EP3546752A1 - Rotationspumpe - Google Patents

Rotationspumpe Download PDF

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Publication number
EP3546752A1
EP3546752A1 EP19166411.9A EP19166411A EP3546752A1 EP 3546752 A1 EP3546752 A1 EP 3546752A1 EP 19166411 A EP19166411 A EP 19166411A EP 3546752 A1 EP3546752 A1 EP 3546752A1
Authority
EP
European Patent Office
Prior art keywords
rotor
pump
lubricant supply
rotary pump
pump chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP19166411.9A
Other languages
German (de)
English (en)
French (fr)
Inventor
Michael Ehringer
Gerd Jäggle
Sven Peters
Holger Braasch
Winfried Baur
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 EP3546752A1 publication Critical patent/EP3546752A1/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—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
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for 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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/0238—Rotary pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C2240/30—Casings or housings

Definitions

  • the invention relates to a rotary pump whose direction of rotation or conveying direction can preferably be switched over, with a housing having a pump chamber with an inlet for a fluid or medium to be pumped into a low pressure region of the pump chamber and an outlet for the fluid or medium to be pumped from a high pressure region of the pump pump room.
  • the pump further comprises at least one rotor, which forms delivery cells in the pump space, and at least one bearing for the at least one rotor and / or for a rotor shaft connected to the rotor.
  • the pump comprises a sealing web axially facing the rotor, which separates the low pressure region in the direction of rotation of the rotor from the high pressure region.
  • a first aspect of the invention relates to a rotary pump, preferably with a reversible direction of rotation, with a housing having a pump chamber with an inlet for a fluid or medium to be pumped into a low-pressure region of the pump Pump space and an outlet for the fluid to be pumped or medium from a high pressure region of the pump chamber, at least one rotor which forms delivery cells in the pump chamber, at least one bearing for the at least one rotor and / or for a rotor shaft connected to the rotor and with a Rotor axially facing sealing land, which separates the low pressure area in the direction of rotation of the rotor from the high pressure area.
  • the rotary pump has at least one lubricant feed in the sealing web, which supplies a fluid from at least one of the feed cells to the bearing.
  • the sealing web and the rotor form an axial sealing gap. In or through the supply of lubricant, the axial sealing gap between the sealing web and the rotor is increased.
  • the rotary pump is designed as an external gear pump with reversible direction of rotation.
  • the housing may comprise one or more parts, for example one or more covers, to close off openings.
  • Parts of the housing may form part of the pump chamber, for example an axial cover for the pump chamber or a peripheral wall or a cup-shaped structure for receiving the at least one rotor.
  • the rotor may be connected or coupled to a drive, such as an electric motor and / or a shaft driven by an internal combustion engine, which generates the drive energy for the rotor.
  • a drive such as an electric motor and / or a shaft driven by an internal combustion engine, which generates the drive energy for the rotor.
  • the rotor is connected to a rotor shaft.
  • the rotor shaft is preferably rotatably mounted in the bearing.
  • the rotor shaft is advantageously connected or coupled to the drive.
  • a direction of rotation or conveying direction of the rotary pump or of the at least one rotor can preferably be switched, so that the pump can be used flexibly.
  • the outlet of the pump which rotates in the first direction of rotation, becomes the inlet for the same pump, which now rotates in the second direction of rotation.
  • the inlet of the pump which is after a change in the direction of rotation of the pump to the outlet.
  • the inlet opens into a low pressure area and the outlet into a high pressure area of the pump. Switching the direction of rotation of the pump changes Thus, the flow direction of the fluid to be pumped or medium by the pump, which in other words is a reversible rotary pump.
  • the fluid or medium to be pumped may be a lubricant, such as a lubricating oil, supplied to one or more units of, for example, the high pressure side of the pump via hoses or lines to lubricate the aggregates.
  • the fluid or medium to be pumped may be a cooling or actuating fluid. But it can also be a fluid or medium for a different purpose, for example, fuel oil, heavy oil or diesel.
  • the fluid to be pumped is also used to lubricate the bearing.
  • the low pressure side of the pump may be fluidly connected to a reservoir for the fluid or medium to be pumped.
  • the lubricant supply is preferably suitable for reliably supplying the bearing with the fluid or medium regardless of the direction of rotation or conveying direction of the pump.
