EP2921702A2 - Unité pompes-moteur - Google Patents

Unité pompes-moteur Download PDF

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Publication number
EP2921702A2
EP2921702A2 EP15158367.1A EP15158367A EP2921702A2 EP 2921702 A2 EP2921702 A2 EP 2921702A2 EP 15158367 A EP15158367 A EP 15158367A EP 2921702 A2 EP2921702 A2 EP 2921702A2
Authority
EP
European Patent Office
Prior art keywords
channel
leakage
rotor
shaft
motor
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
EP15158367.1A
Other languages
German (de)
English (en)
Other versions
EP2921702A3 (fr
EP2921702B1 (fr
Inventor
Reinhard Pippes
Dominik Ketterer
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.)
Eckerle Industrie Elektronik GmbH
Original Assignee
Eckerle Industrie Elektronik 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 Eckerle Industrie Elektronik GmbH filed Critical Eckerle Industrie Elektronik GmbH
Publication of EP2921702A2 publication Critical patent/EP2921702A2/fr
Publication of EP2921702A3 publication Critical patent/EP2921702A3/fr
Application granted granted Critical
Publication of EP2921702B1 publication Critical patent/EP2921702B1/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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/008—Enclosed motor pump units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/04—Draining
    • 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
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible 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
    • F04C15/0007—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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0046—Internal leakage control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0096—Heating; Cooling
    • 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
    • F04C2/10—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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • 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
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

Definitions

  • the invention relates to a motor-pump unit comprising an internal gear machine for reversing operation and an electric motor which is coupled via a shaft with the internal gear machine.
  • a motor-pump unit can be used for example to control a highly dynamic hydraulic axis.
  • motor-pump units In such motor-pump units, it depends on a high dynamics, low noise and Pulsationsarmut, Rekupierkle, long life, freedom from leaks, long life and insensitivity to shock, dirt, water, especially salt water and temperature, especially cold on.
  • motor-pump units In the hitherto known motor-pump units, it may be due to design over the operating time or in operation to faults or even premature failure total. In addition, these motor-pump units are relatively expensive and expensive to manufacture.
  • the rotor or shaft bearing associated with the electric motor are present.
  • the invention relates to a motor-pump unit with a multi-part housing, which comprises an internal gear machine for reversing operation and an electric motor with a rotor and a stator, which is coupled via at least one shaft rotatably mounted in the housing about a shaft rotation shaft with the internal gear machine, wherein the electric motor comprises a rotor arranged in a housing part of the housing, rotatable about a rotor axis of rotation, and a stator, and wherein the internal gear machine comprises a working chamber which is delimited by at least two housing parts of the housing and in which two toothed wheels are arranged which are a pinion gear having externally toothed pinion and a ring gear teeth having internally toothed ring gear, which is eccentrically mounted with respect to the pinion, said ring gear teeth of the ring gear teeth of the ring gear meshing with pinion teeth of the pinion teeth of the pinion in a meshing region, u nd where
  • the shaft extends with a shaft end away from the pinion in the axial direction by the rotor carried by the shaft.
  • the first connection channel and the second connection channel are connected via check valves arranged in the housing or in a housing part of the housing bounding the working chamber to a leakage channel loop fluidly connected to the at least one leakage channel, extending at least into a region of a rotor end extending away from the pinion of the rotor and extending in the axial direction in the shaft or by the shaft extending leakage shaft channel and at least one fluidly connected to the leakage shaft channel, preferably in a radial distance to the leakage shaft channel, in the axial direction in the Rotor or by the rotor extending leakage rotor channel and / or having a fluid-connected to the leakage shaft channel, viewed in the radial direction between the rotor and the stator formed, extending in the axial direction leakage gap channel.
  • the check valves block in a fluid flow direction of the leakage channel loop, preferably the respective active low pressure region, open the working chamber and in an opposite direction or opposite fluid flow direction, preferably from the respective active high pressure region of the working chamber to the leakage channel loop lock, so that during operation of the internal gear machine the leakage fluid from the at least one leakage channel through the leakage channel loop into the working chamber, preferably and from there substantially, that is, except for a leakage component, in which the respectively active low-pressure region associated connection channel flows.
  • a sickle-shaped clearance is formed between the pinion and the ring gear.
  • a one-piece or multi-part filler can be arranged in the crescent-shaped space.
  • a crescent-shaped space is formed, in which a multipart filler is arranged, the more in the radial Direction relative to each other movable radial sealing segments for radially sealing a high-pressure region of the working chamber comprises, of which a first Radialdichtsegment forms a pinion on the pinion teeth of the pinion teeth of the pinion or adjacent pinion segment and of which a second Radialdichtsegment forms a ring gear teeth of the ring gear teeth of the ring gear can be applied or applied ring gear segment.
  • At least one axially movable axial sealing plate for axially sealing the high-pressure region of the working chamber is arranged between axial end surfaces of the gears and at least one housing part of the housing.
  • a radial gap is formed between an inner surface of the pinion segment pointing radially outwards relative to the ring gear segment and a radially opposite inner surface of the ring gear segment, facing radially inwardly toward the pinion segment.
  • the at least one leakage channel is fluidly connected directly to the leakage wave channel of the leakage channel loop and that the at least one leakage rotor channel of the leakage channel loop directly with a housing part of the housing or in the at least one leakage channel containing Housing part of the housing arranged connecting channel or connection space is fluidly connected, so that during operation of the internal gear machine, the leakage fluid flows either from the at least one leakage channel through the leakage wave channel and into and through the at least one leakage rotor channel of the leakage channel loop and from there into the connection channel or into the connection space, or vice versa, or that the at least one leakage channel is fluidly connected directly to the at least one leakage rotor channel of the leakage channel loop and that the at least one leakage wave channel of the leakage channel loop directly with a housing part contained in a housing part of the housing or in the at least one leakage channel of the housing arranged connecting channel or connecting space is fluidly connected, so that during operation of the internal gear machine, the leakage fluid flows either from the at least one
  • a first return flow channel and a second return flow channel are arranged, which in each case one end in the connecting channel or connecting space and the other end, preferably in a respective one Mouth of the respective connection channel in the working chamber opposite the mouth region, open into the working chamber, wherein the first return flow contains a first check valve of the check valves and wherein the second return flow a second check valve of the check valves such that, during operation of the internal gear machine, the leakage fluid passes through the leakage channel loop, preferably from the leakage channel through the leakage wave channel into and through the at least one leakage rotor channel of the leakage channel loop, or vice versa, into and through the connection channel or connection space and therefrom flows into and through the first return flow passage via the first check valve into the working chamber or into and through the second return flow passage via the second check valve into the working chamber.
  • an opening into the working chamber first channel part of the first return flow and the first connection channel in the axial direction preferably coaxially extend, and that a opening into the working chamber second channel portion of the second return flow channel and the second connection channel in the axial direction , preferably coaxial with each other, extend.
  • the leakage shaft channel is an axial bore whose bore longitudinal axis is arranged coaxially with the rotor rotational axis and / or coaxially with the shaft rotational axis.
  • the at least one leakage rotor channel is an axial recess whose recess longitudinal axis is arranged parallel to the pinion rotation axis and / or parallel to the shaft rotation axis.
