EP2921703B1 - Unité pompes-moteur - Google Patents

Unité pompes-moteur Download PDF

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Publication number
EP2921703B1
EP2921703B1 EP15158368.9A EP15158368A EP2921703B1 EP 2921703 B1 EP2921703 B1 EP 2921703B1 EP 15158368 A EP15158368 A EP 15158368A EP 2921703 B1 EP2921703 B1 EP 2921703B1
Authority
EP
European Patent Office
Prior art keywords
sealing
segment
pinion
radial
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.)
Active
Application number
EP15158368.9A
Other languages
German (de)
English (en)
Other versions
EP2921703A3 (fr
EP2921703A2 (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
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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
    • 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
    • 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
    • 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 with a multi-part housing which comprises an internal gear machine for reversing operation and an electric motor which is coupled to the internal gear machine via at least one shaft rotatably mounted in the housing about a shaft axis of rotation, the internal gear machine comprising a working chamber, which is delimited by at least two housing parts of the housing and in which an externally toothed pinion having pinion teeth and an internally toothed ring gear which is eccentrically mounted with respect to the pinion are arranged, the ring gear teeth meshing with the pinion teeth in a tooth engagement region, and wherein between the pinion and a crescent-shaped free space is formed in the ring gear in which a multi-part filler piece is arranged which comprises a plurality of radial sealing segments which are movable relative to one another in the radial direction for the radial sealing of a high-pressure region of the working chamber, one of which first radial sealing segment forms a pinion segment resting against the pinion teeth, and of
  • 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 current generator.
  • a motor-pump unit can be used, for example, to control a highly dynamic hydraulic axis.
  • the document is from the prior art DE 10 2008 053 318 A1 known.
  • This describes a reversibly operable gear machine, comprising a housing in which two gear wheels are arranged.
  • a first storage chamber and a second storage chamber are provided, the first storage chamber in a first operating direction of the gear machine and the second storage chamber having a hydraulic fluid pressure in an opposite, second operating direction is acted upon and forms a hydrostatic bearing for a gear.
  • the publication also shows DE 10 2009 047 643 A1 an internal gear pump for a slip-controlled hydraulic vehicle brake system. It is proposed to form a filler piece (sickle) with a curved inner part running in the circumferential direction and a curved outer part running in the circumferential direction, which are articulated to one another at their suction-side ends and between which a leg spring is arranged, which opposes the inner part and the outer part apart Tooth tips of the teeth of a pinion and a ring gear of the internal gear pump presses.
  • EP 1 760 315 A2 an internal gear pump with ring gear, pinion and filler made of sealing segment and segment carrier.
  • a pressure chamber is formed between the sealing segment and the segment carrier.
  • an additional groove is provided between the pressure chamber and a first tooth gap in the ring gear.
  • the at least one axial sealing plate has at least one sealing plate recess open towards the end faces of the gears in the form of a sealing plate control channel that can be acted upon by pressure medium, which starts from a sealing plate recess, is open towards the radial gap and directly towards the radial gap opposite, being in the Sealing plate recess two control grooves open towards the end faces, a first of the control grooves being arranged directly opposite one another of the control grooves between the pinion teeth and the second of the control grooves between the internal gear teeth.
  • a further development of the invention provides that the pinion segment and / or the ring gear segment has or have at least one radial sealing segment depression in the form of a radial sealing segment control channel which extends in a circumferential direction around the pinion axis of rotation or the ring gear axis of rotation and can be acted upon by pressure medium or with the pressure medium, which is open to the radial gap and which opens directly into the radial gap.
  • the pinion segment and / or the ring gear segment has a sealing roller groove that extends in the axial direction and in which a sealing roller, movable in the radial direction relative to the pinion segment and to the ring gear segment, is used to seal the radial gap between the pinion element and the ring gear segment is arranged and that the pinion segment and / or the ring gear segment has a segment spring groove extending in the axial direction, which is offset at a circumferential distance from the sealing roller groove in the direction of a pinion segment end of the pinion segment or ring gear segment end of the ring gear segment assigned to the high pressure area, with a preloaded in the segment spring groove Spring is arranged, by means of which the ring gear segment and the pinion segment are pressed away from one another in the radial direction in such a way that the pinion segment with a radially inward facing outer surface on pinion teeth of the pinion teeth and that the ring gear segment with a radially outwardly
  • sealing plate control channel is designed as a sealing plate control groove.
  • a further development of the invention provides that the sealing plate control channel in a parallel to the axial direction extending cross section viewed has a V-shaped cross section.
  • a further development of the invention provides that the sealing plate control channel extends along the radial slot and / or when the sealing plate control channel extends in the circumferential direction.
  • sealing plate control channel has a control channel length over which it is open to the radial slot and is directly opposite the radial slot over its entire control channel length.
  • the sealing plate control channel opens into a preferably kidney-shaped sealing plate recess, in particular kidney-shaped sealing plate, which is arranged essentially in the high-pressure area and can be acted upon by pressure medium, the axial end faces of the gears assigned to the same sides of the gears Gears is open and is directly opposite, so that the sealing plate control channel can be acted upon directly by the pressure medium via the sealing plate recess.
  • the sealing plate recess can also be referred to as a sealing plate control recess.
  • sealing plate control channel extends, starting from the sealing plate recess, preferably in the circumferential direction, along the radial slot.
  • a further development of the invention provides that the sealing plate control channel, starting from the sealing plate recess, preferably in the circumferential direction, either along the radial slot into an area which is directly opposite the segment keyway or along the radial slot and the segment keyway, directly opposite the segment keyway, extends into an area either located between the segment keyway and the sealing roller groove or which extends to the sealing roller groove or which is directly opposite the sealing roller groove.
  • a further development of the invention provides that the radial sealing segment control channel extends in a direction or circumferential direction in which the pinion is or are rotatable about its pinion axis of rotation or in which the ring gear is or are rotatable about its ring gear axis of rotation and / or that the radial sealing segment control channel extends in a direction or circumferential direction lying transverse or perpendicular to the axial direction.
  • a development of the invention provides that the radial sealing segment control channel is designed as a bevel or as a groove or that at least one first radial sealing segment control channel is designed as a bevel and at least one second radial sealing segment control channel is designed as a groove.
  • a further development of the invention provides that 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 the sealing roller groove and / or that the radial sealing segment control channel extends between the segmented spring groove and the stop surface of the stop extends and / or that the radial sealing segment control channel extends up to the stop surface of the stop and / or that the radial sealing segment control channel extends over or beyond the stop surface of the stop to a ring gear tooth of the ring gear teeth of the ring gear opposite free surface of the pinion segment and / or the ring gear segment.
  • a further development of the invention provides that the pinion segment and / or the ring gear segment or the filler piece is or are sickle-shaped.
  • the pinion segment is designed in one piece and / or is made from one part and / or the ring gear segment is made in one piece and / or is made from one part.
  • a further development of the invention provides that the radial seal segments comprise at least two or exactly two ring gear segments and / or that the radial seal segments comprise at least two or precisely two pinion segments.