  • the lubricant supply can preferably be short-circuited in any position of the rotor in the pump chamber with the inlet to the pump chamber and the outlet from the pump chamber. That is, a direct fluidic connection of the lubricant supply to the inlet and the outlet should be excluded.
  • a short circuit to the inlet or suction side of the pump may reduce, prevent, or even reverse a flow of lubricant through the lubricant supply to the bearing, which could result in undersupplying of the bearing with lubricant. The result could be damage to the point of destruction of the rotary pump.
  • lubricant supply is prevented in both directions of rotation that the lubricant supply to the inlet is shorted.
  • a change in the direction of rotation through which an outlet becomes the inlet does not change the lubricant supply of the bearing.
  • the housing may have a radially surrounding the pump chamber inner peripheral wall, which together with the at least one rotor for sealing adjacent conveying cells forms a radial sealing gap.
  • This sealing gap or a radial width of this sealing gap, can change in size in the direction of rotation. That is, a distance between an imaginary radial outer circumferential circle of the rotor, which includes, for example, the radial ends of conveying elements, which delimit adjacent conveying cells in the direction of rotation of the pump, and the radial inner peripheral wall of the pump chamber can be different in size.
  • a radial dimension of the sealing gap, in particular in a peripheral region, in which the lubricant supply is formed be smaller than a mean radial distance between the circumferential circle and the inner peripheral wall.
  • the radial sealing gap in the peripheral region of the lubricant supply can be smaller than a middle radial sealing gap.
  • axial and radial are particularly related to the axis of rotation of the rotor or the rotor shaft, so that the term “axially” in particular denotes a direction which is parallel or coaxial with the axis of rotation. Further, the term “radial” refers in particular to a direction which is perpendicular to the axis of rotation.
  • the radial sealing gap can have a uniform or a varying dimension in the axial direction.
  • the radial sealing gap can also change in size in the axial direction.
  • To increase the radial sealing gap in a peripheral region of the radial sealing gap can be increased only over an axial length of the peripheral portion.
  • To reduce the radial sealing gap in a peripheral region, the radial sealing gap can be reduced only over an axial partial length of the peripheral region.
  • the radial sealing gap is preferably enlarged or reduced over its entire axial length.
  • the radial sealing gap in the circumferential region in which the radial sealing gap is larger than the radial sealing gap in at least one other circumferential region, can be greater over an axial partial length or over its entire axial length than the radial sealing gap in the at least one other peripheral region.
  • the radial sealing gap in the peripheral region, in which the radial sealing gap is smaller than the radial sealing gap in at least one other Peripheral region, over an axial length or over its entire axial length may be smaller than the radial sealing gap in the at least one other peripheral region.
  • a lubricant supply is formed, for example, only in an axial end wall of the pump chamber, in particular the larger sealing gap can also be formed only over an axial partial length on the side of the lubricant supply.
  • a lubricant supply in both axial end walls of the pump chamber may be formed on both sides of the larger sealing gap only over an axial length, the two partial axial lengths are separated by a web, for example, has the dimension of the smaller sealing gap.
  • the web may in turn have interruptions in order to fluidly connect the two partial axial lengths.
  • the radial sealing gap can preferably be larger than the sealing gap in the peripheral region of the lubricant supply in the peripheral region of the pump chamber between the low-pressure region or inlet into the pump chamber and the lubricant supply and / or between the high-pressure region or outlet from the pump chamber and the lubricant supply. Due to the larger radial sealing gap, a certain preferred defined leakage between the conveyor cells should be set. Due to the smaller radial sealing gap in the peripheral region of the lubricant supply, therefore, the delivery cells, which are currently overflowing the lubricant supply, are better sealed in relation to the other delivery cells. This ensures that the bearing is supplied with sufficient lubricant, or the lubricant pressure is high enough, for example, to promote the lubricant safely into the camp.
  • grooves in the inner circumferential wall and / or in the rotor facing inner sides of the axial end walls of the pump chamber may be formed in the peripheral region in which no lubricant supply is arranged in the pump chamber , which connect adjacent delivery cells in the peripheral areas of the pump chamber without lubricant supply to each other and thus provide for the leakage.
  • the peripheral region In the direction of rotation of the rotor, the peripheral region extends with the smaller sealing gap in the peripheral region of the lubricant supply via a peripheral portion of the inner peripheral wall, which is larger than a conveyor cell.
