EP3276127A1 - Machine hydraulique à roue dentée - Google Patents

Machine hydraulique à roue dentée Download PDF

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Publication number
EP3276127A1
EP3276127A1 EP17182228.1A EP17182228A EP3276127A1 EP 3276127 A1 EP3276127 A1 EP 3276127A1 EP 17182228 A EP17182228 A EP 17182228A EP 3276127 A1 EP3276127 A1 EP 3276127A1
Authority
EP
European Patent Office
Prior art keywords
sealing
gear
seal
fluid machine
leg
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
EP17182228.1A
Other languages
German (de)
English (en)
Other versions
EP3276127B1 (fr
Inventor
Reinhard Pippes
Artur Bohr
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 Technologies GmbH
Original Assignee
Eckerle Technologies GmbH
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Filing date
Publication date
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Publication of EP3276127A1 publication Critical patent/EP3276127A1/fr
Application granted granted Critical
Publication of EP3276127B1 publication Critical patent/EP3276127B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/18—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/08—Axially-movable sealings for working fluids
    • F01C19/085—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or engines, e.g. gear machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • 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
    • 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
    • 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
    • F04C18/12—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 other than internal-axis type
    • F04C18/14—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 other than internal-axis type with toothed rotary pistons
    • F04C18/18—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 other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/101—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with a crescent-shaped filler element, located between the inner and outer intermeshing members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—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 one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the invention relates to a gear fluid machine, comprising a machine housing, a first gear and a second gear meshing with the first gear, wherein the first gear and the second gear are each rotatably mounted in the machine housing with respect to a rotation axis and at least partially at least partially with at least one abut axial play in the machine housing arranged axial disc having on its side facing away from the gears a pressure field, which is encompassed by a circumferential seal which rests sealingly on the one hand to a first support surface of the axial disc and on the other hand on a second support surface of the machine housing.
  • the gear fluid machine may be configured, for example, as a gear pump or as a gear motor. Also, an embodiment is possible as an internal gear fluid machine or as an external gear fluid machine, so that the gear fluid machine can be present as an internal gear pump, internal gear motor, external gear pump or external gear motor. In any case, the gear fluid machine has the first gear and the second gear. The two gears mesh with each other, wherein the first gear has a first toothing and the second gear has a second toothing and engage the two gears at least partially in one another. In the following, only the internal gear fluid machine will be discussed purely by way of example. Of course, the embodiments are always readily transferable to the Au . leopardradfluidmaschine.
  • the first gear is designed as a pinion and the first gear as external teeth
  • the second gear is present as a ring gear, which has the second toothing designed as an internal toothing.
  • the pinion is arranged in the ring gear, that the two gears mesh with each other.
  • the pinion is mounted eccentrically with respect to the ring gear. This means that the first gear is rotatably mounted about a first axis of rotation and the second gear about a second axis of rotation, wherein the two axes of rotation are preferably arranged at a distance from each other in parallel. If the gear fluid machine is designed as an external gear fluid machine, then the two gears lie as meshing external teeth before. Also in this case, the two axes of rotation are spaced parallel to each other.
  • the gear wheels are subjected to a rotational movement, whereby a conveying effect is exerted on a fluid present in the gear fluid machine.
  • the gear fluid machine is designed as a motor, then its fluid is supplied, whereby the gears are rotated. On one of the gears a torque is provided so far, which can be tapped.
  • the versions can always be transferred to the engine.
  • the gear fluid machine on the first gear, the second gear and the machine housing As essential components, the gear fluid machine on the first gear, the second gear and the machine housing.
  • the two gears are rotatably mounted in the machine housing, namely around the first axis of rotation and the second axis of rotation.
  • the two axes of rotation are spaced apart, in particular parallel spaced, arranged to each other.
  • the pinion In the case of the internal gear fluid machine, the pinion is disposed in the ring gear and accordingly has an outer diameter which is smaller than an inner diameter of the ring gear. Both the pinion and the ring gear are seen in cross section with respect to the respective axis of rotation substantially round.
  • the outer diameter of the pinion and the inner diameter of the ring gear are selected such that the outer teeth of the pinion seen in the circumferential direction with respect to the second axis of rotation is only in engagement with a portion of the internal teeth of the ring gear.
  • the first gear is arranged for example on a drive shaft of the gear fluid machine, in particular rotatably connected thereto.
  • the first gearwheel can be driven via the drive shaft and set in a rotational movement about the first axis of rotation. Due to the second toothing engaging with the first toothing, the rotational movement of the first toothed wheel is also impressed on the second toothed wheel.
  • the first gear is directly driven by the drive shaft, while the driving of the second gear is provided by the drive shaft only indirectly via the first gear.
  • Both the first toothing and the second toothing each have a plurality of teeth and interdental spaces between the teeth. The conveying effect is achieved in the case of the internal gear pump or the external gear pump by the meshing of the first toothing and the second toothing.