  • a further development of the invention provides that the pinion segment and / or the ring gear segment by means of at least one retaining pin, which is rotatably mounted in a housing part of the housing that is located opposite the same sides of the gear wheels and is located opposite the housing part of the housing, against displacement in the direction of a low-pressure area or is mounted on a suction side of the working chamber, the retaining pin having at its end associated with the filler piece a retaining body which, viewed in a cross section perpendicular to the axial direction, has a V-shaped or trapezoidal cross-section and holding body support surfaces which enclose an acute angle, preferably 20 to 30 degrees or approximately 24 degrees, 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, which , viewed in a cross-section perpendicular to the axial direction, also has a V-shaped or a trapezoidal cross-section and comprises sealing segment support surfaces, which also
  • a further development of the invention provides that there are at least two axial pressure fields in the form of recesses or depressions, which are provided in the at least one axial sealing plate and / or which are provided in the housing part that widens the at least one axial sealing plate on its away from the gear wheels Side opposite.
  • the at least one axial sealing plate has at least two control fields or pressure kidneys in the form of recesses or depressions on its side facing the end faces of the gearwheels.
  • a further development of the invention provides that the filler piece and / or the control fields or pressure kidneys one or each axial sealing plate and / or the axial pressure fields and / or the at least one or each axial sealing plate is designed symmetrically to an imaginary plane of symmetry containing the pinion axis of rotation and the ring gear axis of rotation.
  • a further development of the invention provides that the electric motor is a brushless direct current motor (EC motor).
  • EC motor brushless direct current motor
  • the shaft is a one-piece and / or one-piece motor pump shaft, on which the rotor is fixed in a rotationally fixed manner, preferably non-positively, in particular by pressing or shrinking on, and on which the pinion is fixed in a rotationally fixed manner, is preferably positively, in particular releasably, attached.
  • the motor-pump unit 20 comprises an internal gear machine 21 for reversing operation, an electric motor 22 and integrated electronics 74, in particular for speed control.
  • the electric motor 22 comprises a rotor 22.1 and a stator 22.2.
  • the rotor 22.1 which can rotate about a rotor axis of rotation 34.1 relative to the stator 22.2, is connected in a rotationally fixed manner to a shaft 23 which can rotate about a shaft axis of rotation 35.
  • the rotor 22.1 is connected to the gear via the shaft 23 the internal gear machine 21 is coupled.
  • the shaft 23 is preferably a common, one-piece motor pump shaft.
  • the motor pump shaft 23 is mounted in the housing 25 so as to be rotatable about a shaft rotation axis 35.
  • the motor-pump unit 20 can preferably be used for controlling a highly dynamic hydraulic axis, which is or are not shown in the figures.
  • the motor-pump unit 20 comprises a multi-part housing 25 which contains 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 designed 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 preferably used in a closed hydraulic system.
  • the motor-pump unit 20 is characterized by high dynamics, low noise and pulsation, recuperation, a long service life, absolute freedom from leaks, service life filling of the system, insensitivity to shock and insensitivity to dirt, water, especially salt water, and temperature, especially cold .
  • the motor-pump unit 20 has in particular the following design features:
  • a hydraulic pump in the form of an internal gear pump with axial and radial sealing gap compensation is used as the internal gear machine 21.
  • the internal gear machine 21 comprises a working chamber 24, which is delimited by preferably two housing parts 25.1 and 25.2 of the housing 25 of the motor-pump unit 20.
  • Two gear wheels 26, 30 are arranged in the housing 25 or in the working chamber 24. These are an externally toothed pinion 26 having pinion teeth 28 and an internally toothed ring gear 30 having ring gear teeth 31.
  • the ring gear 30 is mounted eccentrically in a bearing ring 27 with respect to the pinion 26.
  • the bearing ring 27 is non-rotatably connected to the housing part 25.2 of the housing 25, preferably pressed in.
  • the ring gear 30 is arranged in such a way 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 tooth engagement region 33.
  • the pinion 26 is rotatably mounted about a pinion axis of rotation 34.2.
  • the pinion rotation axis 34.2 is arranged coaxially to the shaft rotation axis 35 of the shaft 23.
  • the ring gear 30 is mounted rotatably about a ring gear axis of rotation 36.
  • the directions of rotation of pinion 26 and ring gear 30 are in the same direction. This means that if, for example, the pinion 26 rotates clockwise, then the ring gear 30 inevitably also rotates clockwise.
  • the pinion 26 is preferably detachably connected to the shaft 23, for example via a feather key 37, which engages positively in matching grooves 38.1, 38.2 of both the shaft 23 and the pinion 26 (see FIG Figure 3 ). Consequently, the pinion 26 and the shaft 23 are positively connected to one another in a rotationally fixed manner.
  • the ring gear axis of rotation 36 and the pinion axis of rotation 34.2 extend in an axial direction 39 parallel to one another.
  • a sickle-shaped free space 40 of the working chamber 24 is formed between the pinion 26 and the ring gear 30.
  • a multi-part sickle-shaped filler piece 41 is arranged in the free space 40.
  • the filler piece 41 comprises a plurality of radial sealing segments 42 which are movable relative to one another in the radial direction; 43.1, 43.2 for the radial sealing of the "active" high-pressure area 44.1, 44.2 of the working chamber 24, which is dependent on the direction of rotation 104.1, 104.2.
  • the high-pressure area 44.1, 44.2 is assigned to that area of the working chamber 24 which, starting from a pressure build-up area of the working chamber 24, the during 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 filler piece 41 or the area of the filler piece 41 in which at least one, preferably two, retaining pin (s) or retaining bolt 45.1, 45.2 for the filler piece 41 or for its radial sealing segments 42; 43.1, 43.2 is arranged, viewed in the respective direction of rotation 104.1, 104.2 of pinion 26 or ring gear 30, extends up to the tooth engagement area 33 in which the teeth 28, 31 of the gear wheels 26, 30 mesh with one another.
  • the respective active high-pressure area 44.1, 44.2 is semisickle-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
  • high fluid pressure forms in a first area 44.1 of the working chamber 24, which is then the active first High pressure area 44.1 acts.
  • a low fluid 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, in which the pinion 26 and the ring gear 30 rotate in their second direction of rotation 104.2 Rotate opposite to the first direction of rotation 104.1, high fluid pressure is formed in the second area 44.2 of the working chamber 24, which is then the active second high pressure area 44.2.
  • a low fluid pressure then forms in the first region 44.1 of the working chamber.
  • a first connection channel 105.1 opens into said first area 44.1 of working chamber 24 and a second connection channel 105.2 opens into said second area 44.2 of the working chamber. (please refer Figure 12 ).
  • the first working channel 105.1 is or is acted upon with high fluid pressure and when the internal gear pump 21 rotates in its second operating direction 104.2, the second working channel 105.2 is or becomes with the high fluid pressure of the fluid pressure medium applied.
  • the first connection channel 105.2 and the second connection channel 105 preferably extend parallel to one another in the axial direction 39
  • the radial seal segments 42; 43.1, 43.2 comprise a first radial sealing segment which forms a pinion segment 42, which can also be referred to as a segment carrier and which can be placed or rests against the pinion teeth of the pinion teeth 28 of the pinion 26.
  • the pinion segment 42 is formed in one piece and made from one part, for example by milling.
  • the radial seal segments 42; 43.1, 43.2 also include at least one second radial sealing segment which forms a ring gear segment 43.1, 43.2 and which can be placed or rests against the ring gear teeth of the ring gear teeth 31 of the ring gear 30.