  • the peripheral region with the smaller sealing gap extends, for example, over two or more delivery cells. In the case of the sealing gap, this preferably means that the extent of the peripheral region with the smaller sealing gap in the direction of rotation of the rotor is greater than an extension in the direction of rotation of the one conveying cell on the imaginary circle of the rotor.
  • the radial sealing gap can be referred to as head play, in particular in the case of a gear pump.
  • the radial sealing gap is preferably formed between a tooth tip of a rotor designed as a gear and the inner peripheral wall.
  • the radial sealing gap or the head clearance in the peripheral region of the inner peripheral wall, which is radially opposite the lubricant supply a maximum of 100 microns.
  • the radial sealing gap or the head clearance in the peripheral region of the inner circumferential wall, which is radially opposite the lubricant supply smaller than 100 microns and most preferably less than 75 microns.
  • the radial sealing gap or the head clearance in the peripheral region of the inner circumferential wall between the lubricant supply and the low pressure region or the high pressure region at least 1.5 times and more preferably at least 2 times greater than the radial sealing gap or head clearance in the peripheral region of the inner peripheral wall, which the lubricant supply radially opposite.
  • the radial sealing gap or the head clearance in the peripheral region of the inner peripheral wall between the lubricant supply and the low pressure region or the high pressure region is a maximum of 2.5 times and more preferably at most 3 times greater than the radial sealing gap or the head clearance in the peripheral region of the inner peripheral wall, which the lubricant supply radially opposite.
  • the larger radial sealing gap is at least 1.5 times and particularly advantageously at least 2 times larger than the smaller radial sealing gap.
  • the larger radial sealing gap is advantageously at most 2.5 times and particularly advantageously at most 3 times larger than the smaller radial sealing gap.
  • the supply of lubricant may in particular be a depression or a groove which extends, preferably beginning at the bearing, in the radial direction so far that it is overflowed successively by the delivery cells when the rotor rotates.
  • the recess may be a straight line which lies, for example, on a beam which intersects or runs parallel to an axis of rotation of the rotor or of the rotor shaft.
  • the depression may also be curved or wavy or take any other shape.
  • the recess may have branches or extensions that extend in or against the direction of rotation of the rotor.
  • the recess may be L-shaped. Be formed T-shaped, Y-shaped, F-shaped or V-shaped, without being limited to these training.
  • the shape of the recess may be arbitrary, for example, U-shaped, V-shaped or rectangular, the depth of the recess may vary.
  • an end facing away from the bearing of the recess and / or the sides of the recess at least partially open a slope in the rotor facing the inside of the axial wall of the pump chamber, so that the lubricant can flow into the recess.
  • the recess may open into the bearing at one end and the mouth may be the only connection of the recess to the bearing.
  • the recess may be connected to the bearing via one or more channels, so that the lubricant can be supplied to the bearing at several points at the same time.
  • the lubricant supply may be centrally located in the seal land, that is, have a substantially equal distance to a nearest edge of the facing ends of the outlet and the inlet. Due to the central or central arrangement, the geometry of the pump relative to the lubricant supply with the corresponding shape of the recess in both directions of rotation is identical.
  • the inlet and the outlet can be formed in the pump chamber substantially the same.
  • the lubricant supply may be arranged off-center in the sealing web, preferably closer to the inlet for the medium to be pumped in the first direction of rotation. This can be useful if the rotary pump is a preferred first and a less preferred second direction of rotation or conveying direction.
  • the eccentric arrangement of the lubricant supply is advantageous because in main operation in the first direction of rotation or conveying direction, a distance of the lubricant supply to the inlet is greater than in the central arrangement, which is avoided with an additional security that the lubricant guide to the inlet to be shorted can.
  • the rotary pump may in particular be an external-axis pump, such as an external gear pump.
  • the pump can be designed in planetary gear design, that is, the pump includes, for example, a driven gear that drifts on several other gears, or vice versa.
  • Such pumps with a planetary gear are, for example, from DE 10 2010 056 106 B4 , of the EP 1 801 418 A1 , of the EP 0 300 293 A2 and the WO 2008/062023 A1
  • the invention is not limited to the exemplary embodiments illustrated and described there, but also includes pumps differing therefrom, in particular external-axis pumps, such as external gear pumps.
  • the lubricant supply may be a groove in the sealing land or comprise a groove.
  • the groove may be rectangular in a section transverse to its longitudinal axis, U-shaped or V-shaped or formed as desired.
  • a width and a length of the groove may be adapted to the rotary pump.