  • the fluid is present in the latter.
  • the fluid is preferably conveyed to a pressure side or into a pressure chamber of the gear fluid machine, namely, starting from a suction side or from a suction chamber.
  • the pressure chamber is formed, for example, in the machine housing of the gear fluid machine. If the gear fluid machine is designed as a gear fluid motor, the fluid flows from the pressure chamber in the direction of the suction side or the suction chamber of the gear fluid machine, whereby the first gear and the second gear are driven.
  • the gear fluid motor represents the kinematic reversal of the gear fluid pump.
  • the at least one axial disc is arranged, which rests at least partially on an end face of the first gear and / or on an end face of the second gear.
  • the axial disc causes a seal, in particular the pressure side opposite the suction side, so that the fluid present in the gear fluid machine can not flow past the first gear or the second gear on the front side.
  • an axial disc is of course arranged on both sides of the first gear and the second gear. In the following, however, only one of these axial discs will always be discussed; However, the statements are always transferable.
  • the axial discs are symmetrical to each other or even exist as equal parts.
  • the axial disc In order to always achieve a reliable seal by means of the axial disc, this is arranged with axial play with respect to the axis of rotation or the axes of rotation in the machine housing.
  • the pressure field is preferably in the form of a depression in the axial disk, which is preferably closed at the edge, that is to say has a peripheral edge.
  • the depression passes through the axial disc in the direction of the gears only partially, so not completely. In this respect, it has a continuous floor.
  • the pressure field or the depression is pressurized with pressurized fluid at least during operation of the gear fluid machine.
  • the fluid is preferably the same which is present in the pressure chamber and / or the suction chamber of the gear fluid machine.
  • the pressure field is fluidically connected to the pressure side of the gear fluid machine, in particular via at least one at least partially or completely formed in the machine housing flow channel.
  • a throttle and / or an orifice may be provided in the flow channel to adjust the desired pressure in the pressure field.
  • the pressure field is encompassed by the circumferential seal, which is arranged on the axial disc.
  • the seal is arranged in a recess of the axial disc and / or a recess of the machine housing stationary.
  • the seal surrounds the pressure field completely and is designed in this respect as a circumferential seal.
  • the seal is - seen in the axial direction - on the one hand on a support surface of the axial disc and on the other hand on a second support surface of the machine housing, wherein the support surfaces are preferably arranged parallel to each other.
  • the axial disc Due to the sealing of the pressure field by means of the seal, the axial disc is urged by the fluid present in the pressure field in the direction of the first gear and / or the second gear, so that the axial disc preferably on the first gear - or the second gear - the front side is applied.
  • an internal gear pump with an axial disc which abuts the lateral boundary of a pump chamber on end faces of a ring gear and a pinion of the internal gear pump and which has a pressure field on a ring facing away from the ring gear and the pinion, which is sealed with a sealing ring, the pressure field encloses.
  • the internal gear pump has a sealing arrangement with the sealing ring, which has the shape of an outline of the pressure field and an L-shaped annular cross-section, and with an elastic ring which rests inside the L-shaped annular cross-section of the sealing ring.
  • the seal is partially considered in section.
  • the section is preferably understood to mean a sealing cross-section which corresponds to a part of a longitudinal section through the seal, the sectional plane of this longitudinal section receiving or at least parallel to the axis of rotation of the first gear and / or the second gear.
  • the sealing cross-section now designates that part of the longitudinal section which is present on one side of an imaginary plane perpendicular to the cutting plane. Because the seal is configured circumferentially, lie in the longitudinal section of two of these areas of the seal. If one speaks of the cut of the seal, then preferably only one of these ranges is meant. If the seal is viewed as a circumferential sealing ring with a continuous, in particular curved and / or annular, longitudinal central axis, then the sealing cross section is present as a cross section through the seal with respect to this longitudinal center axis.
  • the seal is U-shaped and has in so far three legs, namely the first sealing leg, the second sealing leg and the connecting leg.
  • the two sealing legs are seen spaced apart from each other and are joined together by the connecting leg.
  • the two sealing legs and the connecting leg are configured in one piece and / or of the same material. Under the latter is to be understood that the sealing leg and the connecting leg consist of the same material.
  • the seal exclusively on the two sealing legs and the connecting leg, so that the total seal as such consists of only one material, which may also be referred to as a sealing material.
  • the seal has the described shape at least partially, so not necessarily along its entire extent. Preferably, however, the shape is present along the entire extent of the seal.
  • first sealing leg on the first support surface and the second sealing leg on the second support surface Seen in longitudinal section through the gear fluid machine is now the first sealing leg on the first support surface and the second sealing leg on the second support surface. More specifically, the first sealing leg abuts with a first sealing surface on the first support surface and the second sealing leg with a second sealing surface on the second support surface.