  • the rotor contains a plurality of leakage rotor channels extending through the latter in the axial direction, which each have one end with the leakage wave channel are fluid-connected and the other end fluidly connected to the working chamber and / or with the connecting channel or with the connecting space.
  • the at least one leakage rotor channel extends through the rotor and is open toward rotor ends of the rotor pointing away from one another in the axial direction or that the leakage rotor channels extend through the rotor and into the axial direction facing away from each other rotor ends of the rotor are open.
  • the shaft has at least one radial recess which opens into the leakage shaft channel at one end and the other end is open radially outward and at least one in the region of the open to the shaft, preferably designed as an annular space Leakage channel is arranged for receiving the leakage fluid, so that during operation of the internal gear machine, the leakage fluid from the at least one leakage channel, preferably immediately, flows into the leakage wave channel.
  • the shaft in the region of its shaft end assigned to the rotor or at its shaft end assigned to the rotor via a rotor bearing of the rotor on a housing part of the housing assigned to the electric motor about its rotor axis of rotation and / or about its shaft axis.
  • Rotary axis is rotatably mounted, and that the leakage shaft channel of the shaft and the at least one leakage rotor channel of the rotor are fluidly connected to a bearing gap of the rotor bearing, so that during operation of the internal gear machine the leakage fluid flows to the bearing gap of the rotor bearing or through the bearing gap of the rotor bearing.
  • the rotor bearing may preferably be a roller bearing or a ball bearing.
  • the shaft has at least one radial recess, which is arranged in the region of the rotor bearing and which opens at one end into the leakage shaft channel and the other ends fluidly fluidly connected to one with the bearing gap of the rotor bearing first connection channel or, preferably designed as an annular space, connecting space is open, which is fluidly connected to the at least one leakage rotor channel or into which the at least one leakage rotor channel, so that during operation of the internal gear machine, the leakage fluid from the leakage wave channel in the the connecting gap of the rotor bearing fluid-connected connecting channel or in the, preferably designed as an annular space, connecting space and from there into the at least one leakage rotor channel, or vice versa.
  • a Lagerbefest Trents- and / or sensor body is attached to the shaft in the region of its shaft associated with the rotor, by means of which the rotor bearing is attached to the shaft and / or a sensor, preferably a speed sensor contains ,
  • the leakage shaft channel is releasably closed in the region of the shaft end of the shaft associated with the rotor by means of the bearing fastening and / or sensor body.
  • the bearing fastening and / or sensor body is a bearing fastening and / or sensor screw which is screwed to the shaft.
  • the Lagerbefestists- and / or sensor body made of a non-magnetic material and the sensor can generate magnetic signals or generates magnetic signals.
  • the Lagerbefestists- and / or sensor body fluidly connected to the leakage shaft channel AxialausNOung is arranged, which opens into a radial recess of the Lagerbefest todays- and / or sensor body, the radially outwardly to one or the connecting with the bearing gap of the rotor bearing fluid-connected connection channel or, preferably designed as an annular space, connecting space is open, which is disposed on a side facing away from the pinion side of the rotor bearing, so that during operation of the internal gear machine, the leakage fluid from the leakage wave channel flows through the axial recess and the radial recess of Lagerbefest Trents- and / or sensor body and the connecting channel or connecting space through the bearing gap of the rotor bearing into the at least one leakage rotor channel, or vice versa.
  • a sealing tube which extends in the axial direction over substantially the entire length of the stator, is arranged between the rotor and the stator, which has a length in the axial direction, made of a non-magnetic material the stator is fixed and which is sealed to the stator against ingress of the fluid pressure medium or leakage fluid.
  • the leakage gap channel is formed in the radial direction between the sealing tube and the rotor.
  • the leakage gap channel is a leakage annular gap channel.
  • the shaft is a one-piece and / or one-piece motor pump shaft, to which the rotor is secured against rotation, preferably non-positively, in particular by pressing or shrinking, and on which the pinion rotatably, preferably form-fitting, in particular releasably secured.
  • the electric motor is a brushless DC motor (EC motor).
  • the motor-pump unit 20 comprises an internal gear machine 21 for reversing operation, an electric motor 22 and an integrated electronics 74, in particular for speed control.
  • the electric motor 22 comprises a rotor 22.1 and a stator 22.2.
  • the relative to the stator 22.2 about a rotor axis 34.1 rotatable rotor 22.1 is rotatably connected to a rotatable about a shaft axis 35 shaft 23.
  • the rotor 22. 1 is coupled via the shaft 23 to the gear of the internal gear machine 21.
  • the shaft 23 is a common one-piece motor pump shaft.
  • the motor pump shaft 23 is rotatably mounted in the housing 25 about a shaft rotation axis 35.
  • the motor-pump unit 20 can preferably be used for the control of a highly dynamic hydraulic axis, which are not shown in the figures.
  • the motor-pump unit 20 includes a multi-part housing 25 containing both the electric motor 22 and the internal gear machine 10.
  • both the rotor 22.1 and the stator 22.2 are arranged in a tubular housing part 25.3 of the housing 25 assigned to the motor 22.
  • the stator could also form part of a housing part of the housing of the motor-pump unit or as a Housing part of the housing of the motor-pump unit could be formed.
  • the internal gear machine 21 is a hydraulic machine in the form of a compensated four-quadrant internal gear machine 21.
  • the motor-pump unit 20 is used in a closed hydraulic system.
  • the motor-pump unit 20 is characterized by high dynamics, low noise and Pulsationsarmut, Rekupierkle, long life, absolute freedom from leaks, lifetime filling of the system, shock resistance and insensitivity to dirt, water, especially salt water, and temperature, especially cold from ,
  • the motor-pump unit 20 in particular has the following design features: Internal gear machine:
  • the internal gear machine 21 is a hydraulic pump in the form of an internal gear pump with axial and radial sealing gap compensation is used.
  • the internal gear machine 21 comprises a working chamber 24, which is bounded by preferably two housing parts 25.1 and 25.2 of the housing 25 of the motor-pump unit 20.
  • two gears 26, 30 are arranged in the housing 25 and in the working chamber 24, two gears 26, 30 are arranged.
  • This is a pinion gear 26 having external gear 26 and a ring gear 31 exhibiting internally toothed ring gear 30.
  • the ring gear 30 is eccentrically mounted with respect to the pinion 26 in a bearing ring 27.
  • the bearing ring 27 is rotatably connected to the housing part 25.2 of the housing 25, preferably pressed.
  • the ring gear 30 is arranged such that ring gear teeth of the ring gear teeth 31 of the ring gear 30 mesh with pinion teeth of the pinion teeth 28 of the pinion 26 in a meshing engagement portion 33.
  • the pinion 26 is about a pinion axis of rotation 34.2 rotatably mounted.
  • the pinion rotation axis 34. 2 is arranged coaxially with the shaft rotation axis 35 of the shaft 23.
  • the ring gear 30 is rotatably mounted about a Hohlradfilachse 36.
  • the directions of rotation of pinion 26 and ring gear 30 are rectified. This means that if, for example, the pinion 26 rotates clockwise, then forcibly also the ring gear 30 rotates clockwise.