  • two separate ring gear segments 43.1, 43.2 are provided, of which each ring gear segment 43.1, 43.2 on ring gear teeth the ring gear teeth 31 of the ring gear 30 can be applied or is applied.
  • the pinion segment 42 In the area of each ring gear segment 43.1, 43.2, the pinion segment 42 has an inner surface 72 pointing radially outward toward 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 which points radially inward toward the pinion segment 42 and which lies opposite the associated inner surface 72 of the pinion segment 42.
  • a radial gap 75.1, 75.2 is formed 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.
  • pressure medium preferably pressure oil, passes from the active high pressure area 44.1, 44.2 assigned to the current direction of rotation of the pinion 26 and the ring gear 30 into the said radial gap 75.1, 75.2 or into the corresponding gap space, which is also referred to as the 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 towards their axial ends pointing away from one another.
  • a sealing roller 49.1, 49.2 which is movable in the radial direction relative to the pinion segment 42 and the respectively assigned ring gear segment 43.1, 43.2 for sealing the radial gap 75.1, 75.2 between the pinion segment 42 and the respective ring gear segment 43.1, 43.2.
  • a pretensioned sealing roller spring 50.1, 50.2, preferably a leaf spring, is also arranged in each sealing roller groove 48.1, 48.2.
  • Each sealing roller spring 50.1, 50.2 is supported on the one hand on a groove base 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 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 respectively assigned ring gear segment 43.1, 43.2 even when the internal gear unit 21 is depressurized or not in operation.
  • 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 towards their axial ends pointing away from one another.
  • a pretensioned 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 arranged offset in the circumferential direction at a circumferential distance or circumferential angle to the respectively assigned sealing roller groove 48.1, 48.2, namely in the direction of a pinion segment end assigned to the high pressure area 44.1, 442., which is dependent on the direction of rotation 53.1, 53.2 of the pinion segment 42 offset.
  • the assigned ring gear segment 43.1, 43.2 and the pinion segment 42 are pressed away from or apart in the radial direction in such a way that the pinion segment 42 with a radially inwardly facing outer surface 46 rests against the ring gear teeth of the ring gear teeth 31 of the ring gear 30 in a sealing manner and that the ring gear segment 43.1, 43.2 with a radially outwardly facing outer surface 47.1, 47.2, which points away from the outer surface 46 of the pinion segment 42, rests sealingly on the ring gear teeth of the ring gear tooth 31 of the ring gear 30.
  • the pinion segment 42 is designed as a segment carrier for the respective ring gear segment 43.1, 43.2 and has a stop 54.1, 54.2, which can also be referred to as a stop pocket, for each ring gear segment 43.1, 43.2.
  • Each 54.1, 54.2 stop has a stop surface 55.1, 55.2 which extends in the axial direction 39 and radially outward towards the ring gear 30 to support the respective ring gear segment 43.1, 43.2 against the respective ring gear segment 43.1, 43.2 being drawn into the internal gear unit 21 during operation Tooth engagement area 33.
  • Each stop 54.1, 54.2 is with its stop surface 55.1, 55.2 at a circumferential distance or at a circumferential angle to the respective segment keyway 51.1, 51.2 in the circumferential direction in the direction of the pinion segment end 53.1, 53.2 of the pinion segment 42 assigned to the active high pressure area 44.1, 44.2 which is dependent on the direction of rotation staggered.
  • two axial sealing plates 58.1, 58.2 which are movable in the axial direction 39 are provided for each housing part 25.1, 25.2. These serve to seal off the high-pressure area 44.1, 44.2 of the working chamber 24, which area is dependent on the direction of rotation of the gear wheels 26, 30.
  • the axial sealing plates 58.1, 58.2 can also be referred to as axial washers. It goes without saying that only a single axial sealing disk can also be provided.
  • the or each axial sealing disk 58.1, 58.2 is between the respectively assigned end faces 56.1, 56.2; 57.1, 57.2 of the gears 26, 30 and a housing part 25.1, 25.2 of the housing 25.
  • the or each axial sealing disk 58.1, 58.2 is, during operation of the internal gear machine 21, by means of pressure medium under high pressure with its respective inner surface 59.1, 60.1 against the respectively assigned end surfaces 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 labeled with axial fields (see Figure 7 ).
  • the pressure fields 61.1, 61.2 form control fields.
  • the pressure fields 61.1, 61.2 are provided in the form of recesses in the respectively assigned housing part 25.1, 25.2 of the housing 25.
  • the pressure fields or a pressure field assigned to 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 disks 58.1, 58.2 have kidney-shaped control fields on their inner sides 59.1, 60.1, that is to say those sides which face the pinion 26 and the ring gear 30 62.1, 62.2, which are also referred to as sealing plate recesses or pressure kidneys (see Figures 4 and 5 ). These are recesses or depressions in the respective axial disk 58.1, 58.2.
  • These control fields 62.1, 62.2 like the pressure fields 61.1, 61.2, can be acted upon with pressure medium under high pressure or are acted upon by pressure medium of the respective high pressure area 44.1, 44.2 during operation of the internal gear machine 21. This creates a counterforce which counteracts the force of the pressure fields 61.1, 61.2.
  • Each pressure kidney 62.1, 62.2 are at least two control grooves 63.1.1, 63.1.2; 63.2.1, 63.2.2 assigned to each of the assigned 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 area of the pinion tooth gaps 29 formed between the pinion teeth 28 of the pinion 26 is arranged directly opposite them and of which a second control groove 63.2.1, 63.2.2 in the area of the internal gear tooth gaps 32 formed between the internal gear teeth 31 of the internal gear 30 are arranged directly opposite them (see Figure 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 are provided in the form of a recess or depression in the respective axial disk 58.1, 58.2.
  • Each control slot 64.1.1, 64.1.2; 62.2.1, 64.2.2 ends in 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 approximately or essentially 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 facing side or inner side 59.1, 60.1 at least one to the end faces 56.1, 56.2; 57.1, 57.2 of the gears 26, 30 have a sealing plate recess or recess 63.3.1, 63.3.2 in the form of an additional or third sealing plate control channel that can be pressurized with pressure medium and is designed as a sealing plate control groove.
  • Said additional or third sealing plate control channel 63.3.1, 63.3.2 is open to the assigned radial gap 75.1, 75.2 and is directly opposite the assigned radial gap 75.1, 75.2 (see FIG Figure 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 assigned radial gap 75.1, 75.2 between the pinion segment 42 and the assigned ring gear segment 43.1 , 43.2 down to an area which is 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 tax groove 63.1.1, 63.1.2; 63.2.1, 63.2.2 do not have a control slot.
  • the respective additional sealing plate control channel or the respective third control groove 63.3.1, 63.3.2 ensures that the necessary radial compensation pressure in the associated radial gap 75.1, 75.2 between the pinion segment 42 and the respectively active ring gear segment 43.1, 43.2 is almost simultaneously is achieved with the respective reversal of the direction of rotation and thus in each case a particularly advantageous seal.