  • the two sealing surfaces are preferably arranged in each case on the outside of the seal, in longitudinal section through the gear fluid machine so on opposite Pages of the seal or on opposite sides of the two sealing legs arranged.
  • Such a configuration of the seal allows easy adjustment of a spring rate of the seal, which influences the contact pressure of the seal on the axial disc and on the machine housing.
  • a spring rate of the seal which influences the contact pressure of the seal on the axial disc and on the machine housing.
  • the described embodiment of the seal allows a gear fluid machine, in which the problems mentioned do not occur because the Axialvorbond the seal and thus the contact pressure of the thrust washer to the first gear and / or the second gear, an advantageous course over a spring travel of the seal. This is caused by an advantageous spring characteristic of the seal, ie the course of the spring force caused by the seal over the spring travel.
  • a further embodiment of the invention provides that the seal of the same material of an elastic material, in particular polyurethane, and / or is configured support ringless.
  • the two sealing legs and the connecting leg are preferably made of the same material and, to this extent, have the same material configuration.
  • polyurethane is used as the material.
  • the seal is designed support ringless, so in particular has no Spring ring made of metal or another elastic material. Rather, the seal consists exclusively of the sealing material.
  • the seal can of course be associated with a support ring or have the seal such.
  • the support ring is arranged for example between the first sealing leg and the first support surface and abuts both. Alternatively, it is disposed between the connecting leg and the machine housing and also abuts both.
  • the support ring is preferably made of a different material than the seal, in particular of metal.
  • the seal is attached to the support ring, in particular cohesively.
  • the seal is molded onto the support ring.
  • the seal is seen in section symmetrical with respect to a spaced apart from the sealing legs, in particular centrally, extending through the connecting leg symmetry plane.
  • the plane of symmetry or a symmetry plane lying in the plane of symmetry and the cutting plane is preferably perpendicular to the connecting leg. In this case, it is arranged at a distance from both sealing legs, for example, it is located in the middle between the sealing legs.
  • the seal is now configured identically on both sides of the plane of symmetry or the symmetry, in particular it is symmetrical with respect to the plane of symmetry.
  • a development of the invention provides that the sealing legs seen in section have in the relaxed state of the seal in the direction away from the connecting leg direction away from each other inclined free ends.
  • Under the relaxed state of the seal is an unassembled state of the seal, so for example, one immediately before mounting To understand the seal present Vormontageschreib the seal.
  • This state the seal, for example, after their manufacture until their assembly.
  • a deformation of the seal can take place, by which the desired preload of the seal and corresponding to the desired contact pressure of the axial disc is achieved to the first gear and / or the second gear.
  • This contact pressure is at least present as long as the pressure field is not acted upon by pressurized fluid and is pressureless in this respect.
  • Each of the sealing legs has on its side facing away from the connecting leg on a free end.
  • the free ends or the sealing legs are now inclined away from each other in the direction away from the connecting leg, so that - again seen in section - imaginary extensions of the sealing legs intersect each other at a certain angle.
  • the sealing legs may be angled in their relaxed state with respect to the axis of rotation of the first gear or the second gear, so with this include an angle which is greater than 0 ° and less than 90 °. Due to this configuration of the seal, it is compressed during assembly of the gear fluid machine in the axial direction with respect to the axis of rotation, so the free ends of the sealing legs to move toward each other. As a result, the bias of the seal is adjusted.
  • a particularly preferred development of the invention provides that the connecting leg seen in section, at least on its side facing away from the sealing legs has an extension in the axial direction with respect to one of the axes of rotation, which is smaller than the distance between the first support surface and the second support surface at the Machine housing adjacent thrust washer.
  • the width of the connecting leg is smaller than the distance between the support surfaces, when the axial disc rests against the machine housing, that is to be displaced to this maximum.
  • a further embodiment of the invention can provide that mutually remote sides of the free ends in the relaxed state of the seal have a greater distance from each other than the first support surface and the second support surface, in particular when abutting the machine housing axial disc.
  • the two sealing legs are seen in section over the connecting leg survive. Seen in longitudinal section with respect to the axis of rotation so the distance between the outer and therefore facing away from each other sides of the free ends, which corresponds to the maximum dimensions of the seal in the axial direction in this state, be greater than the distance between the two support surfaces, especially if the axial disc on the Machine housing rests. Accordingly, said distance is greater than the width of the connecting leg.
  • the distance between the opposite sides of the free ends preferably means their greatest distance, this being determined in a plane perpendicular to the plane of symmetry.
  • the distance corresponds, for example, to the distance of the support surfaces when the axial disc resting against the machine housing plus an axial clearance and / or a prestressing projection.
  • the axial play is greater than zero. For example, it is based on the distance between the support surfaces at least 5%, at least 10%, at least 15%, at least 20% or at least 25%.
  • the preload projection is preferably selected such that the axial disc is subjected to a specific bias voltage.
