EP2921703A2 - Unité pompes-moteur - Google Patents

Unité pompes-moteur Download PDF

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Publication number
EP2921703A2
EP2921703A2 EP15158368.9A EP15158368A EP2921703A2 EP 2921703 A2 EP2921703 A2 EP 2921703A2 EP 15158368 A EP15158368 A EP 15158368A EP 2921703 A2 EP2921703 A2 EP 2921703A2
Authority
EP
European Patent Office
Prior art keywords
segment
pinion
ring gear
sealing
radial
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
EP15158368.9A
Other languages
German (de)
English (en)
Other versions
EP2921703B1 (fr
EP2921703A3 (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 EP2921703A2 publication Critical patent/EP2921703A2/fr
Publication of EP2921703A3 publication Critical patent/EP2921703A3/fr
Application granted granted Critical
Publication of EP2921703B1 publication Critical patent/EP2921703B1/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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C14/265—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/10—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/103—Rotary-piston pumps specially adapted for elastic fluids 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 elements
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid
    • F04C27/004—Radial sealing elements specially adapted for intermeshing-engagement type pumps, e.g. gear 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F04C27/006—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type pumps, e.g. gear 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/04—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for reversible 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C28/265—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
    • 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

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.
  • the internal gear machine can be driven or driven by means of the electric motor as an internal gear pump or the electric motor can be driven or driven by means of the internal gear machine as a power generator.
  • Such 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.
  • the pinion segment and / or the ring gear segment has a sealing roller groove extending in the axial direction, in which a sealing roller movable in the radial direction relative to the pinion segment and to the ring gear segment for sealing the radial gap between the pinion gear segment and the ring gear segment is arranged and that the pinion segment and / or the ring gear segment has a extending in the axial direction segment spring groove which is arranged offset in a circumferential distance to the sealing roller groove in the direction of the high-pressure region associated pinion segment end of the pinion segment or Hohlradsegmentendes the Hohlradsegments, wherein in the segment spring groove a prestressed Is arranged spring, by means of which the Hohlradsegment and the pinion segment are pressed away from each other in such a radial direction that the pinion segment with a radially inwardly facing outer surface of pinion teeth of the Ritzelz rn
  • the sealing plate control channel is formed as a sealing plate-control groove.
  • the sealing plate control channel has a V-shaped cross section in a cross section running parallel to the axial direction.
  • sealing plate control channel extends along the radial slot and / or if the sealing plate control channel extends in the circumferential direction.
  • the sealing plate control channel has a control channel length, via which it leads to the radial slot is open and the radial slot over its entire control channel length is directly opposite.
  • the sealing plate control channel opens into a pressure-sensitive, preferably kidney-shaped, sealing plate recess, in particular sealing kidney, of the axial sealing plate which is arranged in the high-pressure region and which is assigned to the same sides of the toothed wheels axial faces of the gears is open and this is directly opposite, so that the sealing plate control channel via the sealing plate recess can be acted upon directly with the pressure medium.
  • the sealing plate recess can also be referred to as a sealing plate control recess.
  • the sealing plate control channel extends from the sealing plate recess, preferably in the circumferential direction, along the radial slot.
  • the sealing plate control channel extends from the sealing plate recess, preferably in the circumferential direction, either along the radial slot into a region which lies directly opposite the segment spring groove or along the radial slot and the segment spring groove, the segment spring groove immediately opposite, extends into a region which is arranged either between the segment spring groove and the sealing roller groove or which extends to the sealing roller groove or which is directly opposite the sealing roller groove.
  • the Radialdichtsegment control channel extends in a direction or circumferential direction in which the pinion about its pinion axis or in which the ring gear is rotatable about its Hohlradcardachse and / or that the Radialdichtsegment Control channel extends in a transverse or perpendicular to the axial direction extending imaginary plane or circumferential direction.
  • the radial sealing segment control channel is designed as a chamfer or a groove or that at least a first radial sealing segment control channel is designed as a chamfer and at least a second radial sealing segment control channel are designed as a groove.
  • the radial sealing segment control channel extends between the segment spring groove and the sealing roller groove and / or that the radial sealing segment control channel opens into the segment spring groove and / or into the sealing roller groove and / or that the radial sealing segment control channel between the segment spring groove and the abutment surface of the stop extend and / or that the Radialdichtsegment control channel extends to the stop surface of the stop and / or that the Radialdichtsegment control channel over or beyond the stop surface of the stop out to a ring gear teeth of the ring gear teeth of the ring gear opposite free surface of the pinion gear segment and / or the ring gear segment extends.