  • the pinion segment 42 and / or the ring gear segment 43.1, 43.2 have at least one radial sealing segment recess in the form of a radial sealing segment which extends in a circumferential direction around the pinion rotation axis 34.2 or the ring gear rotation axis 36 and can be acted upon by the pressure medium Control channel 65; 65.1, 65.2, 65.3, 65.4, 65.5, 65.6, which is open to the assigned radial gap 75.1, 75.2 and which opens directly into the assigned radial gap 75.1, 75.2.
  • the radial sealing segment control channel 65 preferably extends in a direction or in the direction of rotation in which the pinion 26 is or are rotatable about its pinion rotation axis 34.2 or in which the ring gear 30 is or are rotatable about its ring gear rotation axis (36) and / or extends Radial sealing segment control channel 65 in an imaginary plane running perpendicular to the axial direction 39.
  • pressure medium preferably pressure oil
  • Both the externally toothed pinion 26 and the internally toothed ring gear 30 are shifted in profile.
  • the pressure angle is 25 °.
  • the tooth tip height factor of the pinion toothing is 1.25 and the tooth tip height factor of the ring gear toothing is 1.24. This combination has proven to be extremely quiet.
  • the tooth tip edges are specially shaped.
  • a small backlash (0.02 to 0.05 mm or 0.01 to 0.025 x module) ensures that only very little pressure medium, in particular pressure oil, can flow to the "suction side" via the meshing even in highly dynamic reversing operation.
  • the radial compensation is provided by three segment parts 42, also referred to as radial sealing segments; 43.1, 43.2 shown symmetrically.
  • the one-piece pinion segment 42 is actively sealing for both directions of rotation both in pump and motor operation.
  • the two ring gear segments 43.1, 43.2 are only actively sealing when the direction of rotation is appropriate.
  • the inactive 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, that is 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 consist 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 against a sealing surface of the pinion segment 42 and against a sealing surface of the respectively active ring gear segment 43.1, 43.2 under pressure medium pressure.
  • the sealing rollers 49.1, 49.2 are pressed against the sealing surfaces by the respective sealing roller spring 50.1, 50.2.
  • the sealing surfaces are arranged at a special angle 66 which is smaller than 110 °.
  • the pressing force of the sealing rollers 49.1, 49.2 also causes a radial “spreading” of the radial sealing segments 42; 43.1, 43.2 and thus a system of the radial sealing segments 42; 43.1, 43.2 to the tooth tips of teeth 28, 31 of pinion 26 and ring gear 30.
  • the hydraulic control takes place via the radial gap 75.1, 75.2 between the outer circumferential surface 43 of the pinion segment 42, also referred to as the inner surface, and the respective inner circumferential 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 provided 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 pass through the radial gap 75.1, 75.2 between the radial sealing segments 42; 43.1, 43.2 get into the associated gap space, but also into the gaps between the segments 42; 43.1, 43.2.
  • This "double" control has been shown to be extremely effective in order not to suffer a drop in the conveyance, particularly in the case of the dynamic requirements during reversing operation of the internal gear machine 21.
  • the necessary radial compensation pressure in the gap 75.1, 75.2 between the segments 42; 43.1, 43.2 achieved almost "simultaneously" with the reversal of the direction of rotation and thus an optimal radial seal.
  • chamfers 65.1, 65.2, 65.5, 65.6 and / or grooves 65.3, 65.4 on the pinion segment 42 and / or on the ring gear segments 43.1, 43.2 can advantageously be on both sides, but also on one side of the segments 42; 43.1, 43.2 are attached.
  • the pressure medium or pressure oil that builds up in the pressure chamber can enter the gap more quickly, i.e. into the gap or compensation space formed by 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.
  • bevels 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 segment spring groove 51.1 up to the stop pocket or up to the stop 54.1 on the segment carrier 42 and / or over the entire stop surface 55.1 up to the free surface 67.1 be arranged. Pressure medium or pressure oil can then flow directly or immediately into the gap or compensation space 75.1, 75.2 via these chamfers 65.1, 65.2. Alternatively or additionally, as shown, these chamfers 65.5, 65.6 can be attached to the ring gear segments 43.1, 43.2. Control grooves 65.3, 65.4 on the outer circumference of the pinion segment 42 and / or on the inner circumference of the ring gear segments can also perform the same tasks.
  • the filler piece 41 is supported by means of 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 circular cylindrical guide area 69.1, 69.2 which spans an outside diameter.
  • the guide length is preferably 1.5 x the outer diameter of the guide area 69.1, 69.2.
  • the retaining pins or bolts 45.1, 45.2 can be made from sintered material, preferably from sintered iron, with a corresponding strength.
  • the inner diameter of the bores 68.1, 68.2 of the housing parts 25.1, 25.2 is a few micrometers larger than the outer diameter of the guide area 69.1, 69.2 of the retaining pins or bolts 45.1, 45.2. This results in a clearance fit.
  • the retaining pins or bolts 45.1, 45.2 can rotate during operation of the internal gear machine 21 and the contact surfaces 71.1, 71.2, preferably enclosing an angle 70 of 24 °, can be in a position for the sealing function of the segments 42; 43.1, 43.2 turn 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 loads and changes in the direction of rotation and dynamic changes between motor and pump operation. For reasons of cost, this wear protection is achieved by surface hardening, such as nitriding or carbonitriding with the appropriate choice of material.
  • the respective retaining pin or bolt 45.1, 45.2 has a circular-cylindrical shoulder 76.1, 76.2 on its side facing away from the V-shaped contact surfaces 71.1, 71.2.
  • the shoulder 76.1, 76.2 has a significantly smaller outer diameter compared to the guide area 69.1, 69.2.
  • the end face 77.1, 77.2 of the paragraph 76.1, 76.2 is at the bottom of the hole 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 relevant 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 base 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 in principle have an axial play, but must also or even not collide with the teeth 28, 31 of the pinion 26 or the ring gear 30. Open spaces are also appropriate for this purpose.
  • 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 radii 83 on the groove base 79.1, 79.2 of the grooves 80.1, 80.2 of the pinion segment 42 intended for support on the retaining pin or bolt 45.1, 45.2
  • These radii 81, 83 reduce at the segments 42; which are preferably made of special brass or sintered material. 43.1, 43.2 the notch stress without impairing the mobility of the segments 42; 43.1, 43.2 is restricted by clamping.
  • control grooves 63.1.1, 63.1.2 made in the respective axial disk 58.1, 58.2; 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 with a triangular V-shaped cross-section, preferably with a V angle of 60 °, and an angle of inclination, preferably in the range of 4 °, optimized so that in interaction with the location 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 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 axial sealing disk 58.1, 58.2 and are thus acted upon directly with pressure medium or with pressure oil during operation of the internal gear machine 21.
  • one-sided solutions are also conceivable in which the cross-sections are adapted accordingly.
  • the retention of the segments 42; 43.1, 43.2 is due to 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 protrusion of the retaining pin 45.1, 45.2 the pinion segment 42 also reaches radially outward.
  • the position of the segments 42; 43.1, 43.2 given form-fitting.
  • 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 parts 86.1, 86.2 of the respective retaining pin 45.1, 45.2, also referred to as retaining bodies.