  • each of the sealing legs seen in section on its side facing the other of the sealing leg side of a first imaginary line and on its side facing away from the other of the sealing leg side of a second imaginary straight line wherein the first straight line and the second straight line are angled relative to one another in the relaxed state of the seal.
  • the first straight line defines the sealing surface of the respective sealing leg which bears against the support surface
  • the second straight line defines an inner surface of the respective sealing leg facing away from the sealing surface.
  • the two straight lines each have a non-zero extension, so that the sealing surface and the inner surface are at least partially planar or even.
  • the angle enclosed by the two straight lines is identical for the two sealing legs. However, different angles can be realized from each other.
  • the included angle is for example at least 2.5 °, at least 5 °, at least 7.5 °, at least 10 °, at least 15 ° or at least 20 °.
  • a preferred embodiment of the invention provides that the connecting leg is rectangular in section and has on its side facing away from the sealing legs at least one chamfer or a round edge.
  • the seal is preferably arranged in a recess which is present in the machine housing or the axial disk.
  • the recess has a chamfer or round edge adapted to the chamfer or round edge, wherein the adaptation is preferably provided with regard to the shape and / or the dimensions.
  • the chamfer or edge of the connecting leg rests continuously on the bevel or edge of the recess after assembly of the seal.
  • the connecting leg in the radial direction has an extension which is greater than the extent of the first sealing leg and / or the extension of the second sealing leg in the axial direction.
  • the two sealing legs preferably extend inward in the radial direction, starting from the connecting leg.
  • the section described here can thus be understood as a longitudinal section with respect to the axis of rotation.
  • a material thickness of the connecting leg is greater than a material thickness of the sealing legs, wherein for the two sealing legs preferably the same material thickness is used.
  • the material thickness is in the axial direction for the connecting leg in the radial direction and for the sealing leg.
  • the free ends of the sealing legs seen in section have at least one rounding, which is present between the first imaginary line and the second imaginary line, in particular from the first imaginary straight line to the second imaginary line extends. Seen on average, the free ends are flat, for example, so they are bounded by a straight line.
  • This straight line can now be connected to the first straight line or the second straight line via the at least one rounding so that the rounding extends from the straight line up to the first straight line or the second straight line.
  • such a rounding preferably occurs on both sides of the straight line, so that a first of the curves extends from the straight line up to the first imaginary straight line and a second one of the curves extends from the straight line up to the second imaginary straight line.
  • the two imaginary straight lines only a rounding are connected to each other, so that the rounding of the first imaginary line extends to the second imaginary line.
  • the embodiment described is provided for at least one of the sealing legs, but preferably for both sealing legs.
  • the radius of the rounding can in principle be chosen arbitrarily.
  • the rounding represents a circular arc section, that is, has a continuously constant curvature.
  • the rounding runs at least on one side, but particularly preferably on both sides, tangentially into the first straight line or the second straight line.
  • a further embodiment of the invention provides that the seal has at least one first sealing region and at least one second sealing region, wherein the first sealing region and the second sealing region have different sealing cross sections.
  • the seal is, as already explained above, designed circumferentially. If only exactly one first sealing area and exactly one second sealing area are provided, then they merge into one another on both sides. In other words, the first sealing region merges into the second sealing region both on the one hand and on the other hand, with a first end of the first sealing region merging into a first end of the second sealing region and a second end of the first sealing region merging into a second end of the second sealing region.
  • first sealing regions and second sealing regions there may also be a plurality of first sealing regions and a plurality of second sealing regions.
  • the seal alternately consists of one of the first sealing regions and one of the second sealing regions, so that in this respect first sealing regions and second sealing regions alternate.
  • first sealing region or the first sealing regions respectively and / or overall have a smaller extension than the second sealing region or the second sealing regions.
  • each of the first sealing portions has a smaller extension than each of the second sealing portions.
  • the two sealing regions that is to say the first sealing region and the second sealing region, can have different properties. Preferably, they differ only in terms of their cross-section, so are seen differently in cross-section. Additionally or alternatively, however, they may also differ with respect to the material, in particular consist of different materials.
  • the seal in both the first sealing region and in the second sealing region has the embodiment described above, ie each seen in section U-shaped and has the first sealing leg, the second sealing leg and the connecting leg connecting them.
  • the seal in one of the sealing regions deviates from this shape.
  • the seal in one of the sealing regions seen in section is designed block-like, so that the connecting leg is present only in an imaginary form and together with the sealing legs form a solid block. In this case, the otherwise free ends of the sealing legs are directly connected.
  • the seal is trapezoidal, is seen in section so limited by two opposite parallel lines and two spaced, these lines interconnecting and angled against each other lines.
  • a particularly advantageous embodiment of the invention provides that the distance of the mutually remote sides of the free ends of the sealing legs in the relaxed state of the seal in the first sealing region has a first value and in the second sealing region a second value different from the first value.