  • the pinion 26 is releasably connected to the shaft 23, for example via a feather key 37, which engages in a form-fitting manner in matching grooves 38.1, 38.2 of both the shaft 23 and the pinion 26 (see FIG. 3 ). Consequently, the pinion 26 and the shaft 23 are positively connected rotationally fixed to each other.
  • the Hohlradcardachse 36 and the pinion rotation axis 34.2 extend in an axial direction 39 parallel to each other.
  • a sickle-shaped clearance 40 of the working chamber 24 is formed between the pinion 26 and the ring gear 30, a sickle-shaped clearance 40 of the working chamber 24 is formed.
  • a multi-part crescent-shaped filler 41 is arranged in the free space 40.
  • the filling piece 41 comprises a plurality of radial sealing segments 42 which are movable relative to each other in the radial direction; 43.1, 43.2 for the radial sealing of the respectively dependent on the direction of rotation 104.1, 104.2 "active" high pressure area 44.1, 44.2 of the working chamber 24.
  • the high pressure area 44.1, 44.2 is associated with that area of the working chamber 24, starting from a pressure build-up area of the working chamber 24, the in operation of the internal gear machine 21 corresponds approximately to that area in which the teeth 28, 31 of the gears 26, 30 reach the filling piece 41 or the region of the filling piece 41, in which at least one, preferably two, retaining pin / retaining pin 45.1, 45.2 for the filling piece 41 or for the radial sealing segments 42; 43.1, 43.2 is arranged in the Viewed respective direction of rotation 104.1, 104.2 of pinion 26 and ring gear 30, to the tooth engagement portion 33 extends, in which the teeth 28, 31 of the gears 26, 30 mesh with each other.
  • the respective active high-pressure area 44.1, 44.2 is formed semi-sickle-shaped or kidney-shaped.
  • a first connection channel 105.1 opens into said first region 44.1 of the working chamber 24, and a second connection channel 105.2 opens into said second region 44.2 of the working chamber. (please refer FIG. 12 ).
  • the internal gear pump 21 rotates in its first operating direction 104.1, or is the first working channel 105.1 pressurized with fluid high pressure and when the internal gear pump 21 rotates in its second operating direction 104.2, or is the second working channel 105.2 with high fluid pressure of the fluid pressure medium applied.
  • the first connection channel extend 105.2 and the second connection channel 105. In the axial direction 39 parallel to each other
  • Radial sealing segments 42; 43.1, 43.2 comprise a first radial sealing segment which forms a pinion segment 42 which can also be designated as a segment carrier and which can be applied to pinion teeth of the pinion teeth 28 of the pinion 26.
  • the pinion segment 42 is integrally formed and made of one part, for example by milling.
  • Radial sealing segments 42; 43.1, 43.2 also comprise at least a second Radialdichtsegement, which forms a ring gear segment 43.1, 43.2 and which can be applied to ring gear teeth of the ring gear teeth 31 of the ring gear 30 and rests.
  • a second Radialdichtsegement which forms a ring gear segment 43.1, 43.2 and which can be applied to ring gear teeth of the ring gear teeth 31 of the ring gear 30 and rests.
  • two separate ring gear segments 43.1, 43.2 are provided, of which each ring gear segment 43.1, 43.2 can be applied or abut against ring gear teeth of the ring gear teeth 31 of the ring gear 30.
  • the pinion segment 42 has, in the region of each ring gear segment 43.1, 43.2, an inner surface 72 pointing radially outward to the respective ring gear segment 43.1, 43.2.
  • Each ring gear segment 43.1, 43.2 has an inner surface 73.1, 73.2 pointing radially inward toward the pinion segment 42, which lies opposite the associated inner surface 72 of the pinion segment 42. Between the inner surface 72 of the pinion segment 42 and the inner surface 73.1, 73.2 of the respective ring gear segment 43.1, 43.2, a radial gap 75.1, 75.2 is formed in each case.
  • pressure medium preferably pressurized oil, passes from the active high-pressure region 44.1, 44.2, which is assigned to the current direction of rotation of the pinion 26 and the ring gear 30, into the radial gap 75.1, 75.2 or into the corresponding gap space, which also is designated compensation space.
  • the pinion segment 43.1, 43.2 has two sealing roller grooves 48.1, 48.2 extending in the axial direction 39.
  • Each sealing roller groove 48.1, 48.2 is open to their axial ends facing away from each other.
  • movable sealing roller 49.1, 49.2 for sealing the radial gap 75.1, 75.2 between the Ritzelsgement 42 and the respective ring gear 43.1, 43.2 arranged.
  • each sealing roller groove 48.1, 48.2 is also a prestressed sealing roller spring 50.1, 50.2, preferably a leaf spring arranged.
  • Each sealing roller spring 50.1, 50.2 is supported on the one hand on a groove bottom of the associated sealing roller groove 48.1, 48.2 and on the other hand is supported on the associated sealing roller 49.1, 49.2. This will make every sealing roll 49.1, 49.2 pressed against a sealing surface of the sealing roller groove 48.1, 48.2 of the pinion segment 42 and also against a sealing surface of the respective associated ring gear segment 43.1, 43.2 even in the pressure-released state or in non-operation of the internal gear machine 21.
  • the pinion segment 42 has two segment spring grooves 51.1, 51.2 extending in the axial direction 39.
  • Each segment spring groove 51.1, 51.2 is open to their axial ends facing away from each other.
  • a prestressed spring 52.2, 52.2 preferably a leaf spring, is accommodated in each segment spring groove 51.1, 51.2.
  • Each segment spring groove 51.1, 51.2 is offset in the circumferential direction at a circumferential distance or circumferential angle relative to the respectively assigned sealing roller groove 48.1, 48.2, in the direction of the pinion segment end 53.1, 53.2 of the pinion segment 42, which is dependent on the direction of rotation, high-pressure region 44.1, 442 added.
  • the pinion segment 42 is formed as a segment carrier for the respective ring gear segment 43.1, 43.2 and has for each ring gear segment 43.1, 43.2 a markable as a stop bag stop 54.1, 54.2. Every 54.1, 54.2 abutment has an abutment surface 55.1, 55.2 extending in the axial direction 39 and radially outward toward the ring gear 30 for supporting the respective ring gear segment 43.1, 43.2 against retraction of the respective ring gear segment 43.1, 43.2 during operation of the internal gear machine 21 in the tooth engagement region 33 , Each stop 54.1, 54.2 is with its stop surface 55.1, 55.2 at a circumferential distance or in a circumferential angle to the respective segment spring groove 51.1, 51.2 in the circumferential direction in the direction of the dependent on the direction of rotation active high-pressure region 44.1, 44.2 associated pinion segment end 53.1, 53.2 of the pinion 42nd staggered.
  • the or each Axialdichtis 58.1, 58.2 is in operation of the internal gear machine 21 by means of pressure medium under high pressure with their respective inner surface 59.1, 60.1 against the respectively associated end faces 56.1, 56.2; 57.1, 57.2 of pinion 26 and ring gear 30 pressed.
  • so-called pressure fields 61.1, 61.2 are provided, which can also be marked with axial fields (see FIG. 7 ).
  • the print fields 61.1, 61.2 form control fields.
  • the pressure fields 61.1, 61.2 are provided in the form of recesses in the respective associated housing part 25.1, 25.2 of the housing 25 in this embodiment.