  • the game must correspond to the gear tolerances of the housing parts 25.1, 25.2, segments 42; 43.1, 43.2, bearing bushings as well as the deformation under load and taking into account the thermal expansion of the components in the temperature range of the application:
  • a clearance between 0.05 to 0.1 x module of the displacement teeth has been found to be advantageous. This prevents the toothing from jamming by the wedge-shaped segments 42; 43.1, 43.2 prevented even with depressurized operation.
  • the axial compensation which is preferably bilateral, is also built up by intrinsic pressure.
  • the axial compensation is constructed symmetrically to a plane of symmetry 87 containing the axes of rotation of pinion 26 and ring gear 30 via axial pressure fields 61.1, 61.2 controlled axial plates 58.1, 58.2.
  • This plane of symmetry 87 runs, viewed in a cross section perpendicular to the axial direction 39 or perpendicular to the axes of rotation 34.2, 36 of pinion 26 and ring gear 30, through the center point 88 of the axis of rotation 34.2 of the pinion 26 and through the center point 89 of the axis of rotation 36 of the Ring gear 30.
  • the axial pressure fields 61.1, 61.2 are preferably sealed by axial seals 90 with support rings 91 (see FIG Figures 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""inside” towards the pressure field. This necessary "edge” would make the manufacture of the housing or cover parts more difficult.
  • 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 completely mechanically processed, but can be produced by the casting process, for example in the case of die-cast parts or other cast parts.
  • the support ring 91 also has the advantage that it prevents a gap extrusion of the axial seal 90 into the gap between the axial plate 58.1, 58.2 and the 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 in the hydraulic-mechanical efficiency and would therefore worsen the energy efficiency of the motor-pump unit.
  • the hydraulic machine could fail due to seal failure or due to increased wear of the running surfaces of the axial disk on the gear side.
  • the "inward" support effect of the support rings 91 is significantly improved by one or more webs 92.
  • the arrangement of these webs 92 must be selected so that the oil flow, in particular to the axial pressure outlet, or the oil flow from the inlet, is not impaired.
  • the web 92 is in exactly the same position as a web 93.1, 93.2, which is arranged in the kidney-shaped pressure kidney 62.1, 62.2 of the respective axial disk 58.1, 58.2.
  • the axial compensation is optimally matched by the measures described below.
  • An exact adaptation of the axial compensation is achieved through a computational and empirical determination and definition of the relief diameter of pinion 26 and ring gear 30.
  • the or each axial disk 58.1, 58.2 preferably has two openings 94.1, 95.1; 94.2, 95.2. Through these openings 94.1, 95.1; 94.2, 95.2, the pressure medium flows from the inlet side to the kidney pressure 62.1, 62.2 and vice versa from the kidney pressure 62.1, 62.2 via the pressure fields 61.1, 61.2 to the pressure outlet.
  • the respective web 93.1, 93.2 is located approximately at the level of the center of the pinion and has a cross-section which is thus is dimensioned that about 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, is included.
  • Transition radii at the openings reduce the notch stress and thus increase the permissible operating pressures or increase the service life of the hydraulic machine 21.
  • the or each axial disk 58.1, 58.2 is usually made of brass or aluminum, but can also be produced by a sintering process or by metal injection molding (MIM technology ) must be made. To reduce the friction, a corresponding friction-minimized coating is advantageously applied.
  • the radial expansion 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 as well as through the V-shaped open surface 85 and on the tooth engagement 33 through the seal along the line of engagement.
  • the respective axial plate 58.1, 58.2 is fixed on the one hand by protruding the bearing bushes supporting the shaft 23 on the inner diameter and on the through hole holding pins or bolts 45.1, 45.2 on the outer circumference of the respective holding pin or bolts 45.1, 45.2. In the axial direction 39, the respective axial plate 58.1, 58.2 can move freely within the intended axial play.
  • the leakage oil created via the axial washer or plate 58.1, 58.2 and the leakage oil above the sealing roller 49.1, 49.2 collects in the area of the V-shaped open surface 85 and in the annular space created by the chamfer 96 of the respective axial sealing washer 58.1, 58.2 on the ring gear 30 and in the annular space 101.1, 101.2, also referred to as a leakage channel, which is formed with the bevel 97 of the respective axial sealing disk 58.1, 58.2 on the pinion 26. Via a hole 98 as well as through a groove 99 in the connecting space 106 this leakage oil is partially conducted.
  • a leakage shaft channel 23 also referred to as a leakage shaft channel 23 (see Figures 2 , 11 and 12 ).
  • the bore 98 and / or the groove 99 could also be omitted. In this last-mentioned case, all of the leakage oil would flow into the leakage shaft channel 102 via the radial bores 100.1, 100.2 of the shaft 23.
  • the “can space” 107 denotes that space which, viewed in the radial direction 109, is located inside or inside the sealing or can 110 and which is delimited radially outward by the sealing or can 110. Even better heat dissipation could be achieved by taking the above measures. At the same time, even better lubrication of the motor bearing 111 could be achieved. As a result, an even longer service life or an even longer, trouble-free operation of the motor-pump unit 20 could be achieved overall.
  • a vent screw 103 is fitted in the pump cover 25.1 for filling and venting the complete hydraulic system.
  • the relief bore 102 is closed in the area of the radial ball bearing 111 arranged in the motor flange 25.4 by a bearing fastening or sensor screw 112 made of a non-magnetic material, also referred to as closure means, and opens into a radially attached bore 113 Annular space 114 designated connecting space.
  • the magnetic coupling is ruled out for reasons of space and cost.
  • a special motor 22 with a “can” 110 also referred to as a sealing tube, was developed.
  • the term “can” stems from the fact that this tube 110 is arranged between the rotor 22.1 and the stator 22.2.
  • the sealing or can 110 consists of a non-magnetic material, preferably a high-temperature-resistant, pressure-resistant, fiber-reinforced plastic.
  • the sealing tube 110 extends almost over the entire length of the stator core and is cast with plastic to form a unit with the stator 22.2 including the winding and motor housing 25.3.
  • O-rings received in the O-ring grooves 116, 119 assume the sealing function, that is to say seal the can space 107 on both sides of the rotor 22.1 at least leakage fluid-tight.
  • the common motor-pump shaft 23 carries the pressed-on rotor 22.1, contains pressure equalization bores and the bearing fastening or sensor screw 107 to accommodate a speed sensor 120.
  • the motor-pump shaft 23 is only on the motor side or in the radial ball bearing 111 and on the pump side or in at least one slide bearing, preferably on or in two slide bearings 121.1, 121.2.
  • the pinion 26 of the pump or hydraulic machine 21 is supported by a clearance fit on the pump motor shaft 23 and is driven in rotation by the slightly spherical key 37.
  • the inner ring 122.1 of the ball bearing 111 is firmly connected to the motor-pump shaft 23 by the bearing fastening and sensor screw 112.
  • the outer ring 122.2 of the ball bearing 111 is screwed with the bearing fastening screw 117 to the electronics-side bearing cover or housing part 25.4.
  • the bearing cover 25.4 has a specially stepped blind bore 123 into which the bearing fastening and 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 area of the sensor 120.
  • the wall thickness is preferably approximately 2 mm.
  • the electronic circuit board On the side of the bearing cover or housing part 25.4 facing away from the motor 22, the electronic circuit board is in a housing part in the form of a flange 25.5 124 of the speed sensor 120 and at a certain axial distance therefrom a circuit board 125 of the motor controller fitted on both sides, here the output stage 126. A controller board is arranged on this output stage 126.
