyor 11 and the inner conveyor 15.
  • the rotor 8 is shown as an assembly consisting of two components.
  • the funding profiles 13, 17 of the conveying means 11, 15 do not extend as far as the first end face 9 but over a smaller width 23 than the rotor 8.
  • 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 flow electric drive, which comprises precisely one stator 7 connected in a torque-proof manner to the housing 6 and precisely one rotor 8 arranged such that it can rotate with respect 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 in a radial direction 14 inside the rotor 8 and has a second conveying profile 17 on an outer peripheral surface 16 which interacts with the first conveying profile 13 for conveying 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 outer 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 can be created between the first end face 9 and the stator 7 through the fluid 18 during operation of the electric drive.
  • the coil assembly of the stator 7 has cores 32, e.g. B. from SMC, which are comprised of current-carrying windings 31.
  • the rotor 8 of the electric drive has magnets 33 .
  • Cores 32 and windings 31 are spaced apart from magnets 33 by gap 21 .
  • the rotor 8 has a first conveying profile 13 (here a first toothing) on the inner peripheral surface 12, via which the inner conveying means 15 and the second conveying profile 17 (here a second toothing) arranged on the outer peripheral surface 16 of the inner conveying means 15 for conveying the Fluid 18 interacts.
  • first conveying profile 13 here a first toothing
  • second conveying profile 17 here a second toothing
  • the inner conveying means 15 is driven via the outer conveying means 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 .
  • Pump 2 is designed as a gerotor pump.
  • a gap 21 is set between the first end face 9 and the stator 7 by the fluid 18 during operation of the electric drive by the first fluid guide structure 20 which is arranged between the first end face 9 and the stator 7 and is connected to the pressure side 3 .
  • the pressure of the fluid 18 set by the pump arrangement 1 on the pressure side 3 is used here to set and maintain the distance along the axial direction 10 between the first end face 9 and the stator 7 or the housing 6 .
  • 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 conveying profile 13 and the second conveying profile 17 each extending over the same width 23, the according 2 extend according to the invention over the width 23 of the rotor 8 and according to 1 and Figures 3 to 8 (not according to the invention) only over part of the width 23 of the rotor 8.
  • the housing 6 On a second end face 22 of the rotor 8 arranged opposite the first end face 9, the housing 6 has a pressure line 24 connected to the pressure side 3 (see FIG 4 ), wherein the first fluid guide structure 20 via the centering element 19 and/or via the conveying profiles 13, 17 (see 2 , to the left of the axes of rotation 29, 30: the connection between the pressure line 24 and the first fluid guide structure 20 is also connected to the pressure line 24 exclusively via conveying profiles 13, 17).
  • the fluid 18 is conveyed 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 Figures 2 to 8 ).
  • the inner conveying means 15 is rotatably mounted on a first outer peripheral surface 25 of the centering element 19 , 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 On a second end face 22 of the rotor 8 arranged opposite the first end face 9, the housing 6 has a suction line 27 connected to the suction side 4, with leakage of the fluid from the first fluid conducting 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 via the centering element 19 and via the second fluid guide structure 26 and, if necessary, via the conveying profiles 13, 17 towards the first end face 9 of the rotor 8 (see FIG Figures 2 to 8 ). Then the fluid 18 flows 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 as a leakage conveyed outwards across the gap 21 (see 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) towards the second end face 22 and the suction side 4 arranged there (see Fig 2 and 8 ).
  • the rotor 8 comprises two components which are connected to one another via a connection which acts in a form-fitting manner in relation to a circumferential direction 35 .
  • 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, including the outer conveying means 11, inner conveying means 15) of the pump assembly 1 are arranged without contact with respect to fixed components (housing 6, stator 7, centering element 19) of the pump assembly 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 non-contact 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)
EP20191931.3A 2020-08-20 2020-08-20 Agencement de pompe Active EP3957822B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP20191931.3A EP3957822B1 (fr) 2020-08-20 2020-08-20 Agencement de pompe
SI202030382T SI3957822T1 (sl) 2020-08-20 2020-08-20 Ureditev črpalke
CN202180050927.4A CN115943248A (zh) 2020-08-20 2021-08-17 泵组件
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

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 true EP3957822A1 (fr) 2022-02-23
EP3957822B1 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)

Citations (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
DE102017113825A1 (de) 2017-06-22 2018-12-27 Lisa Dräxlmaier GmbH Befeuchten von klebstoff
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

Patent Citations (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
DE102017113825A1 (de) 2017-06-22 2018-12-27 Lisa Dräxlmaier GmbH Befeuchten von klebstoff
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
WO2022038137A1 (fr) 2022-02-24
CN115943248A (zh) 2023-04-07
EP3957822B1 (fr) 2023-12-13
SI3957822T1 (sl) 2024-05-31
US20230304494A1 (en) 2023-09-28

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