  • the pressure fields or a pressure field associated with an axial sealing plate can also be provided in the form of a recess in the axial sealing plate or in the respective axial sealing plate.
  • the or each pressure field 61.1, 61.2 is designed kidney-shaped.
  • the axial discs 58.1, 58.2 have on their inner sides 59.1, 60.1, ie those sides which face the pinion 26 and the ring gear 30, kidney-shaped control fields 62.1, 62.2, which are also referred to as sealing plate recesses or pressure kidneys (see FIGS. 4 and 5 ). These are recesses or depressions in the respective axial disk 58.1, 58.2.
  • These control fields 62.1, 62.2 are, as well as the pressure fields 61.1, 61.2, acted upon by pressure medium under high pressure or are acted upon during operation of the internal gear 21 with pressure medium of the respective high-pressure area 44.1, 44.2. As a result, a counter force is generated which counteracts the force of the pressure fields 61.1, 61.2.
  • Each printing kidney 62.1, 62.2 are at least two cam grooves 63.1.1, 63.1.2; 63.2.1, 63.2.2 assigned to each of the associated end faces 56.1, 56.2; 57.1, 57.2 of the gears 26, 30 are open, of which a first control groove 63.1.1, 63.1.2 in the range of formed between the pinion teeth 28 of the pinion 26 pinion tooth gaps 29 this immediately is arranged opposite one another and of which a second control groove 63.2.1, 63.2.2 in the region of between the ring gear teeth 31 of the ring gear 30 formed ring gear tooth spaces 32 is arranged directly opposite this (see FIG. 5 ).
  • Both the first control groove 63.1.1, 63.1.2 and the second control groove 63.2.1, 63.2.2 each open with a first end into the associated pressure kidney 62.1, 62.2.
  • a control slot 64.1.1, 64.1.2; 62.2.1, 64.2.2 provided in the form of a recess or depression of the respective thrust washer 58.1, 58.2.
  • Each control slot 64.1.1, 64.1.2; 62.2.1, 64.2.2 opens into the respectively assigned first and second control groove 63.1.1, 63.1.2; 63.2.1, 63.2.2.
  • Each control slot 64.1.1, 64.1.2; 62.2.1, 64.2.2 extends approximately or substantially in the circumferential direction.
  • the pinion segment 42 and / or the ring gear segment 43.1, 43.2 has at least one radial-sealing-segment depression in the form of a circumferential direction about the pinion rotation axis 34.2 or the ring gear rotation axis 36 extending, pressurizable with the pressure medium Radialdichtsegment control channel 65; 65.1, 65.2, 65.3, 65.4, 65.5, 65.6 which is open towards the associated radial gap 75.1, 75.2 and which opens directly into the associated radial gap 75.1, 75.2.
  • the Radialdichtsegment control channel 65 extends in a direction or in the direction of rotation in which the pinion 26 is about its pinion axis 34.2 or in which the ring gear 30 is rotatable about its Hohlradcardachse (36) and / or extends Radial sealing segment control channel 65 in a plane perpendicular to the axial direction 39 imaginary plane direction.
  • pressure medium which builds up in the active pressure chamber 44.1, 44.2 preferably pressurized oil, can reach the gap space of the active radial gap 75.1, 75.2 more quickly.
  • the necessary radial compensation pressure in the active radial gap 75.1, 75.2 between the pinion segment 42 and the respective active ring gear segment 43.1, 43.2 is achieved in an even shorter time at the respective direction of rotation reversal and thus in each case an even better or optimal seal.
  • Both the externally toothed pinion 26 and the internally toothed ring gear 30 are profile-shifted.
  • the pressure angle is 25 °.
  • the tooth crown height factor of the pinion teeth is 1.25 and the tooth crown height factor of the ring gear teeth is 1.24. This combination has proven to be extremely quiet.
  • the tooth tip edges are specially shaped.
  • the radial compensation is by three, also referred to as radial sealing segments, segment parts 42; 43.1, 43.2 symmetrical shown.
  • the one-piece pinion segment 42 is actively sealing both directions of rotation in both pump and motor operation.
  • the two Hohlradsegmente 43.1, 43.2 are actively sealing only in the corresponding direction of rotation.
  • the non-active sealing segment 43.1, 43.2 is held in position by a spring element 52.1, 52.2.
  • the seal between the radial sealing segments 42; 43.1, 43.2, ie between the pinion segment 42 and the respective ring gear segment 43.1, 43.2, is ensured by sealing rollers 49.1, 49.2 arranged on both sides.
  • the sealing rollers 49.1, 49.2 are made of a high-strength temperature-resistant plastic.
  • the sealing rollers 49.1, 49.2 are received in suitable recesses 48.1, 48.2 of the pinion segment 42.
  • the sealing rollers 49.1, 49.2 are pressed during operation of the internal gear machine 21 under pressure medium pressure against a sealing surface of the pinion segment 42 and against a sealing surface of the respective active ring gear segment 43.1, 43.2. In the pressureless state, the sealing rollers 49.1, 49.2 are pressed by the respective sealing roller spring 50.1, 50.2 against the sealing surfaces.
  • the sealing surfaces are arranged in a special angle 66 which is smaller than 110 °.
  • the hydraulic actuation takes place via the radial gap 75.1, 75.2 between the outer peripheral surface 43 of the pinion segment 42, also referred to as inner surface, and the respective inner peripheral surface 44.1, 44.2 of the respective ring gear segment 43.1, 43.2, also referred to as the inner surface.
  • at least one axial sealing plate preferably in the Axialdichtplatten 58.1, 58.2, at least one additional control groove 63.3.1, 63.3.2 attached.
  • the pressure medium or control oil can not only flow via the radial gap 75.1, 75.2 between the radial sealing segments 42; Enter 43.1, 43.2 in the associated gap space, but also on the end faces or end face side in the gaps between the segments 42; 43.1, 43.2.
  • This "double" control has been shown to be extremely effective in order to get a slump in the promotion, especially in the dynamic requirements in reversing the internal gear machine 21. In other words, this results in the necessary radial compensation pressure in the gap 75.1, 75.2 between the segments 42; 43.1, 43.2 reached almost "at the same time” with the direction of rotation reversal and thus an optimal radial seal.
  • the chamfers 65.1, 65.2, 65.5, 65.6 can advantageously on both sides, but also on one side of the segments 42; 43.1, 43.2 are attached.
  • the pressure medium or pressure oil which builds up in the pressure chamber can flow more rapidly into the gap space, ie into the gap or compensation space formed between the radial gap 75.1, 75.2 between the pinion 26 and the active ring gear segment 43.1, 43.2 to get to the respective sealing roller 49.1, 49.2.
  • chamfers 65.1, 65.2 can, as shown, between the segment spring groove 51.1 and the sealing roller groove 48.1 and / or from the segmented spring groove 51.1 to the stop pocket or until the stop 54.1 on the segment carrier 42 and / or over the entire stop surface 55.1 out to the free surface 67.1 be arranged.
  • pressure medium or pressure oil can flow directly or directly into the gap or compensation space 75.1, 75.2.
  • these bevels 65.5, 65.6 can be attached to the ring gear segments 43.1, 43.2.