  • the cross sections of the seal thus differ between the two sealing regions with respect to the distance that exists in the relaxed state of the seal.
  • the distance In the first sealing region, the distance should have the first value and in the second sealing region the second value.
  • the second value is different from the first value. Most preferably, it is smaller.
  • a further advantageous embodiment of the invention provides that the height of the connecting leg has a first value in the first sealing area and a second value different from the first value in the second sealing area.
  • the height of the connecting leg corresponds to the material thickness of the connecting leg.
  • the height or the material thickness of the connecting leg of the seal should now be different for the two sealing regions.
  • the height of the connecting leg in the first sealing region corresponds to the first value and in the second sealing region to the second value.
  • the second value is different from the first value.
  • the second value is smaller than the first value.
  • first sealing area and the second sealing area are both with respect to the distance of the facing away from each other Differentiate sides of the free ends of the sealing legs in a relaxed state of the seal and in the height of the connecting leg.
  • first value is less than the second value
  • first value is greater than the second value.
  • the values for the distance and the height are chosen such that the same spring rates of the seal or its sealing legs are achieved, which act between the machine housing and the axial disc.
  • a development of the invention provides that the first sealing region and the second sealing region merge into one another via a transition region.
  • the transition region is so far between the first sealing area and the second sealing area.
  • such a transition region is provided for each transition between a first sealing region and a second sealing region or vice versa, so that there is in each case such a transition region between each first sealing region and the second sealing region directly adjacent thereto.
  • the cross sections of the first seal portion and the second seal portion gradually become equal to each other.
  • the distance of the mutually remote sides of the free ends and / or the height of the connecting leg from the first sealing region to the second sealing region change.
  • the first sealing region and the second sealing region directly adjoin one another, ie merge directly into one another or run into one another.
  • first sealing region and the second sealing region are connected to each other via a bend, wherein the bend has a greater curvature than the first sealing region and the second sealing region.
  • this has a curvature value, which may also be zero, so that the seal is straight. The further the curvature value deviates from zero, the more pronounced the curvature.
  • the first sealing area and the second sealing area are now connected to each other via the bend.
  • the bend may coincide with the transition region or the transition region may represent the bend.
  • the bend is characterized by a greater curvature compared to the first seal area and the second seal area, so that the curvature value for the bend is larger in absolute terms is considered as for the first sealing area and the second sealing area, respectively over their entire extent.
  • the first sealing region and the second sealing region at their respective ends adjacent to the bend at an angle to each other, which is preferably at most 135 °, at most 90 ° or at most 45 °, but in any case greater than 0 °.
  • the angle is at least 45 ° and at most 135 °, at least 60 ° and at most 120 °, at least 75 ° and at most 105 ° or approximately or exactly 90 °.
  • the seal runs almost straight in the first sealing region, ie has a comparatively small curvature, in particular in comparison with the second sealing region, which is preferably more curved than the first sealing region.
  • the strongest curvature of the first sealing region is smaller than the strongest curvature of the second sealing region, which in turn is smaller than the strongest curvature of the bend.
  • the FIG. 1 shows a schematic longitudinal sectional view through a gear fluid machine 1, which is designed here, for example, as formerly leopardradfluidpumpe.
  • the gear fluid machine 1 has a pinion gear designed as a first gear 2, designed as a ring gear second gear 3 and a machine housing 4.
  • the first gear 2 has an external toothing, not shown in detail, which meshes with a part of the internal gear teeth of the second gear 3, also not shown in detail.
  • the first gear 2 is rotatably supported with respect to a rotation axis 5, while a rotatable mounting of the second gear 3 is provided about a further rotation axis, not shown here, which is arranged in parallel spaced from the rotation axis 5.
  • the gears 2 and 3 are stored so far eccentric to each other.
  • a filler 6 may be arranged, which is preferably sickle-shaped.
  • the filler 6 may be formed integrally or in several parts.
  • the machine housing 4 can - as shown here - be designed in several parts.
  • the front wheels of the gears 2 and 3 Axialusionn 7 and 8 are arranged.
  • the axial discs 7 and 8 are in front of axially opposite sides of the gears 2 and 3 in front. They are arranged with little play in the axial direction in the machine housing 4.
  • they are rotatably mounted relative to the machine housing 4.
  • the axial disk 7 will be discussed in more detail.
  • the embodiments are analogous to the axial disc 8.
  • the axial disc 7 has on its side facing the machine housing 4 and so far the gears 2 and 3 side facing away from a pressure field 9, which is formed for example in the form of a recess in the axial disc 7.
  • the pressure field 9 can be acted upon by a fluid channel 10, which is formed in the machine housing 4, with pressurized fluid.
  • the pressure field 9 is fluidly connected via the fluid channel 10 with a pressure side of the gear fluid machine 1 not shown here.
  • the pressure field 9 is pressurized via the fluid channel 10 and accordingly urged in the axial direction in the direction of the gears 2 and 3.