  • the phase lines 127 (see Figure 1 ) of the motor 22 preferably lead through bores in the housing part or bearing cover 25.4 and are screwed, plugged or soldered onto the output stage 126. Sensor lines of temperature sensors which measure the winding temperatures of the motor 22 are similarly arranged.
  • the motor / pump unit 20 is connected via a power connector 128 and a small signal connector 129.
  • the two connectors 128, 129 are attached to the electronics box 130 in a sealing manner.
  • the electronics box 130 is formed with a tubular housing part 25.6 and with a housing part 25.7 designed as a cover and with the tubular housing part 25.4, also referred to as a bearing cover or motor flange.
  • the electronics box 130 with cooling fins 131 is also screwed on. Sealing elements are also arranged between the individual elements of the electronics box 130.
  • the output stage 126 is mounted on a mounting bracket 132, preferably made of copper, with thermal paste. As a result, the heat generated by the components is conducted through the copper angle 132 into the cooling fins 131 of the tubular housing part 25.6 of the electronics box 130.
  • the cover 25.6 of the electronics box 130 and the tubular motor housing 25.3 are also provided with cooling fins 131.
  • the intermediate housing of the hydraulic machine also represents the bearing cover 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 essentially fluidly connected to the interior of the sealing or can 110.
  • an electric motor 22 in the form of a brushless DC motor (EC motor) has proven to be particularly advantageous, in particular for the application or use of the motor-pump unit 20 for controlling or operating a highly dynamic hydraulic axis.
  • the rotor 22.1 of the electric motor 22 comprises a plurality of recesses 133.1, 133.2, 133.3, 133.4, 133.5, also referred to as leakage rotor channels. These are preferably arranged offset from one another at the same circumferential angles around the rotor axis of rotation 33.1 or around the shaft axis of rotation 35. In the exemplary 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 at the same circumferential angles around the rotor axis of rotation 34.1 or around the shaft axis of rotation 35.
  • ten magnets 134 are provided.
  • the magnets 134 are provided with a tubular bandage 135 on their outer surface pointing radially outward from the rotor axis of rotation 34.1 or from the shaft axis of rotation 35. This bandage 135 delimits the rotor 22.1 radially outward on its outer circumference.
  • the rotor 22.1 is rotatably supported relative to the stator 22.2 in a cylindrical receiving space 136 of the stator 22.2.
  • the can 110 also referred to as a sealing tube, is arranged, which is firmly connected to the stator 22.2.
  • a narrow annular gap 137 which is also referred to as leakage gap channel 137, is formed between the sealing tube or can 110 and the rotor 22.1 is.
  • This annular channel 137 extends in the axial direction 39, preferably essentially 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 as well as several 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 at the other end to the outer tube 139 .
  • twelve webs 140 are preferably provided (see Figure 14 ). How out Figure 12 As can be seen, the webs 140 at their radially outer ends have 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 that is or are slightly smaller than the axial length of the rotor 22.1.
  • the stator 22.2 is made from several stator laminations.
  • a receiving space 142 is formed between adjacent webs 140 of webs 140, the inner tube 138 and the outer tube 139 of the stator 22.2.
  • twelve receiving spaces 142 are preferably provided corresponding to the number of webs 140.
  • Each receiving space 140 serves to receive stator windings made of metal wires, which form the phase lines 127.
  • 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 firmly connected to the motor housing 25.3.
  • the at least one leakage channel 101.1, 101.2 which is fluidly connected to the working chamber 24, preferably designed as an annular space, through which the internal gear pump 21 runs under pressure during operation Leakage oil arising from the axial and radial sealing surfaces is diverted.
  • the at least one leakage channel 101.1, 101.2 serves to divert a leakage that forms during operation of the internal gear machine 21, in particular in the case of radial and / or axial gap sealing 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 fluid.
  • each axial sealing plate 58.1, 58.2 which is open in the axial direction 39 to the working chamber 24 and which is open in the radial direction 109 to the shaft 23 (see FIG Figures 2 , 4th and 11 ).
  • the shaft 23 extends with one shaft end 23.1 of its two shaft ends 23.1, 23.2 away from the pinion 26 in the axial direction 39 through the rotor 22.1 carried by the shaft 23.
  • the connection channels 105.1, 105.2 arranged in the housing part 25.1 of the housing 25 are fluidly connected to the check valves 143.1, 143.2 arranged in the housing 25 or in a housing part 25.2 of the housing 25 that delimits the working chamber 24 of the internal gear machine 21, with 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 that extends away from the pinion 26.
  • the leakage channel loop 108 has the extending in the axial direction 39 in the shaft 23 or through the shaft 23, Leakage shaft channel 102, also referred to as a relief bore, and at least one leakage rotor channel 133.1, 133.2, 133.3 which is fluidly connected to the leakage shaft channel 102 and extends in the axial direction 39 through the rotor 22.1 at a radial distance from the leakage shaft channel 102, 133.4, 133.5 of the rotor 22.1 and the leakage gap channel 137 which is also fluidly connected to the leakage shaft channel 102 and is formed between the rotor 22.1 and the stator 22.2 and which extends in the axial direction 39 when viewed in the radial direction 109.
  • the check valves 143.1, 143.2 open in a fluid flow direction from the leakage channel loop 108 to the respectively active low-pressure area of the working chamber 24 and block in an opposite direction or in an opposite fluid flow direction from the respectively active high-pressure area of the working chamber 24 to the leakage channel loop 108
  • the internal gear pump 21 achieves 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 assigned to the respectively active low-pressure region, that is, apart from a leakage flow component that is small compared to the total leakage flow.
  • a leakage shaft channel 102 extending in the axial direction 39 is arranged, which is fluidly connected to the at least leakage channel 101.1, 101.2, and that in the rotor 22.1 at least one , preferably at a radial distance, in particular parallel, to the leakage shaft channel 102, in the axial direction 39 through the rotor 22.1 extending leakage rotor channel 133.1, 133.2, 133.3, 133.4, 133.5 is arranged, which is fluidly connected to the leakage shaft channel 102 and / or that one, viewed in the radial direction 109, formed between the rotor 22.1 and the stator 22.2 and 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 an in the housing 25 or
  • the Figure 12 shows a longitudinal section through the gear machine 21 in the area of two arranged check valves 143.1, 143.2.
  • the check valves 143.1, 143.2 which are also referred to as shuttle valves, have the task of always connecting the can space 107 with the working connections or To connect connection channels 105.1 and 105.2 in such a way that the lowest possible pressure prevails in the can space 107.
  • the motor-pump unit 20 described is preferably used in a closed hydraulic system, not shown in the figures. In addition to a double or single-acting hydraulic cylinder, this hydraulic system can also contain a pressure accumulator, preferably designed as a diaphragm pressure accumulator, which can or compensates for volume changes due to different piston areas and temperature fluctuations.
  • the pressure accumulator ensures a certain system or preload pressure.
  • the system or preload pressure is preferably in the range from 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 up to 250 bar or more.
  • the shuttle valves 143.1, 143.2 now have the task of ensuring that only the lower pressure prevails in the region of the can space 107.