  • the groove may be funnel-shaped at its end facing the bearing and / or facing away from the bearing.
  • the longitudinal sides of the groove may be parallel to each other or may be inclined towards or away from each other in the direction of the bearing, so that a width of the groove changes continuously over the length.
  • the same can apply to the depth of the groove.
  • the shape such as length, width and depth of the groove is not fixed, but can be chosen freely by the skilled person.
  • a groove may also divide deltatone so that the groove comprises at least one of its ends a plurality of arms. Finally, the groove does not have to form a straight line, but may for example be slightly bent.
  • the lubricant supply may include a pocket in the seal land.
  • the bag can end directly at the bearing or via a groove or a hole with be connected to the camp.
  • the bag can be round, oval, rectangular or any length, width and depth.
  • a short circuit to the inlet or suction side of the pump may reduce, prevent, or even reverse a flow of lubricant through the lubricant supply to the bearing, which could result in undersupplying of the bearing with lubricant. The result could be damage to the point of destruction of the rotary pump.
  • An imaginary extension of the groove or bore, or an axial center axis of the groove or bore, may intersect an axis of rotation of the rotor or a straight line parallel to the axis of rotation of the pump. That is, the imaginary extension of the groove can impinge at least at one point on a circumferential outer surface of the bearing perpendicular or at an angle that can be specified on the design side.
  • the lubricant supply may extend from the bearing to between the inlet and the outlet.
  • the bearing facing the end of the lubricant supply may be open, the end facing away from the bearing of the groove-shaped lubricant supply without bag can be closed.
  • the pump chamber is limited at its axial ends usually by a cover and a bottom.
  • the inlet, the outlet, the sealing ridge and the lubricant supply can optionally be formed in the lid or in the bottom of the pump chamber or both in the lid and in the bottom of the pump chamber.
  • the rotary pump may comprise two inlets into the low-pressure region of the pump chamber, two outlets from the high-pressure region of the pump chamber, two sealing webs axially facing the rotor, which separate the low-pressure region from the high-pressure region in the direction of rotation of the rotor, and one lubricant supply in each of the two sealing webs.
  • the rotary pump may have two rotors in the form of gears, which mesh with each other in a drive way in a known manner.
  • Each of the two rotors or each of the two rotor shafts has a bearing, and each of the bearings is associated with a prescribed lubricant supply.
  • the two lubricant feeders can be connected to each other via the drive bridge.
  • Each of the rotors may be associated with a lubricant guide as described above, two of the lubricant supply lines or all three lubricant supply lines may be connected to one another via a drive web or the drive webs. If the rotary pump has more than three gears, what has been said applies accordingly.
  • sealing ridge preferably lacks a meshing engagement of the rotors designed as gears.
  • the delivery cells which supply the lubricant supply with the fluid or medium are advantageously bounded or formed by the axially opposite sealing webs, the inner peripheral wall and the rotor.
  • the rotor may be connected or coupled to a drive, such as an electric motor or a shaft driven by an internal combustion engine, which generates the drive energy for the rotor.
  • a drive such as an electric motor or a shaft driven by an internal combustion engine, which generates the drive energy for the rotor.
  • the rotor is connected to an electric motor and provided in particular for use in a motor vehicle. If the motor vehicle has an internal combustion engine as a drive, then the rotary pump can be driven by the electric motor, preferably independently of the internal combustion engine, for example when the internal combustion engine is at a standstill.
  • the rotary pump may advantageously have the electric motor.
  • the rotary pump is preferably designed as an electric rotary pump.
  • the rotary pump can be designed as an auxiliary pump and / or an auxiliary pump for supporting and / or for at least partially replacing a main or primary pump in a lubricant and / or coolant system of the motor vehicle.
  • the rotary pump may be provided for lubricating and / or cooling a drive motor and / or a transmission of the motor vehicle.
  • the motor vehicle may be an internal combustion engine driven motor vehicle, an electric motor driven motor vehicle or a Hybrid vehicle with an internal combustion engine and an electric motor.
  • “trained” is meant in particular specially vpronce understood, executed, arranged and / or programmed.