  • the pressure field 9 is assigned a seal 11.
  • the seal 11 preferably surrounds the pressure field 9 completely and is insofar annular, although not necessarily circular. Much more The seal 11 may be out of round, that is to say deviate from a circular shape.
  • the pressure field 9 or the corresponding recess is designed approximately kidney-shaped, so that the seal 11 is arranged in kidney shape.
  • the seal 11 is on the one hand on a first support surface 12 of the axial disc 7 and on the other hand on a second support surface 13 of the machine housing 4 sealingly.
  • the seal 11 is made of an elastic material, so that after assembly of the gear fluid machine 11 by means of the seal 11, a bias on the axial disc 7 can be applied, which in turn causes a certain contact force of the axial disc 7 in the axial direction of the gears 2 and 3.
  • FIG. 2 shows a detail of the above-described longitudinal sectional view of the gear fluid machine 1.
  • the machine housing 4 and the axial disc 7 are partially and the seal 11 completely visible.
  • the seal 11 is arranged in a recess 14 of the machine housing 4.
  • the seal 11 bears sealingly against a first sealing surface 15 on the first support surface 12 and with a second sealing surface 16 on the second support surface 13.
  • the first sealing surface 15 is present on a first sealing leg 17, while the second sealing surface 16 is formed on a second sealing leg 18.
  • the two sealing legs 17 and 18 are spaced from each other in the axial direction with respect to the axis of rotation 5 and connected to each other via a connecting leg 19, so that overall the seal 11 is U-shaped in section.
  • the seal 11 is - as indicated by the hatching - in one piece and formed of the same material of a sealing material.
  • a sealing material for example, polyurethane may be used as the sealing material.
  • the seal 11 is designed without support ring, so has no example, metallic support ring.
  • the seal 11 consists exclusively of the sealing material.
  • a support ring may be provided.
  • the connecting leg 19 is seen in section substantially rectangular and has on its sides facing away from the sealing legs 17 and 18 sides round edges 20. One of the round edges 20 abuts a corresponding round edge 21 of the recess 14.
  • the recess 14 in the radial direction with respect to the axis of rotation 5 has larger dimensions than the seal 11. Due to the design of the seal 11 as a circumferential seal this has an inherent spring force, which is directed to an increase in the radial direction, so the seal 11 or its connecting leg 19 is always urged against a recess 14 in the radial direction outwardly limiting step 22.
  • the recess 14 is delimited by a web 23 which separates the recess 14 from the fluid channel 10.
  • the web 23 is optional and can be omitted accordingly.
  • the seal 11 seen in section is designed symmetrically with respect to a plane of symmetry 24, wherein the plane of symmetry 24 is preferably perpendicular to the axis of rotation 5 and is arranged centrally between the sealing legs 17 and 18. In other words, the plane of symmetry 24 is perpendicular to a longitudinal central axis 25 of the connecting leg 19.
  • FIG. 3 shows a section of the seal 11 in a first embodiment, wherein the seal 11 in unassembled state, ie in particular in a pre-assembly state, is present. Accordingly, the seal 11 is relaxed, so that due to their spring action, the sealing legs 17 and 18 on their side facing away from the connecting leg 19 from each other in the axial direction, so that increases their distance in this direction with increasing distance from the connecting legs 19.
  • the symmetry plane 24 and the longitudinal central axis 25 are also indicated in turn.
  • a respective longitudinal central axis 26 or 27 is likewise indicated.
  • an imaginary logical separation between the sealing legs 17 and 18 on the one hand and the connecting leg 19 on the other hand is shown.
  • the connecting leg 19 constitutes a type of main body of the seal 11, from which the sealing legs 17 and 18 extend and, viewed in longitudinal section with respect to the axis of rotation 5, extend in the radial direction, for example inwards.
  • Each of the sealing legs 17 and 18 has on its side facing away from the connecting leg 19 via a free end 28 and 29, respectively.
  • the seal 11 has seen in the sealing cross-section on a maximum width B, namely on its side facing away from the connecting leg 19.
  • the maximum width B corresponds to the extent of the maximum distance of the sealing legs 17 and 18 and the maximum distance of the sealing surfaces 15 and 16.
  • the connecting leg 19, however, has a width b, which may be defined, for example, as average width or width in the region of its longitudinal central axis 25.
  • the width b is smaller than the width B.
  • the width b of the connecting leg 19 is preferably less than or equal to a width of the recess 14, in which the seal 11 is arranged.
  • a reverse embodiment, as described above is of course possible. In this case, the width b is greater than the width of the recess 14 or greater than the extent thereof in the axial direction with respect to the axis of rotation. 5
  • the sealing legs 17 and 18 are each delimited by a flat surface defined by a straight line 30 or 31.
  • the straight line 30 is connected on the one hand via a rounding 32 to the first sealing surface 15 or a straight line defining it, while on the other hand is connected via a rounding 33 to an inner surface 34 of the first sealing leg 17 or a straight line defining it.