  • the same tasks can also take control grooves 65.3, 65.4 on the outer circumference of the pinion segment 42 and / or on the inner circumference of the Hohlradsegmente.
  • the filling piece 41 is supported via two retaining pins or bolts 45.1, 45.2, which are rotatably mounted in the housing parts 25.1, 25.2 via corresponding bores 68.1, 68.2.
  • the retaining pins or bolts 45.1, 45.2 have a guide roller on a circular cylindrical guide portion 69.1, 69.2, which spans an outer diameter.
  • the guide length is 1.5 x outer diameter of the guide portion 69.1, 69.2.
  • the retaining pins or bolts 45.1, 45.2 made of sintered material, preferably made of sintered iron, can be produced with appropriate strength.
  • the inner diameter of the holes 68.1, 68.2 of the housing parts 25.1, 25.2 is larger by a few micrometers than the outer diameter of the guide portion 69.1, 69.2 of the retaining pins or bolts 45.1, 45.2. This results in a clearance fit.
  • the holding pins or bolts 45.1, 45.2 can rotate during operation of the internal gear 21 and the, preferably an angle 70 of 24 ° enclosing, contact surfaces 71.1, 71.2, can in one for the sealing function of the segments 42; 43.1, 43.2 turn the optimal position.
  • a wear protection layer on the outer diameter of the respective retaining pin or bolt 45.1, 45.2 increases the service life of the gear machine 21, in particular in the case of highly dynamic load and change of direction of rotation as well as dynamic switching between engine and pump operation. For cost reasons, this wear protection is achieved by a surface hardening, such as nitriding or carbonitriding with appropriate choice of material.
  • the respective retaining pin or bolts 45.1, 45.2 has on its side facing away from the V-shaped contact surfaces 71.1, 71.2 side facing a circular cylindrical shoulder 76.1, 76.2.
  • the paragraph 76.1, 76.2 has compared to the guide portion 69.1, 69.2 a much smaller outer diameter.
  • the end face 77.1, 77.2 of paragraph 76.1, 76.2 is at the bottom of the hole bore in the housing part 25.1, 25.2 and thereby forms an axial stop of the retaining pins or bolts 45.1, 45.2 in the direction of the affected housing part 25.1, 25.2.
  • the axial displaceability of the retaining pin or bolt 45.1, 45.2 is limited by an end face 78.1, 78.2 between the contact surfaces 71.1, 71.2 and the groove bottom 79.1, 79.1 of the segment grooves 80.1, 80.2 of the pinion segment 42.
  • the retaining pin or bolt 45.1, 45.2 must basically have an axial play, but may not or nevertheless not collide with the teeth 28, 31 of the pinion 26 or the ring gear 30. For this purpose, open spaces are appropriate.
  • Chamfers 82 on the segment-side end face 77.1, 77.2 of the respective retaining pin or bolt 45.1, 45.2 also allow grooves 79, 79.2 of the groove pins 80.1, 45.2 of the pinion segment 42 to be supported on the retaining pin or bolts 45.1, 45.2
  • These radii 81, 83 reduce at the, preferably made of special brass or sintered material, segments 42; 43.1, 43.2 the notch stress, without the mobility of the segments 42; 43.1, 43.2 is restricted by terminals.
  • the pressure build-up in the tooth gaps 29, 32 of pinion 26 and ring gear 30 is formed by in the respective thrust washer 58.1, 58.2 control grooves 63.1.1, 63.1.2; 63.2.1, 62.2.2 and control slots 64.1.1, 64.1.2; 64.2.1, 64.2.2 controlled.
  • control slots 64.1.1, 64.1.2; 64.2.1, 64.2.2 having a triangular V-shaped cross-section, preferably with a V-angle of 60 °, and an inclination angle, preferably in the range of 4 °, optimized so that in conjunction with the position and position of the segments 42; 43.1, 43.2, in particular the sealing roller position and the angle 70 of the contact or support surfaces 71.1, 71.2; 73.1, 73.2 of the retaining bolts 45.1, 45.2 or the Ritzelsegmentnuten 80.1, 80.2 and the position and position, in particular the two side surfaces 84.1, 84.2 of the V-shaped free surface 85 in the axial pulleys 58.1, 58.2, an optimal in almost all operating points radial compensation effect of Pinion segment 42 and the respective active ring gear segment 43.1, 43.2 results.
  • control grooves 63.1.1, 63.1.2; 63.2.1, 62.2.2 have a direct connection to the respective pressure kidney 62.1, 62.2 of the respective Axialdichtin 58.1, 58.2 and are thus applied during operation of the internal gear 21 directly with pressure medium or with pressure oil.
  • the retention of the segments 42; 43.1, 43.2 is achieved by the engagement of the respective retaining pin 45.1, 45.2 in the corresponding grooves 80.1, 80.2 in the pinion segment 42 and by a radial projection of the retaining pin 45.1, 45.2 beyond the pinion segment 42 also radially outward.
  • the position of the segments 42; 43.1, 43.2 given a positive fit.
  • the grooves 80.1, 80.2 of the pinion segment 42 must be slightly larger or wider than that in the grooves 80.1 , 80.2 projecting, also referred to as a holding body part 86.1, 86.2 of the respective retaining pin 45.1, 45.2.
  • the game must be in accordance with the gearbox tolerances of the housing parts 25.1, 25.2, segments 42; 43.1, 43.2, bearing bushes and the deformation under load and taking into account the thermal expansion of the components in the temperature range of the application to be selected: It has proven advantageous to play between 0.05 to 0.1 x module of the Verdrängervertechnikung. This will jamming the gearing by the wedge-shaped segments 42; 43.1, 43.2 prevented even in depressurized operation.
  • the preferably double-sided axial compensation is also built up by autogenous pressure.
  • the axial compensation is based on Axialdruckfelder 61.1, 61.2 controlled axial plates 58.1, 58.2 symmetrical to a rotational axes of pinion 26 and ring gear 30 containing symmetry plane 87 constructed.
  • This plane of symmetry 87 extends, viewed in a perpendicular to the axial direction 39 or perpendicular to the axes of rotation 34.2, 36 of pinion 26 and ring 30 extending cross section, through the center 88 of the axis of rotation 34.2 of the pinion 26 and through the center 89 of the axis of rotation 36 of the Hohlrads 30.
  • This symmetry applies both to the respective thrust washer 58.1, 58.2 as well as for in the preferably cup-shaped housing part 25.2 and / or in the preferably designed as a cover housing part 25.1 Axialdruckfelder 61.1, 61.2.
  • the sealing of the Axialdruckfelder 61.1, 61.2 is preferably carried out by axial seals 90 with support rings 91 (see FIGS. 8 to 10 ).
  • the axial seal would have to be completely or partially “chambered” in this highly dynamic, reversibly used hydraulic machine. This means that the groove for receiving the seal would also have to have an "edge” to the pressure field "inside”. This necessary "edge” would complicate the production of the housing or lid parts.
  • the pressure field 61.1, 61.2 can be made completely kidney-shaped. The bottom of the pressure fields 61.1, 61.2 does not have to be processed completely mechanically, but can be made for example in die castings or other castings by the casting process.