  • the pinion segment and / or the ring gear segment or the filler is or are formed sickle-shaped.
  • the pinion segment can be designed in one piece and / or be made of one part and / or the ring gear segment can be designed in one piece and / or be made of one part.
  • the radial sealing segments comprise at least two or exactly two ring gear segments and / or that the radial sealing segments comprise at least two or exactly two pinion segments.
  • the pinion segment and / or the Hohlradsegment by means of at least one retaining pin which is rotatably mounted in a the same sides of the gears associated axial end faces of the gears opposite housing part of the housing, against a displacement in the direction of Low pressure region or a suction side of the working chamber is mounted, wherein the retaining pin has at its end associated with the filling piece a holding body, which, viewed in a cross section perpendicular to the axial direction, a V-shaped or trapezoidal cross-section and comprises holding body support surfaces, the one include tips, preferably 20 to 30 degrees or amounts to approximately 24 degrees, angle, and wherein the pinion segment and / or the ring gear segment has at least one sealing segment recess for receiving the holding body of the at least one retaining pin, in a em cross-section viewed perpendicular to the axial direction, also has a V-shaped or a trapezoidal cross-section and includes sealing segment support
  • At least two Axialdruckfelder may be provided in the form of recesses or depressions, which are provided in the at least one Axialdichtplatte and / or which are provided in the housing part, the at least one Axialdichtplatte on its away from the gears away side opposite lies.
  • the filler and / or the control panels or pressure kidneys of one or each Axialdichtplatte and / or the Axialdruckfelder and / or the at least one or each Axialdichtplatte symmetrical to an imaginary the pinion rotation axis and the ring gear Rotational axis containing symmetry plane is designed or are.
  • the electric motor is a brushless DC motor (EC motor).
  • 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 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. Preferably it is at the shaft 23 to 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 could be formed as a housing part of the housing of the motor-pump unit.
  • 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:
  • 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 rotatably mounted about a pinion axis 34.2.
  • 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.
  • 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, viewed in the 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.
  • the internal gear pump 21 rotates in its first operating direction, in which the pinion 26 and the ring gear 30 rotate in their first direction of rotation 104.1
  • fluid high pressure forms in a first region 44.1 of the working chamber 24, which is then the active first High pressure range 44.1 acts.
  • a fluid low pressure then forms in the second region 44.2 of the working chamber.
  • the internal gear pump 21 rotates in its second operating direction opposite to the first operating direction, ie in which the pinion 26 and the ring gear 30 rotate in their second direction of rotation 104.2 opposite to the first direction of rotation 104.1, fluid high pressure forms in the second region 44.2 Working chamber 24, which is then the active second high-pressure region 44.2.
  • a low-pressure fluid then forms in the first region 44. 1 of the working chamber.
  • 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 first connection channel 105.2 and the second connection channel 105 extend in the axial direction 39 parallel to one another
  • 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 formed in one piece 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 each has in the area each ring gear segment 43.1, 43.2 has an inner surface 72 pointing radially outwards relative 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 area 44.1, 44.2 assigned to the current direction of rotation of the pinion 26 and ring gear 30 into the said radial gap 75.1, 75.2 or into the corresponding gap space, which is also designated compensation space.
  • the pinion segment 43.1, 43.2 has two extending in the axial direction 39 Seal grooves 48.1, 48.2.
  • Each sealing roller groove 48.1, 48.2 is open to their axial ends facing away from each other.
  • a in the radial direction relative to the pinion segment 42 and the respective associated ring gear segment 43.1, 43.2 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.
  • each sealing roller 49.1, 49.2 is also pressed in the pressure-released state or in non-operation of the internal gear machine 21 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.
  • 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.
  • this spring 52.1, 52.2 are the associated Hohlradsegment 43.1, 43.2 and the pinion segment 42 in such a radial direction away from each other or pressed apart that the pinion segment 42 sealingly abuts with a radially inwardly facing outer surface 46 of ring gear teeth of the ring gear teeth 31 of the ring gear 30 and that the ring gear segment 43.1, 43.2 with a radial outwardly facing outer surface 47.1, 47.2, which points away from the outer surface 46 of the pinion gear 42, sealingly abuts against Hohlradzähen the Hohlradzähe 31 of the ring gear 30.
  • 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.
  • Each 54.1, 54.2 stop 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 engaging portion 33 on.