  • a second aspect of the invention relates to a rotary pump, preferably with a reversible direction of rotation, with a housing having a pump chamber with an inlet for a fluid or medium to be pumped into a low-pressure region of the pump chamber and an outlet for the fluid or medium to be pumped from a high-pressure region of the pump Pump chamber has, at least one rotor which forms feed cells in the pump chamber, at least one bearing for the at least one rotor and / or for a rotor shaft connected to the rotor and with a rotor axially facing the sealing web which separates the low pressure region in the direction of rotation of the rotor from the high pressure region ,
  • the housing has an inner circumferential wall radially delimiting the pump chamber, which forms a radial sealing gap together with the at least one rotor for sealing adjacent delivery cells, the size of the radial sealing gap being changed in the direction of rotation of the rotor.
  • the inner peripheral wall has at least a first circumferential region between the low-pressure region and the high-pressure region and at least one second circumferential region between the low-pressure region and the high-pressure region, wherein the radial sealing gap in the first circumferential region is greater than the radial sealing gap in the second circumferential region.
  • the rotary pump preferably lacks a lubricant supply as described in the first aspect.
  • An axial sealing gap between the sealing web and the rotor is preferably constant or identical in the direction of rotation.
  • a supply of the bearing with the pumped fluid is preferably carried out via the axial sealing gap. Due to the second peripheral region, which has the smaller radial sealing gap, the supply of the bearing with the pumped fluid is improved.
  • the rotary pump of the second aspect may be formed like the rotary pump of the first aspect, and the rotary pump of the second aspect lacks the lubricant supply.
  • the FIGS. 1 to 7 show a rotary pump 1 of a motor vehicle.
  • the rotary pump 1 is electrically driven.
  • the rotary pump 1 is designed as an external gear pump. It is designed as a gear pump.
  • the rotary pump 1 is provided for lubrication and / or cooling of a transaxle of the motor vehicle. Additionally or alternatively, the rotary pump 1 may be provided for sucking a fluid from a fluid sump of the motor vehicle.
  • the motor vehicle is designed as an electric motor driven motor vehicle. It is designed as an electric vehicle.
  • the fluid delivered by the rotary pump 1 is formed as an oil.
  • FIG. 1 shows in two figures a view into the open rotary pump 1.
  • the rotary pump 1 has two intermeshing rotors 10, 11 and a housing 2.
  • the left picture of the FIG. 1 shows the opened rotary pump. 1 with the rotors 10, 11 arranged therein.
  • the right-hand illustration of FIG FIG. 1 shows the open rotary pump 1 without the rotors 10, 11, wherein the rotors 10, 11 are indicated.
  • An inner surface of an axial side wall of the rotary pump 1, for example a bottom or a lid, can be seen.
  • FIG. 2 shows the open rotary pump 1 in perspective partly in exploded view.
  • FIG. 3 an enlarged portion of the opened rotary pump 1 is shown.
  • the rotors 10, 11 are formed as externally toothed gears.
  • the rotors 10, 11 are each arranged on a rotor shaft or axis A0, A1.
  • the rotors 10, 11 are each arranged on the rotor shaft or axis A0, A1 rotationally and non-displaceably. They are each pressed onto the rotor shaft or axis A0, A1.
  • the rotor shafts or axles A0, A1 are rotatably supported in the housing 2 by bearings 50, 51.
  • the bearings 50, 51 are designed as shaft bearings. They are designed as plain bearings.
  • the rotor 11 is formed as a driven rotor 11 which drifts on the rotor 10.
  • the housing 2 forms a pump chamber 7 with an inner peripheral wall 70, 71.
  • the housing 2 has an inlet 4 in the pump chamber 7 and an outlet 3 from the pump chamber 7.
  • the inner peripheral wall 70, 71 together with the rotors 10, 11 a radial sealing gap which can be called a head game.
  • the radial sealing gap extends with respect to each rotor 10, 11 from the inlet 4 in the pump chamber 7 to the outlet 3 from the pump chamber 7.
  • the radial sealing gap may at least partially overlap the inlet 4 and / or the outlet 3. In the rotary pump 1 of the embodiment, the radial sealing gap overlaps the inlet 4 and the outlet 3, as can be seen in particular in the right figure.
  • the rotors 10, 11 form in the pump chamber 7 conveyor cells 8.
  • the conveyor cells 8 are limited by the bottom, the lid, the respective inner peripheral wall 70, 71 and the respective rotor 10, 11.
  • Inlet 4 and outlet 3 are defined according to the direction of rotation D of the rotary pump 1, which is shown in the right figure.
  • the rotary pump 1 may be a reversible rotary pump 1, in which the direction of rotation D can be changed, whereby the inlet 4 to the outlet from the pump chamber 7 and the outlet 3 to the inlet into the pump chamber 7 is.