  • the changeover valves 143.1, 143.2 are each located in one in the respective pressure field 61.1, 61.2, for example here the housing part 25.2 (see Figures 7 and 13th ), located, preferably formed as a blind hole, also designated as a channel part of a return flow channel 154.1, 154.2 axial bore 145.1, 145.2 (see Figures 12 and 13 ).
  • an inclined bore 146.1, 146.2 of the respective return flow channel 154.1, 154.2 connects the bottom of the bore of the respective axial bore 145.1, 145.2 with the can space 107 via the connecting space 106 (see Figures 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 blocking element and with a spring 148, by means of which the ball 147 moves into its sealing or blocking position is biased.
  • the ball 147 and the spring 148 are mounted in a guide element 149.
  • the guide element 149 is pressed into the respective axial bore 145.1, 145.2 and secured with a locking sleeve.
  • a higher pressure now arises in one of the pressure fields 61.1, 61.2. This closes the sealing or blocking element (ball) 147 of one of the shuttle valves 143.1, 143.2 assigned to this pressure field 61.1, 61.2.
  • leakage oil arises in the internal gear pump 21, which is preferably axially and radially compensated, along the axial and radial sealing surfaces.
  • This leakage oil collects in open spaces 85 and annular spaces 96, 101.1, 101.2, in particular in the axial disks 58.1, 58.2 (see Figure 4 ).
  • the leakage oil flows into the axial relief bore 102 in the pump shaft 23, also referred to as the leakage shaft channel, and from there in turn via the radial bore 113 and the recesses 133.1, 133.2, 133.3, 133.4, 133.5 in the rotor 22.1, also known as leakage rotor channels or via the annular gap, also referred to as leakage gap channel 137, between the rotor 22.1 and the stator 22.1, specifically between the bandage 135 of the rotor 22.1 and the gap tube 110, also known as the sealing tube and firmly connected to the stator 22.2, back into the connecting space 106 .
  • this annular gap or leakage gap channel 137 In view of the preferably very small gap width of this annular gap or leakage gap channel 137 and the large number and also the recesses 133.1, 133.2, 133.3, 133.4, 133.5 of the rotor 22.1, each of which has a comparatively large passage cross-section and also referred to as leakage rotor channels, the largest portion flows or a substantial portion of the total leakage oil through the leakage rotor ducts 133.1, 133.2, 133.3, 133.4, 133.5 back into the connection space 106. This creates a slight overpressure in the connection space 106, which ultimately, depending on the direction of rotation 104.1, 104.2, the shuttle valve 143.1, 143.2 opens in the lower pressure loaded pressure field 61.1, 61.2.
  • the open shuttle valve 143.1, 143.2 thus establishes a connection between the inlet side, that is to say the system or preload pressure, and the can space 107.
  • 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, the frictional heat is transported away and the service life is thus significantly increased.
  • the radial bore 113 opens on the ball bearing side, viewed from the pinion 26, in front of the ball bearing 111, but is connected to the bearing gap 155 formed between the inner ring 122.1 and the outer ring 122.2 of the ball bearing 111 fluid-connected (see Figures 11 and 12 ), so that both sufficient lubrication and a cooling effect are achieved and frictional heat is removed.
  • An improvement in the bearing lubrication could be achieved by an axial bore, not shown in the figures, and an additional radial bore, also not shown in the figures, in the bearing fastening or sensor screw.
  • These additional bores can be made in the motor-pump shaft 23 in addition to the radial bore 113 arranged in front of the bearing 111 or in front of the bearing fastening or sensor screw 112, viewed from the pinion 26, or alternatively, i.e. instead. In this way, an advantageous forced lubrication of the bearing 111 can be achieved.
  • a one-piece or 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 take place through a spline, for example with a head or foot centering, in order to fix the two shafts.
  • the two shafts could also be fixed using an additional fit between the motor and pump shaft.
  • both the motor shaft and the pump shaft would then 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 fastening and sensor screw 112 is preferably made of a non-magnetic material in order not to influence the magnetic signals of the sensor 120.
  • the sensor 120 is fastened, preferably glued in, in an axial bore 150 of the bearing fastening and sensor screw 112.
  • the outer diameter of the bearing fastening and sensor screw 112 is greater than the inner diameter of the ball bearing 111 or its inner ring 122.1. This results in an axial fixation of the ball bearing 111 or the motor-pump shaft 23 on the ball bearing 111.
  • the sensor screw 112 is offset at its outer diameter and encloses 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 approximately 2 mm.
  • This advantageous embodiment of the housing or cover part 25.4 enables the motor-pump unit 20 to be loaded with a high system pressure, preferably up to 200 bar.
  • the small remaining 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 is only slightly larger than the outer diameter of the tubular part 151 of the bearing mounting and sensor screw 112.

Claims (12)

  1. Ensemble moteur-pompe avec un boîtier (25) en plusieurs parties, qui comprend une machine à roues dentées intérieures (21) pour un fonctionnement réversible et un moteur électrique (22), qui est couplé à la machine à roues dentées intérieures (21) par l'intermédiaire d'au moins un arbre (23) monté de manière à pouvoir tourner autour d'un axe de rotation d'arbre (35) dans le boîtier (25), dans lequel la machine à roues dentées intérieures (21) comprend un compartiment de travail (24), qui est délimité par au moins deux parties de boîtier (25.1, 25.2) du boîtier (25) et dans lequel sont disposés un pignon (26) à denture extérieure présentant des dents de pignon (28) et une couronne (30) à denture intérieure présentant des dents de couronne (31), montée de manière excentrée par rapport au pignon (26), dans lequel les dents de couronne (31) s'engagent dans une zone de prise de dent (33) avec les dents de pignon (28), et dans lequel est réalisé, entre le pignon (26) et la couronne (30), un espace libre (40) en forme de croissant, dans lequel est disposée une pièce de remplissage (41) en plusieurs parties, qui comprend plusieurs segments d'étanchéité radiaux (42 ; 43.1 ; 43.2) mobiles les uns par rapport aux autres dans la direction radiale, servant à l'étanchéification radiale d'une zone à haute pression (44.1, 44.2) du compartiment de travail (24), dont un premier segment d'étanchéité radial forme un segment de pignon (42) reposant au niveau des dents de pignon (28) et dont un deuxième segment d'étanchéité radial forme un segment de couronne reposant au niveau des dents de couronne (31), et dans lequel une fente radiale (75.1, 75.2) est réalisée entre une face intérieure (72), pointant radialement vers l'extérieur en direction du segment de couronne, du segment de pignon (42) et une face intérieure (73.1, 73.2), faisant face à celle-ci, pointant radialement vers l'intérieur en direction du segment de pignon (42), du segment de couronne, et dans lequel au moins une plaque d'étanchéité axiale (58.1, 58.2) servant à l'étanchéification axiale de la zone haute pression (44.1, 44.2) du compartiment de travail (24) est disposée entre des faces frontales (56.1, 57.1 ; 56.2, 57.2) axiales des roues dentées (26, 30) et au moins une des parties de boîtier (25.1, 25.2), caractérisé en ce que l'au moins une plaque d'étanchéité axiale (58.1, 58.2) présente au moins un renfoncement de plaques d'étanchéité ouvert en direction des faces frontales (56.1, 57,1 ; 56.2, 57.2) des roues dentées (26, 30) sous la forme d'un canal de commande de plaques d'étanchéité (63.3.1, 63.3.2) pouvant être soumises à l'action d'un moyen de pression, qui part d'un évidement de plaques d'étanchéité (62.1, 62.2), est ouvert en direction de la fente radiale (75.1, 75.2) et fait face directement à la fente radiale (75.1, 75.2), dans lequel deux rainures de commande (63.1.1, 63.2.1 ; 63.2.1, 63.2.2) débouchent dans l'évidement de plaques de d'étanchéité (62.1, 62.2), qui sont ouvertes en direction des faces frontales (56.1, 56.2 ; 57.1, 57.2), dans lequel une première des rainures de commande (63.1.1, 63.1.2) est disposée de manière à faire face directement à des interstices de dent de pignon (29), qui sont réalisés entre les dents de pignon (28), et une deuxième des rainures de commande (63.2.1, 63.2.2) est disposée de manière à faire face directement à des interstices de dent de couronne (32), qui sont réalisés entre les dents de couronne (31).