  • 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 respective 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 between the pinion teeth 28 of the pinion 26 formed pinion tooth spaces 29 this is arranged directly opposite 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 motor-pump unit 20 according to the invention or the internal gear machine 21 according to the invention has, inter alia, the following features essential to the invention:
  • the at least one axial sealing plate 58.1, 58.2 has on its end faces 56.1, 56.2; 57.1, 57.2 of the gears 26, 30 pointing side or inside 59.1, 60.1 at least one of the end faces 56.1, 56.2; 57.1, 57.2 of the gears 26, 30 towards open sealing plate recess or -Ausbloodung 63.3.1, 63.3.2 in the form of an acted upon with pressure medium additional or third sealing plate control channel, which is designed as a sealing plate control groove.
  • a third control channel of three control channels which in each case in the pressure medium acted upon kidney-shaped sealing plate recess or pressure kidney 62.1, 62.2 of the two sealing plate recesses or pressure kidneys 62.1, 62.2 of each thrust washer 58.1, 58.2 opens.
  • the said additional or third sealing plate control channel 63.3.1, 63.3.2 is open towards the associated radial gap 75.1, 75.2 and lies directly opposite the associated radial gap 75.1, 75.2 (see FIG FIG. 5 ).
  • the respective additional or third sealing plate control channel 63.3.1, 63.3.2 extends from the respective sealing plate recess or pressure kidney 62.1, 62.2 in the circumferential direction along the associated radial gap 75.1, 75.2 between the pinion segment 42 and the associated ring gear segment 43.1 , 43.2 into a region which lies directly opposite the segment spring groove 51.1, 51.2.
  • Said additional sealing plate control channel 63.3.1, 63.3.2 in contrast to the respective first and second control groove 63.1.1, 63.1.2; 63.2.1, 63.2.2 no control slot.
  • the invention further provides that the pinion segment 42 and / or the ring gear 43.1, 43.2 at least one Radialdichtsegment depression in the form of a circumferentially about the pinion axis 34.2 and the Hohlradcardachse 36 extending, acted upon by 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.
  • 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 shown symmetrically.
  • 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 additional control groove 63.3.1, 63.3.2 is mounted in at least one axial sealing plate, preferably in the axial sealing plates 58.1, 58.2.
  • 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, be made 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.
  • 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. As a result, jamming of the teeth 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 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 machined completely mechanically, but rather can be produced, for example, in the case of die-cast parts or other cast parts 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, recorded becomes.
  • 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 achieved by the V-shaped free surface 85 and the tooth engagement 33 by the seal along the engagement line.
  • 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 as well Connection space designated annulus 114.
  • a special motor 22 with a "split tube” 110 also referred to as a sealing tube, has been developed.
  • the term “can” derives from the fact that this tube 110 is arranged between the rotor 22.1 and the stator 22.2.
  • the sealing or gap tube 110 consists 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.
  • 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.
  • the O-ring grooves 116, 119th recorded O-rings not shown in the figures are, take over the sealing function, thus sealing 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 by 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 Trentsund sensor screw 112 protrudes.
  • 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 power amplifier 126 is arranged a regulator board.
  • 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 total 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.
  • leakage channel 101.1, 101.2 is arranged, through which the resulting during operation of the internal gear pump 21 under pressure along the 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 in a radial direction Distance to the leakage wave channel 102, extending in the axial direction 39 through the rotor 22.1 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 wave channel 102, viewed in the radial direction 109, formed between the rotor 22.1 and 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 ensures that the leakage fluid flows from the at least one leakage channel 101. 1, 101. 2 through the leakage channel loop 108 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 one, 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 shaft 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 in a working
  • 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 described motor-pump unit 20 is preferably used in a not shown in the figures, closed hydraulic system.
  • 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 located in a 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 locking 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.
  • 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.
  • 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.
  • an advantageous forced lubrication of the bearing 111 can be achieved.
  • a one-piece motor-pump shaft 23 is 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 Trentsund 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 with a high system pressure preferably up to 200 bar
  • 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.
EP15158368.9A 2014-03-21 2015-03-10 Unité pompes-moteur Active EP2921703B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014103958.0A DE102014103958A1 (de) 2014-03-21 2014-03-21 Motor-Pumpen-Einheit