  • Each of the sealing legs is seen in section on its side facing the other of the sealing legs 18 and 17 facing side of the respective inner surface 34 and 37 and on the other side of the sealing legs 18 and 17 facing away from the respective sealing surface 15 and 16 respectively.
  • the inner surface 37 is defined by a first straight line 38 and the sealing surface 16 by a second straight line 39.
  • the two lines 38 and 39 and thus extensions of the sealing surface 16 and the inner surface 37 are angled against each other, so cut each other at an angle ⁇ .
  • the angle ⁇ can basically be chosen arbitrarily. For example, it is at least 2.5 °, at least 5 °, at least 7.5 ° or at least 10 °.
  • the seal 11 is configured such that the two straight lines 38 and 39 or the sealing surface 16 and the inner surface 37 are angled in the relaxed state of the seal 11 against each other, but after mounting the seal 11 in the gear fluid machine 1 include a smaller angle or parallel are arranged to each other.
  • the seal 11 has a height H.
  • This is composed of a height h 1 of the connecting leg 19 and a height h 2 of the sealing legs 17 and 18.
  • the height h 1 simultaneously corresponds to a material thickness s 1 of the connecting leg 19, ie in particular its extension in the plane of symmetry 24 in section. It can be clearly seen that the height h 2 is greater than the height h 1 , for example, the height h 2 by at least 25%, at least 50%, at least 75% or at least 100% greater than the height h 1 .
  • the material thickness s 1 of the connecting leg 19 is greater than a material thickness s 2 of the sealing legs 17 and 18.
  • the extent is of the connecting leg 19 in the radial direction with respect to the axis of rotation 5 is greater than the extension of the sealing legs 17 and 18 in the axial direction.
  • the material thickness s 1 is at least 5%, at least 10%, at least 15%, at least 20% or at least 25% greater than the material thickness s 2 .
  • the ratio between the height H and the width b and / or the width B is selected such that a demolding of the seal 11 without movable mold elements is possible.
  • FIG. 4 shows a section through a second embodiment of the seal 11.
  • the above statements with respect to the first embodiment is fully incorporated and reference is made only to the differences. These are that the free ends 28 and 29 of the sealing legs 17 and 18 are not limited by straight lines 30 and 31, but rather that the free ends 28 and 29 have continuous curves 40 and 41.
  • Each of the curves 40 and 41 starts from the respective sealing surface 15 or 16 and extends up to the respective inner surface 34 and 37, respectively.
  • the curves 40 and 41 are configured, for example, as circular segments and dimensioned such that they, on the one hand, enter the sealing surface 15 or 16 and on the other hand enter into the inner surface 34 and 37 tangentially.
  • FIG. 5 shows a schematic representation of the seal 11, wherein it is clear that this has at least a first sealing portion 42 and a second sealing portion 43, in the embodiment shown here, two first sealing portions 42 and two second sealing portions 43.
  • the sealing portions 42 and 43 differ in particular their curvature.
  • the first sealing region 42 is less curved than the second sealing region 43. If only one of the first sealing regions 42 and / or one of the second sealing regions 43 is discussed in the context of this description, the embodiments are preferably always analogous to each of the first sealing regions 42 and / or each of the second sealing regions 43.
  • the first sealing region 42 merges via a transition region 44 into the second sealing region 43.
  • a transition region 44 is provided in each case between each of the first sealing regions 42 and the second sealing regions 43 adjacent thereto.
  • the seal 11 has a bend 45.
  • the bend 45 a greater curvature is realized in comparison with the first sealing region 42 and the second sealing region 43.
  • the curvature of the seal 11 in the bend 45 is stronger than over the entire first sealing region 42 and / or the entire second sealing region 43 away.
  • the curvature of the second sealing region 43 is continuously stronger across it than in the first sealing region 42.
  • the first sealing region 42 extends at least in regions or even continuously straight.
  • the first sealing region 42 differs from the second sealing region 43, in particular with regard to the sealing cross section.
  • the transition region 44 can therefore be designed such that a smooth transition of the two sealing regions 42 and 43 is realized in one another, so there is no abrupt change in the sealing cross-section.
  • FIG. 6 shows a section through the seal 11 in the first sealing region 42, indicated in the FIG. 5 drawn by the cutting mark A.
  • FIG. 7 shows a sectional view of the seal 11 in the second sealing region 43, wherein the corresponding point in the FIG. 5 indicated by the cutting mark B. Again, the height h 1 of the connecting leg 19 and the width B are shown. It is clear that the seal 11 in the second sealing region 43 preferably has a greater width B than in the first sealing region 42. Conversely, the height h 1 for the second sealing region 43 is smaller than for the first sealing region 42.
  • the height h 1 has a first value in the first sealing region 42 and a second value in the second sealing region 43, the second value being smaller than the first value.