  • the inlet 4 and the outlet 3 are separated from one another in the direction of rotation D by sealing webs 90, 91, so that the medium or fluid conveyed by the rotary pump 1 can not flow directly from the inlet 4 to the outlet 3.
  • the fluid is transported in the delivery cells 8 from the inlet 4 to the outlet 3.
  • a drive web 9 is formed, which also fluidly separates the inlet 4 from the outlet 3 and prevents Inlet 4 and outlet 3 are fluidically shorted.
  • lubricant feeds 60, 61 are formed in the sealing webs 90, 91, which supply the bearings 50, 51 with the fluid from the pump chamber 7.
  • the lubricant feeders 60, 61 are T-shaped.
  • the free end or foot of the lubricant supply 60, 61 opens into the respective bearing 50, 51, wherein the lubricant supply 60, 61 radially extends so far away from the bearing 50, 51, that at least the head of the lubricant supply 60, 61 in itself rotating rotor 10, 11 is overflowed by the conveyor cells 8.
  • the head of the lubricant supply 60, 61 connects two directly adjacent conveyor cells 8 with each other. In principle, it is conceivable that the lubricant supply 60, 61, in particular the head of the lubricant supply 60, 61, at least two non-adjacent conveyor cells 8 connects together.
  • the inner peripheral wall 70, 71 has in each case a peripheral region 70r i , 71r i , in which the radial sealing gap or the head clearance is smaller than in the remaining peripheral region of the inner circumferential wall 70, 71.
  • the peripheral regions 70r i , 71r i are in the inner circumferential wall 70, 71 formed where an imaginary radial extension of the lubricant feeders 60, 61 would hit the inner peripheral wall 70, 71.
  • an extension of the peripheral regions 70r i , 71r i is at least so great that the peripheral region 70r i , 71r i has at least one delivery cell 8 at its rotational direction D of the rotary pump 1 the furthest extent completely covered.
  • the circumferential regions 70r i , 71r i extend , with a corresponding rotor position, over two adjacent conveyor cells 8, as can be seen in the right-hand illustration. These two conveyor cells 8 are better sealed due to the smaller radial sealing gap compared to the upstream in the direction of rotation D upstream and downstream conveyor cells 8.
  • a maximum extent of the circumferential regions 70r i , 71r i is determined by the inlet 4 and the outlet 3, or the course of the inner peripheral wall 70, 71, with the premise that the lubricant supply 60, 61 is not directly connected to the inlet 4 and / or Outlet 3 is to be connected.
  • the inner peripheral wall 70, 71 in the peripheral regions 70r i , 71r i is part of a circle about the axis A0, A1 having a radius Ri smaller than a radius Ra in the peripheral region of the inner peripheral wall 70, 71 outside the peripheral regions 70r i , 71r i .
  • the radius Ri substantially corresponds to the radius of a circumferential circle U, which contacts all the radially outer ends of the conveying elements, in the illustrated embodiment, teeth of the rotor 10, 11.
  • the radial sealing gap in the peripheral regions 70r i , 71r i is smaller than the remaining sealing gap between the rotor 10, 11 and inner peripheral wall 70, 71, whereby the delivery cells 8 are better sealed in these peripheral regions 70r i , 71r i .
  • the fluid in the better sealed delivery cells 8 is under a higher pressure, which is advantageous in order to push the fluid into the bearing 50, 51.
  • the transitions in the sealing gap are not stepped in the exemplary embodiment, but the inner peripheral wall 70, 71 merges in a curve in the peripheral regions 70r i , 71r i .
  • FIG. 2 shows the left picture of the FIG. 1 in a partial exploded view. Both rotor shafts or axles A0, A1 are missing, the rotor 11 is taken out of the pump chamber 7, while the rotor 10 lies in the pump chamber 7. In the rotors 10, 11 facing axial inside of the housing 2, the inlet 4, the outlet 3 and the lubricant supply 60, 61 are introduced.
  • the lubricant feeds 60, 61 radially opposite the inner peripheral wall 70, 71 has a peripheral portion 70 r i , 71r i , which projects radially inwardly from the inner peripheral wall 70, 71.
  • the inner peripheral wall 70, 71 and the peripheral regions 70r i , 71r i extend over their entire axial length substantially perpendicular to the axial end face of the housing 2.