Publications (3)

Publication Number Publication Date
EP2921703A2 true EP2921703A2 (fr) 2015-09-23
EP2921703A3 EP2921703A3 (fr) 2015-11-04
EP2921703B1 EP2921703B1 (fr) 2020-08-19

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EP (1) EP2921703B1 (fr)
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EP3822487A4 (fr) * 2018-07-12 2022-07-13 Emerson Climate Technologies (Suzhou) Co., Ltd. Dispositif de pompage de fluide et compresseur horizontal
US20230258176A1 (en) * 2022-02-14 2023-08-17 Dana Motion Systems Italia S.R.L. Electric motor with integrated pump
DE102022117048A1 (de) 2022-07-08 2024-01-11 Hydac Drive Center Gmbh Elektro-hydraulisches Antriebssystem
DE102022117052A1 (de) 2022-07-08 2024-01-11 Hydac Drive Center Gmbh Elektro-hydraulisches Antriebssystem

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DE102016114540A1 (de) 2016-08-05 2018-02-08 Eckerle Industrie-Elektronik Gmbh Elektrohydraulische Maschine mit integriertem Sensor
DE102016010669A1 (de) 2016-08-29 2018-03-01 Hydac Fluidtechnik Gmbh Motor-Pumpenvorrichtung
DE102016118163A1 (de) 2016-09-26 2018-03-29 Rausch & Pausch Gmbh Lösbare verbindungseinrichtung für hohe ströme
JP6546984B1 (ja) * 2017-12-27 2019-07-17 Ｋｙｂ株式会社 電動液圧アクチュエータ
US11168769B2 (en) 2018-09-14 2021-11-09 Lippert Components Manufacturing, Inc. Drive mechanism for telescopic linear actuator
US11649636B2 (en) 2018-10-09 2023-05-16 Taylor Made Group, Llc Tubular motor seal for extendable awning
DE102019111980A1 (de) 2019-05-08 2020-11-12 Rapa Automotive Gmbh & Co. Kg Energieversorgungseinheit für aktives fahrwerksystem
DE102019118384A1 (de) 2019-07-08 2021-01-14 Rapa Automotive Gmbh & Co. Kg Mpe-achssatz mit gemeinsamer ecu
DE102019118697A1 (de) * 2019-07-10 2021-01-14 Ipgate Ag Zahnradpumpe
DE102019118708A1 (de) * 2019-07-10 2021-01-14 Ipgate Ag Druckversorgungseinrichtung mit einer Zahnradpumpe
JP2021055553A (ja) * 2019-09-27 2021-04-08 株式会社Ｓｕｂａｒｕ 内接歯車ポンプ
US11680567B1 (en) 2020-02-27 2023-06-20 Parker-Hannifin Corporation Hydraulic gear pump with axial compensation
US11506200B1 (en) 2020-02-27 2022-11-22 Parker-Hannifin Corporation Hydraulic gear pump with radial pressure compensator
DE102020110217A1 (de) * 2020-04-14 2021-10-14 Hydraulik Nord Technologies GmbH Innenzahnradmaschine
DE102021105032A1 (de) 2021-03-02 2022-09-08 Rapa Automotive Gmbh & Co. Kg Gehäuseausführung für mpe-achssatz
CN113236554B (zh) * 2021-06-04 2022-06-21 中国人民解放军海军工程大学 一种可双向旋转的渐开线齿廓内啮合齿轮泵
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US20230258176A1 (en) * 2022-02-14 2023-08-17 Dana Motion Systems Italia S.R.L. Electric motor with integrated pump
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DE102022117052A1 (de) 2022-07-08 2024-01-11 Hydac Drive Center Gmbh Elektro-hydraulisches Antriebssystem
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Also Published As

Publication number Publication date
EP2921703B1 (fr) 2020-08-19
US9945377B2 (en) 2018-04-17
DE102014103958A1 (de) 2015-09-24
US20150267701A1 (en) 2015-09-24
EP2921703A3 (fr) 2015-11-04

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