  • the width of the seal 11 in the first sealing region 42 has a first value and in the second sealing region 43 has a second value, wherein the second value is greater than the first value.
  • the height h 1 in the first sealing region 42 relative to the height h 1 in the second sealing region 43 is at least 101%, at least 102%, at least 103%, at least 104% or at least 105%.
  • said ratio may also be greater and be at least 110%, at least 120%, at least 130%, at least 140% or at least 150%.
  • the width B is in the first sealing area 42 in the second sealing region 43, preferably at most 90%, at most 80%, at most 75%, at most 70%, at most 60% or at most 60% or at most 50%.
  • the values for the distance B and the height h 1 are chosen such that the sealing elements 42 and 43 have the same spring action of the seal 11 in the direction of their width B, ie with the seal 11 mounted between the machine housing 4 and the axial disk 7 or 8 results.
  • FIG. 8 shows a schematic sectional view of an alternative embodiment of the first sealing portion 42.
  • the connecting leg 19 possibly exists in an imaginary form and the two sealing legs 17 and 18 are connected to each other over the entire height H of the seal 11, so they do not unconnected free ends exhibit.
  • the height h 2 of the sealing legs 17 and 18 preferably corresponds to the total height H.
  • the embodiment described may alternatively also be provided in the second sealing area 43. It is important, however, that in at least one of the sealing regions 42 and 43 the initially described form of the seal 11 is present, namely with sealing legs 17 and 18, which are connected to each other by the connecting leg 19 and each having a free end facing away from the connecting leg 19 Side have.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rotary Pumps (AREA)
  • Sealing Devices (AREA)
EP17182228.1A 2016-07-26 2017-07-19 Machine hydraulique à roue dentée Active EP3276127B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102016213696.8A DE102016213696B4 (de) 2016-07-26 2016-07-26 Zahnradfluidmaschine

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EP3276127A1 true EP3276127A1 (fr) 2018-01-31
EP3276127B1 EP3276127B1 (fr) 2020-12-23

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EP (1) EP3276127B1 (fr)
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DE102020133200A1 (de) * 2020-12-11 2022-06-15 Schwäbische Hüttenwerke Automotive GmbH Sickendichtung

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EP0512514A2 (fr) * 1991-05-07 1992-11-11 SAUER-SUNDSTRAND S.p.A. Machine à engrenages
US6171089B1 (en) * 1998-05-12 2001-01-09 Parker-Hannifin Corporation External gear pump with drive gear seal

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US3097893A (en) * 1955-11-04 1963-07-16 Charles S White Sealing and bearing device having low friction sealing faces
DE1225454B (de) 1963-12-20 1966-09-22 Nsu Motorenwerke Ag Dichtsystem fuer Rotationskolbenmaschinen
FR2069498A5 (fr) * 1969-11-17 1971-09-03 Burkert Christian
US3895890A (en) 1974-01-24 1975-07-22 Hydroperfect Int Geared hydraulic apparatus
DE3716605A1 (de) 1987-05-18 1988-12-08 Bosch Gmbh Robert Zahnradmaschine (pumpe oder motor)
ES2061870T3 (es) 1989-10-06 1994-12-16 Sauer Sundstrand Spa Maquina de engranajes para utilizar como bomba o motor.
JPH0741905Y2 (ja) 1990-02-16 1995-09-27 株式会社小松製作所 ギヤポンプのシール装置
DE4322239C2 (de) * 1993-07-03 1997-04-24 Eckerle Rexroth Gmbh Co Kg Innenzahnradmaschine (Pumpe oder Motor)
US6484687B1 (en) * 2001-05-07 2002-11-26 Saddle Rock Technologies Llc Rotary machine and thermal cycle
DE10061885A1 (de) * 2000-12-12 2002-07-04 Testo Gmbh & Co Kg Dichtvorrichtung
DE10213928A1 (de) * 2002-03-28 2003-10-09 Rheinmetall W & M Gmbh Mörserrohr
DE102012213771A1 (de) 2012-08-03 2014-02-06 Robert Bosch Gmbh Innenzahnradpumpe

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DE7500496U (de) * 1975-01-10 1976-07-22 Robert Bosch Gmbh, 7000 Stuttgart Ahnradmaschine (pumpe oder motor)
EP0512514A2 (fr) * 1991-05-07 1992-11-11 SAUER-SUNDSTRAND S.p.A. Machine à engrenages
US6171089B1 (en) * 1998-05-12 2001-01-09 Parker-Hannifin Corporation External gear pump with drive gear seal

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US10634136B2 (en) 2020-04-28
CN107654260B (zh) 2020-06-05
EP3276127B1 (fr) 2020-12-23
US20180030982A1 (en) 2018-02-01
DE102016213696A1 (de) 2018-02-01
CN107654260A (zh) 2018-02-02
DE102016213696B4 (de) 2020-06-04

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