  • the support ring 91 also has the advantage that it prevents a gap extrusion of the axial seal 90 in the gap between the axial plate 58.1, 58.2 and housing or cover wall.
  • the hydraulic machine 21 can also be used for higher pressures.
  • a gap extrusion of the axial seal occurring without a support ring would also cause a slight increase in the active axial pressure field and thereby increase the compensation force. This in turn would lead to a reduction of the hydraulic-mechanical efficiency and would thus deteriorate the energy efficiency of the motor-pump unit. In the worst case, it could lead to failure of the hydraulic machine by seal failure or by increased wear of the running surfaces of the thrust washer to the transmission side.
  • the supporting action of the support rings 91 "inward" is substantially improved by one or more webs 92.
  • the arrangement of these webs 92 must be selected so that the flow of oil, in particular to the axial pressure output or the flow of oil from the inlet is not affected.
  • the web 92 is located exactly at the same position as a web 93.1, 93.2, which is arranged in the pressure kidney 62.1, 62.2 of the respective thrust washer 58.1, 58.2.
  • the axial compensation is optimally matched in the example carried out by the measures described below.
  • the or each thrust washer 58.1, 58.2 preferably has two apertures 94.1, 95.1; 94.2, 95.2. Through these breakthroughs 94.1, 95.1; 94.2, 95.2, the pressure medium flows from the input side to the print kidney 62.1, 62.2 and vice versa from the print kidney 62.1, 62.2 via the pressure fields 61.1, 61.2 to the pressure outlet.
  • the respective web 93.1, 93.2 is approximately at the level of the center of the pinion and has a cross section which is dimensioned such that approximately 50% of the hydraulic force, caused by the operating pressure in the pressure kidney 62.1, 62.2 and the openings 94.1, 95.1; 94.2, 95.2.
  • the or each thrust washer 58.1, 58.2 is usually made of brass or aluminum, but can also by a sintering process or by metal powder injection molding (MIM technique ). To reduce the friction, a corresponding friction-minimized coating is advantageously applied.
  • the radial extent of the pressures is, as already described, by the control grooves 63.1.1, 63.1.2; 63.2.1, 63.2.2; 63.3.1, 63.3.2 and control slots 64.1.1, 64.1.2; 64.2,1, 64.2.2 and by the V-shaped free surface 85 and the tooth engagement 33 by the seal along the engagement line reached.
  • the respective axial plate 58.1, 58.2 freely movable within the axial play provided.
  • the relief bore 102 is closed in the region of the arranged in the motor flange 25.4 radial ball bearing 111 by a non-magnetic material, also referred to as closure means Lagerbefest Trents- or sensor screw 112 and opens into a radially mounted bore 113.
  • This radial bore 113 opens into a Also referred to as the connecting space annulus 114th
  • a special motor 22 with a "split tube” 110 also referred to as a sealing tube, has been developed.
  • the name “Canned” stems from the fact that this tube 110 is disposed between the rotor 22.1 and the stator 22.2.
  • the sealing or gap tube 110 is made of a non-magnetic material, preferably of a high-temperature resistant, pressure-resistant, fiber-reinforced plastic.
  • the sealing tube 110 extends almost over the entire length of the stator and is sealed with the stator 22.2 including winding and motor housing 25.3 with plastic to form a unit.
  • the cover or housing part 25.2 projects with a corresponding centering collar 115 with O-ring groove 116 into the sealing or gap tube 110.
  • the cover or housing part 25.2 projects with a corresponding centering collar 115 with O-ring groove 116 into the sealing or gap tube 110.
  • On the side facing away from the pinion of the sealing or gap tube 110 protrudes a bolted to the motor flange or housing part 25.4 Bearing fixing screw 117 with a corresponding centering collar 118 with O-ring groove 119 in the sealing or gap tube 110.
  • O-ring grooves 116, 119th taken O-rings take over the sealing function, so seal the canned space 107 on both sides of the rotor 22.1 at least leak fluid from.
  • the common motor-pump shaft 23 carries the pressed-rotor 22.1, includes pressure equalization holes and the Lagerbefest Trents- or sensor screw 107 for receiving a speed sensor 120.
  • the motor-pump shaft 23 is the motor side only on or in the radial ball bearing 111 and pump side or in at least one plain bearing, preferably on or in two plain bearings 121.1, 121.2, stored.
  • the pinion 26 of the pump or hydraulic machine 21 is mounted by a clearance fit on the pump motor shaft 23 and taken by the slightly lekssballige key 37 rotating.
  • the inner ring 122.1 of the ball bearing 111 is fixedly connected to the motor pump shaft 23 through the bearing mounting and sensor screw 112.
  • the outer ring 122.2 of the ball bearing 111 is bolted to the bearing mounting screw 117 with the electronics side bearing cover or housing part 25.4.
  • the bearing cap 25.4 has a specially stepped blind bore 123 in which the Lagerbefest Trents- and sensor screw 112 projects.
  • the signal is transmitted through the closed bearing cover or housing part 25.4, which has a wall thickness of a few millimeters in the region of the sensor 120. Preferably, the wall thickness is about 2 mm.
  • the electronic board 124 of the speed sensor 120 is arranged in a housing part in the form of a flange 25.5 and at a certain axial distance to a two-sided populated board 125 of the motor controller, here the output stage 126th On this output stage 126, a controller board is arranged.
  • the phase lines 127 (see FIG. 1 ) of the motor 22 preferably lead through holes in the housing part or bearing cap 25.4 and are screwed to the output stage 126, plugged or soldered.
  • sensor lines of temperature sensors which measure the winding temperatures of the motor 22.
  • the connection of the motor-pump unit 20 via a power connector 128 and a small sized signal connector 129.
  • the two connectors 128, 129 are sealingly attached to the electronics box 130.
  • the electronics box 130 is formed with a tubular housing part 25.6 and with a designed as a cover housing part 25.7 and with the tubular, also referred to as bearing cap or motor flange housing part 25.4.
  • the electronics box 130 with cooling fins 131 is also screwed on. Between the individual elements of the electronics box 130 sealing elements are also arranged.
  • the output stage 126 is mounted on a, preferably made of copper, receiving angle 132 with thermal paste. As a result, the heat development of the components through the copper angle 132 in the cooling fins 131 of the tubular housing part 25.6 of the electronics box 130 is passed.
  • the intermediate housing of the hydraulic machine also constitutes the bearing cap 25.4 or motor flange of the electric motor 22.
  • the hydraulic machine is designed as a compensated 4-quadrant internal gear machine 21 and is substantially fluidly connected to the interior of the sealing or gap tube 110.
  • an electric motor 22 has been found in the form of a brushless DC motor (EC motor) to be particularly advantageous.
  • the rotor 22.1 of the electric motor 22 includes a plurality of also referred to as leakage rotor channels recesses 133.1, 133.2, 133.3, 133.4, 133.5. Preferably, these are arranged at equal circumferential angles about the rotor rotational axis 33.1 or about the shaft rotational axis 35 offset from each other. In the embodiment shown, there are five leakage rotor channels 133.1, 133.2, 133.3, 133.4, 133.5. intended.
  • the rotor 22.1 comprises a plurality of high-performance magnets 134, preferably permanent magnets.
  • the magnets 134 are arranged offset in the same circumferential angles about the rotor axis of rotation 34.1 or about the shaft rotation axis 35.