  2. Ensemble moteur-pompe selon la revendication 1, caractérisé en ce que le segment de pignon (42) et/ou le segment de couronne (43.1, 43.2) présente ou présentent au moins un renfoncement de segment d'étanchéité radial sous la forme d'un canal de commande de segment d'étanchéité radial (65) s'étendant dans une direction périphérique autour de l'axe de rotation de pignon (34.2) ou autour de l'axe de rotation de couronne (36), pouvant être soumis à l'action d'un moyen de pression ou du moyen de pression, qui est ouvert en direction de la fente radiale (75.1, 75.2) et qui débouche directement dans la fente radiale (75.1, 75.2).
  3. Ensemble moteur-pompe selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal de commande de plaques d'étanchéité (63.3.1, 63.3.2) est réalisé en tant qu'une rainure de commande de plaques d'étanchéité.
  4. Ensemble moteur-pompe selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal de commande de plaques d'étanchéité (63.3.1, 63.3.2) présente, observé dans une section transversale s'étendant de manière parallèle par rapport à la direction axiale (39), une section transversale en forme de V.
  5. Ensemble moteur-pompe selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal de commande de plaques d'étanchéité (63.3.1, 63.3.2) s'étend le long de l'entaille radiale (75.1, 75.2).
  6. Ensemble moteur-pompe selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal de commande de plaques d'étanchéité (63.3.1, 63.3.2) s'étend dans la direction périphérique.
  7. Ensemble moteur-pompe selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal de commande de plaques d'étanchéité (63.3.1, 63.3.2) présente une longueur de canal de commande, sur laquelle il est ouvert en direction de l'entaille radiale (75.1, 75.2) et fait face directement à l'entaille radiale (75.1, 75.2) sur la totalité de sa longueur de canal de commande.
  8. Ensemble moteur-pompe selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal de commande de plaques d'étanchéité (63.3.1, 63.3.2) débouche dans un évidement de plaques d'étanchéité (62.1, 62.2), disposé sensiblement dans la zone haute pression (44.1, 44.2), pouvant être soumis à l'action de moyens de pression, de la plaque d'étanchéité axiale (58.1, 58.2), qui est ouvert en direction des faces frontales (56.1, 57.1 ; 56.2, 57.2) axiales des roues dentées (26, 30) et qui fait face directement à celles-ci.
  9. Ensemble moteur-pompe selon la revendication 8, caractérisé en ce que le canal de commande de plaques d'étanchéité (63.3.1, 63.3.2) s'étend le long de l'entaille radiale (75.1, 75.2) en partant de l'évidement de plaques d'étanchéité (62.1, 62.2).
  10. Ensemble moteur-pompe selon la revendication 8 ou 9, caractérisé en ce que le canal de commande de plaques d'étanchéité (63.3.1, 63.3.2) s'étend en partant de l'évidement de plaques d'étanchéité (62.1, 62.2) soit le long de l'entaille radiale (75.1, 75.2) jusque dans une zone, laquelle fait directement face à la rainure de ressort de segment (51.1, 51.2) soit s'étend le long de l'entaille radiale et de la rainure de ressort de segment, en faisant face directement à la rainure de ressort de segment, jusque dans une zone, qui soit est disposée entre la rainure de ressort de segment et la rainure de rouleau d'étanchéité soit qui va jusqu'à la rainure de rouleau d'étanchéité ou fait face directement à la rainure de rouleau d'étanchéité.
  11. Ensemble moteur-pompe selon l'une quelconque des revendications précédentes, caractérisé en ce que le segment de pignon (42) et/ou le segment de couronne (43.1, 43.2) sont montés contre un déplacement en direction d'une zone de basse pression du compartiment de travail (24) au moyen d'au moins une tige de maintien (45.1, 45.2), qui est montée de manière à pouvoir tourner dans une partie de boîtier (25.1, 25.2) faisant face aux faces frontales (56.1, 57.1 ; 56.2, 57.2) axiales des roues dentées (26, 30), dans lequel la tige de maintien (45.1, 45.2) présente au niveau de son extrémité associée vers la pièce de remplissage (41), un corps de maintien (86.1, 86.2), qui présente, observé dans une section transversale de manière perpendiculaire par rapport à la direction axiale (39), une section transversale en forme de V ou trapézoïdale et comprend des faces d'appui de corps de maintien (71.1, 71.2), qui forment un angle aigu (70), et dans lequel le segment de pignon (42) et/ou le segment de couronne présente au moins un évidement de segment d'étanchéité (80.1, 80.2) servant à recevoir le corps de maintien (86.1, 86.2) de l'au moins une tige de maintien (45.1, 45.2), qui présente, observé dans une section transversale de manière perpendiculaire par rapport à la direction axiale (39), également une section transversale en forme de V ou une section transversale trapézoïdale et comprend des faces d'appui de segment d'étanchéité (71.3, 71.4), qui forment également un angle aigu (70.1), et dans lequel à la fois les faces d'appui de corps de maintien (71.1, 71.2) et les faces d'appui de segment d'étanchéité (71.3, 71.4) s'étendent en forme de coin en direction d'un centre vers le pignon (26), et dans lequel l'au moins une tige de maintien (45.1, 45.2) vient en prise par son corps de maintien (86.1, 86.2) avec l'au moins un évidement de segment d'étanchéité (80.1, 80.2).
  12. Ensemble moteur-pompe selon l'une quelconque des revendications précédentes, caractérisé en ce que la pièce de remplissage (41) et/ou l'au moins une plaque d'étanchéité axiale (58.1, 58.2) est ou sont configurées de manière symétrique par rapport à un plan de symétrie (87) imaginaire contenant l'axe de rotation de pignon (34.2) et l'axe de rotation de couronne (36).
EP15158368.9A 2014-03-21 2015-03-10 Unité pompes-moteur Active EP2921703B1 (fr)

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DE102014103958A1 (de) 2015-09-24
US20150267701A1 (en) 2015-09-24
US9945377B2 (en) 2018-04-17
EP2921703A3 (fr) 2015-11-04
EP2921703A2 (fr) 2015-09-23

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