  • the FIG. 4 shows a rotary pump 1, which is connected to the rotary pump 1 of FIG. 1 is identical, except for the shape of the lubricant supply 60, 61, in the FIG. 4 is formed as a straight line.
  • the lubricant supply 60, 61 has a width which substantially corresponds to a tooth width of a rotor 10, 11.
  • the width of the lubricant supply 60, 61 may also be larger or smaller than the tooth width. With a width of the lubricant supply 60, 61, which is greater than the tooth width, the lubricant supply 60, 61 connects two directly adjacent conveyor cells 8 with each other.
  • FIG. 7 is a rotary pump 1 without the rotors 10, 11 shown.
  • the rotary pump 1 according to the FIGS. 1 to 6 has the rotary pump 1 according to the FIG. 7 a compound 12 which fluidly connects the bearings 50, 51 and the two lubricant supply lines 60, 61 via the web 9.
  • FIG. 8 a rotary pump 1 is shown which has no lubricant feeds.
  • the rotary pump 1 in the FIG. 8 is, apart from the lubricant feeds, identical to the rotary pump 1, which in the FIGS. 1 to 3 is shown.
  • the lubricant feeds In contrast to the rotary pump 1 according to the FIGS. 1 to 3 missing the rotary pump 1 according to the FIG. 8 the lubricant feeds.
  • Analogous to the rotary pump 1 of FIGS. 1 to 3 has the inner peripheral wall 70, 71 of the rotary pump 1 according to FIG. 8 each have a peripheral region 70r i , 71r i , in which the radial sealing gap or the head clearance is smaller than in the remaining peripheral region of the inner peripheral wall 70, 71.
  • the peripheral regions 70r i , 71r i seen in the direction of rotation D substantially centrally between the inlet 4 and the outlet 3 in the inner peripheral wall 70, 71 is formed.
  • an extension of the peripheral regions 70r i , 71r i is at least so great that the peripheral region 70r i , 71r i completely covers at least one conveyor cell 8 at its furthest extent in the direction of rotation D of the rotary pump 1.
  • the circumferential regions 70r i , 71r i extend, with a corresponding rotor position, over two adjacent conveying cells 8. These two conveying cells 8 are better sealed due to the smaller radial sealing gap in comparison to the upstream and downstream conveying cells 8 seen in the direction of rotation D.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP19166411.9A 2018-03-29 2019-03-29 Rotationspumpe Pending EP3546752A1 (de)

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DE102018107695.9A DE102018107695A1 (de) 2018-03-29 2018-03-29 Rotationspumpe

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US3904333A (en) * 1974-05-22 1975-09-09 Weatherhead Co Pressure balancing system for gear pumps or motors
US4927343A (en) * 1988-10-06 1990-05-22 Permco, Inc. Lubrication of gear pump trunnions
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DE102016107447A1 (de) * 2016-04-21 2017-11-09 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit Schmiernut im Dichtsteg

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US5641281A (en) * 1995-11-20 1997-06-24 Lci Corporation Lubricating means for a gear pump
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DE102005061667A1 (de) 2005-12-22 2007-07-05 Vmi-Az Extrusion Gmbh Planeten-Zahnradpumpe
EP1925823B1 (de) 2006-11-21 2016-08-17 Johann Sagawe Umlaufverdrängermaschine
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Publication number Priority date Publication date Assignee Title
CH361720A (de) * 1958-03-19 1962-04-30 Hans Dipl Ing Molly Hydraulische Maschine mit dem Kippen eines oder mehrerer Lagerkörper entgegenwirkender Radialkraft
DE1941641A1 (de) * 1969-08-16 1971-02-18 Zahnradfabrik Friedrichshafen Lagerschmierung einer Zahnradpumpe
US3904333A (en) * 1974-05-22 1975-09-09 Weatherhead Co Pressure balancing system for gear pumps or motors
US4927343A (en) * 1988-10-06 1990-05-22 Permco, Inc. Lubrication of gear pump trunnions
DE102007031909A1 (de) * 2007-07-09 2009-01-15 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Umlaufverdrängerpumpe mit Druckpulsation minderndem Auslass
DE102016107447A1 (de) * 2016-04-21 2017-11-09 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit Schmiernut im Dichtsteg

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US20190301455A1 (en) 2019-10-03
US11280336B2 (en) 2022-03-22
CN110318997A (zh) 2019-10-11
DE102018107695A1 (de) 2019-10-02
CN110318997B (zh) 2022-07-22

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