  • ten magnets 134 are provided.
  • the magnets 134 are provided with a tubular bandage 135 on their outer surface facing away from the rotor rotational axis 34.1 or from the shaft rotational axis 35. This bandage 135 limits the rotor 22.1 radially outward on its outer circumference.
  • the rotor 22.1 is rotatably mounted in a cylindrical receiving space 136 of the stator 22.2 relative to this.
  • a sealing tube gap tube 110 is arranged, which is fixedly connected to the stator 22.2.
  • a narrow annular gap 137 is formed, which is also designated with a leakage gap channel 137.
  • This annular channel 137 extends in the axial direction 39, preferably substantially over the entire axial length or over the entire axial length, of the rotor 22.1.
  • the stator 22.2 comprises an inner tube 138 and an outer tube 139 and a plurality of webs 140 extending in the radial direction 109 between the inner tube 138 and the outer tube 139 and also in the axial direction 39, which are connected at one end to the inner tube 138 and the other end to the outer tube 139 ,
  • preferably twelve webs 140 are provided (see FIG. 14 ). How out FIG. 12 can be seen, the webs 140 at their radially outer ends a recess 141, in which the outer tube 139 of the stator 22.2 is arranged.
  • the respective recess 141 has an axial width or the outer tube 139 has an axial length which is slightly smaller than the axial length of the rotor 22.1.
  • the stator 22.2 is made of a plurality of stator laminations. Between adjacent webs 140 of the webs 140, the inner tube 138 and the outer tube 139 of the stator 22.2, a receiving space 142 is formed in each case. In the embodiment shown, therefore, preferably twelve receiving spaces 142 are provided corresponding to the number of webs 140. Each receiving space 140 serves to accommodate stator windings made of metal wires, which form the phase lines 127. Furthermore, each receiving space 142 serves to receive potting material.
  • the stator 22.2 is received in a cylindrical stator-receiving space of the motor housing 25.3 of the housing 25 of the motor-pump unit 20 and is fixedly connected to the motor housing 25.3.
  • the housing part 25.2 of the working chamber 24 of the pump 21 delimiting housing parts 25.1, 25.2 of the housing 25 is at least one fluidverbunder with the working chamber 24, preferably designed as an annular space, leakage channel 101.1, 101.2 arranged over which during operation of the internal gear pump 21 under pressure along the resulting axial and radial sealing surfaces leakage oil is derived.
  • the at least one leakage channel 101.1, 101.2 is used for discharging an operating gear of the internal gear machine 21, in particular in the case of a radial and / or axial gap seal by means of the radial sealing segments 43.1, 43.2 and / or the at least one axial sealing plate 58.1, 58.2 the fluid pressure medium existing, leakage fluids.
  • each axial sealing plate 58.1, 58.2 which is open towards the working chamber 24 in the axial direction 39 and which is open towards the shaft 23 in the radial direction 109 (see FIG Figures 2 . 4 and 11 ).
  • the shaft 23 extends with a shaft end 23.1 of its two shaft ends 23.1, 23.2 of the pinion 26 away in the axial direction 39 by the shaft 23 carried by the rotor 22.1.
  • the arranged in the housing part 25.1 of the housing 25 connecting channels 105.1, 105.2 are in the housing 25 or in a working chamber 24 of the internal gear 21 limiting housing part 25.2 of the housing 25 arranged check valves 143.1, 143.2 fluidly connected to the at least one leakage channel 101.1, 101.2 Leakage channel loop 108 connected.
  • the leakage channel loop 108 extends beyond the rotor end 144.1 of the rotor 22.1 extending away from the pinion 26.
  • the leakage channel loop 108 has the leakage wave channel 102 extending in the axial direction 39 in the shaft 23 or through the shaft 23, also referred to as a relief bore, and at least one fluidically connected to the leakage wave channel 102, spaced radially from the leakage channel.
  • Shaft channel 102 in the axial direction 39 through the rotor 22.1 extending through leakage rotor channel 133.1, 133.2, 133.3, 133.4, 133.5 of the rotor 22.1 and also fluidly connected to the leakage shaft channel 102, viewed in the radial direction 109, between the rotor 22.1 and formed on the stator 22.2, extending in the axial direction 39 leakage gap channel 137 on.
  • the check valves 143.1, 143.2 open in a fluid flow direction from the leakage channel loop 108 to the respective active low pressure region of the working chamber 24 and block in an opposite or fluid flow direction from the respective active high pressure region of the working chamber 24 to the leakage channel loop 108 the internal gear pump 21 reaches that the leakage fluid from the at least one leakage channel 101.1, 101.2 through the Leakage channel loop 108 flows into the working chamber 24. From there, the leakage fluid essentially flows into the connection channel 105.1, 105.2 associated with the respective active low-pressure region, ie, except for a small leakage current component which is small in comparison to the total leakage flow.
  • a leakage wave channel 102 extending in the axial direction 39 is arranged in the shaft 23, which is fluid-connected to the at least leakage channel 101.1, 101.2, and at least one is located in the rotor 22.1 , preferably at a radial distance, in particular parallel to the leakage wave channel 102, in the axial direction 39 by the rotor 22.1 extending leakage rotor channel 133.1, 133.2, 133.3, 133.4, 133.5 is arranged, which is in fluid communication with the leakage shaft channel 102 and / or that a, as viewed in the radial direction 109, between the rotor 22.1 and the stator 22.2 formed, extending in the axial direction 39 leakage gap channel 137 is fluidly connected to the leakage shaft channel 102, and that the leakage wave channel 102 or the leakage rotor channel 133.1, 133.2, 133.3, 133.4, 133.5 and / or the leakage gap channel 137 via a in the housing 25 or
  • FIG. 12 shows a longitudinal section through the gear machine 21 in the region of two arranged check valves 143.1, 143.2.
  • the check valves 143.1, 143.2 which are also designated with shuttle valves, have the task of always connecting the canned space 107 with the working ports or connecting channels 105.1 and 105.2 such that the lowest possible pressure prevails in the canned space 107.
  • the motor-pump unit 20 described is preferably used in a closed hydraulic system not shown in the figures.
  • This hydraulic system in addition to a, for example, double or single-acting hydraulic cylinder and a, preferably designed as a diaphragm pressure accumulator contain pressure accumulator, which can compensate for volume changes by different piston surfaces and by temperature fluctuations or compensates.
  • the accumulator ensures a certain system or preload pressure.
  • the system or biasing pressure is in the range of 5 to 40 bar.
  • the working pressure of the internal gear machine 21 is superimposed on this preload or system pressure.
  • the working pressure can be up to 120 bar or even up to 250 bar or more.
  • the shuttle valves 143.1, 143.2 now have the task of ensuring that only the lower pressure in the region of the canned space 107 prevails.
  • the shuttle valves 143.1, 143.2 are each in one in the respective pressure field 61.1, 61.2, for example here of the housing part 25.2 (see FIGS. 7 and 13 ), preferably formed as a blind bore, also as a channel part of a return flow 154.1, 154.2 designated axial bore 145.1, 145.2 (see FIGS. 12 and 13 ).
  • an oblique bore 146.1, 146.2 of the respective return flow channel 154.1, 154.2 connects the bore base of the respective axial bore 145.1, 145.2 with the canned space 107 via the connection space 106 (see FIG FIGS. 12 and 13 ).
  • the shuttle valves 143.1, 143.2 are commercially available spring-loaded check valves with a ball 147 as a sealing or locking element and a spring 148, by means of which the ball 147 is biased in its sealing or locking position.
  • the ball 147 and the spring 148 are mounted in a guide member 149.
  • the guide element 149 is pressed into the respective axial bore 145.1, 145.2 and secured with a securing sleeve.
  • 104.2 now arises in one of the pressure fields 61.1, 61.2, a higher pressure.
  • the shuttle valve 61.1 associated with the fluid pressure 61.1 then closes, and with an operating direction in the second direction of rotation 104.2, then the shuttle valve assigned to the pressure field 61.2 then closes.
  • connection space 106 a slight overpressure
  • the shuttle valve 143.1, 143.2 in the lower pressure-loaded pressure field 61.1, 61.2 opens.
  • the preload pressure or system pressure can be many times lower than the working pressure.
  • the leakage oil guide described above also ensures that the ball bearing 111 arranged on the motor side is supplied with oil. As a result, this bearing 111 is lubricated, removed the frictional heat and thus significantly increases the life.
  • the radial bore 113 on the ball bearing side viewed from the pinion 26, opens in front of the ball bearing 111, it is in fluid communication with the bearing gap 155 formed between the inner ring 122.1 and the outer ring 122.2 of the ball bearing 111 (see FIG Figures 11 and 12 ), so that nevertheless reaches both a sufficient lubrication and a cooling effect and removes frictional heat.
  • An improvement in the bearing lubrication could be achieved by an axial bore not shown in the figures and an additional, also not shown in the figures, radial bore in the Lagerbefest Trents- or sensor screw.
  • additional bores can be mounted in the motor pump shaft 23 or alternatively, ie instead, in addition to the radial bore 113 arranged in front of the bearing 111 or in front of the bearing mounting or sensor screw 112, as viewed from the pinion 26.
  • a one-piece or one-piece is made Motor pump shaft 23 shown.
  • separate shafts in the form of a pump shaft and a motor shaft could also be provided.
  • An entrainment could be done by a spline, for example, with a head or rankingzentritation to fix the two waves.
  • a fixation of the two waves could also be done via an additional fit between the motor and pump shaft.
  • both the motor shaft and the pump shaft would have to have an axial leakage shaft channel or an axial relief bore, which would have to be fluidly connected to one another.
  • the bearing mounting and sensor screw 112 is made of a non-magnetic material so as not to affect the magnetic signals of the sensor 120.
  • the sensor 120 is mounted in an axial bore 150 of the bearing mounting and sensor screw 112, preferably glued.
  • the outer diameter of the Lagerbefest Trents- and sensor screw 112 is greater than the inner diameter of the ball bearing 111 and its inner ring 122.1.
  • the sensor screw 112 is offset at its outer diameter and surrounds the sensor 120 with a thin-walled tubular part 151. This tubular part 151 with sensor 120 protrudes into a Blind bore 152 in the housing or cover part 25.4.
  • the bottom of the blind bore 152 has a residual wall thickness of a few millimeters, preferably of about 2 mm.
  • the motor-pump unit 20 can be loaded with a high system pressure, preferably up to 200 bar.
  • the small residual wall thickness of the bottom or wall part 153 of the tubular part 151 of the bearing fastening and sensor screw 112 containing the sensor 120 influences the magnetic flux of the sensor 120 only to a small extent.
  • the bore 150 in the housing or cover part 25.4 only slightly larger than the outer diameter of the tubular part 151 of the Lagerbefest Trents- and sensor screw 112. This is the pressurized surface of the low residual wall thickness having bottom or wall portion 153 of the tubular part Ideally kept as small as possible.

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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)
EP15158367.1A 2014-03-21 2015-03-10 Unité pompes-moteur Active EP2921702B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014103959.9A DE102014103959A1 (de) 2014-03-21 2014-03-21 Motor-Pumpen-Einheit

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EP2921702A2 true EP2921702A2 (fr) 2015-09-23
EP2921702A3 EP2921702A3 (fr) 2015-11-11
EP2921702B1 EP2921702B1 (fr) 2021-06-16

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US10290961B2 (en) 2016-09-26 2019-05-14 Rausch & Pausch Gmbh High currency connection
CN110185609A (zh) * 2019-06-18 2019-08-30 江苏德华泵业有限公司 一种高压齿轮污水泵
CN112985999A (zh) * 2021-02-09 2021-06-18 中铁隧道局集团有限公司 一种用于多场环境耦合作用下的注浆模型试验装置及方法
CN113847238A (zh) * 2020-06-25 2021-12-28 爱塞威汽车有限责任公司 泵滑动轴承的轴向泄压

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JP6507998B2 (ja) * 2015-11-03 2019-05-08 株式会社デンソー 燃料ポンプ
US10914305B2 (en) * 2016-05-27 2021-02-09 Ghsp, Inc. Thermistor flow path
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DE102016114540A1 (de) 2016-08-05 2018-02-08 Eckerle Industrie-Elektronik Gmbh Elektrohydraulische Maschine mit integriertem Sensor
JPWO2018030325A1 (ja) * 2016-08-09 2019-06-13 日本電産株式会社 駆動装置
DE102017127675B4 (de) * 2017-11-23 2023-03-23 HAWE Altenstadt Holding GmbH Hydraulische Druckversorgungseinheit
JP2019112977A (ja) * 2017-12-21 2019-07-11 日本電産トーソク株式会社 電動オイルポンプ
JP2019112978A (ja) * 2017-12-21 2019-07-11 日本電産トーソク株式会社 電動オイルポンプ
DE102018126442A1 (de) * 2018-10-24 2020-04-30 Thomas Magnete Gmbh Elektrohydraulisches Motorpumpenaggregat
DE102019111980A1 (de) 2019-05-08 2020-11-12 Rapa Automotive Gmbh & Co. Kg Energieversorgungseinheit für aktives fahrwerksystem
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US10290961B2 (en) 2016-09-26 2019-05-14 Rausch & Pausch Gmbh High currency connection
CN110185609A (zh) * 2019-06-18 2019-08-30 江苏德华泵业有限公司 一种高压齿轮污水泵
CN110185609B (zh) * 2019-06-18 2024-04-16 江苏德华泵业有限公司 一种高压齿轮污水泵
CN113847238A (zh) * 2020-06-25 2021-12-28 爱塞威汽车有限责任公司 泵滑动轴承的轴向泄压
EP3929439A1 (fr) * 2020-06-25 2021-12-29 Schwäbische Hüttenwerke Automotive GmbH Décharge axiale de pression dans les paliers lisses des pompes
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CN112985999A (zh) * 2021-02-09 2021-06-18 中铁隧道局集团有限公司 一种用于多场环境耦合作用下的注浆模型试验装置及方法

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US10060432B2 (en) 2018-08-28
EP2921702A3 (fr) 2015-11-11
US20150267699A1 (en) 2015-09-24
DE102014103959A1 (de) 2015-09-24
EP2921702B1 (fr) 2021-06-16

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