EP3211230A1 - Machine à piston axial, en particulier pompe à pistons axiaux - Google Patents

Machine à piston axial, en particulier pompe à pistons axiaux Download PDF

Info

Publication number
EP3211230A1
EP3211230A1 EP16201457.5A EP16201457A EP3211230A1 EP 3211230 A1 EP3211230 A1 EP 3211230A1 EP 16201457 A EP16201457 A EP 16201457A EP 3211230 A1 EP3211230 A1 EP 3211230A1
Authority
EP
European Patent Office
Prior art keywords
engine
drive shaft
axial piston
retaining pin
retraction ball
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.)
Withdrawn
Application number
EP16201457.5A
Other languages
German (de)
English (en)
Inventor
Van No Lanevongsa
Didier Angeloz
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.)
Liebherr Machines Bulle SA
Original Assignee
Liebherr Machines Bulle SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Liebherr Machines Bulle SA filed Critical Liebherr Machines Bulle SA
Publication of EP3211230A1 publication Critical patent/EP3211230A1/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • 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
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0668—Swash or actuated plate
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate

Definitions

  • the present invention relates to an axial piston machine, in particular an axial piston pump.
  • a typical embodiment of an axial piston machine is an axial piston pump.
  • This is an energy converter that receives mechanical power through its drive shaft and delivers hydraulic power by sucking oil on the low pressure side of an oil circuit and using the mechanical power - minus existing efficiency losses, such as friction, slugging losses, or the like - to build up compression power, which is fed into the high pressure side of an oil circuit to then supply these to one or more consumers of hydraulic power.
  • an axial piston pump has a plurality of drum turret-like pistons, which are rotatable about a rotation axis. To suck in hydraulic fluid from the low pressure side, the pistons perform during half a revolution parallel to the rotation axis lifting movement, whereas they perform the other half revolution of a full rotation about the rotation axis a lowering movement to supply the sucked hydraulic fluid to the high pressure side.
  • pivoting cradle also referred to as a swashplate
  • the piston carrying out the lifting movement is constantly aligned parallel to it in a rotation about the axis of rotation and is pulled or urged by means of a sliding shoe, which is articulated to the piston, to the movement predetermined by the pivoting cradle and the return plate.
  • the pivoting cradle does not rotate with the piston, so that the sliding shoes fastened to the piston execute a sliding movement on the surface of the pivoting cradle facing the sliding shoes.
  • Too much pressing increases the frictional force there, resulting in increased wear and lower energy efficiency. Too little pressing, in turn, causes the running surfaces of the Do not rest flat shoes on the swashplate. This causes one-sided wear on the shoes, whereby the wear of both the shoes and the swash plate increases massively.
  • an elastic support of the retraction ball on the engine cylinder drum Such a disclosure is for example in the DE 10 2008 009 815 A1 shown. As envisioned therein, an elastic support can be achieved by using a multi-tooth clutch. Alternatively, the prior art proposes a central spring (cf. DE 10 2010 055 657 A1 ).
  • a so-called multi-tooth clutch which surrounds the drive shaft in the circumferential direction and generates a torsionally rigid connection with this.
  • the multi-tooth clutch on its inner circumference on an internal toothing, which is in engagement with an external toothing of the drive shaft.
  • a plurality of spring elements is provided, which is aligned in the longitudinal direction of the drive shaft. In this case, the plurality of springs are inserted into recesses, which face with their respective opening of the drive shaft.
  • the recesses are typically arranged rotationally symmetrical to the axis of rotation of the drive shaft. Due to the assembly of numerous comparatively small springs to be used in the multi-tooth clutch, this is very expensive. Already inserted in their mounting position springs tend to fall back. In addition, there is a risk of losing such feathers.
  • each of the individual spring elements inserted in the retraction ball is held in place with an additional fixing element. When using such elements suitable for fixing the springs, although falling out of springs during disassembly / assembly can be avoided, however, the elements for fixing the springs must additionally be mounted.
  • a central spring is used instead of a multi-tooth clutch.
  • the restoring force of a single central spring is transmitted via retaining pins on the retraction ball.
  • the retaining pins run through the opening of the engine, through which the engine itself is guided and give the force of the arranged inside the engine spring.
  • teeth are removed on the internal teeth of the engine, which generates a torsionally rigid connection with the drive shaft, so that at these positions - with a drive shaft used - face each two gear grooves of the inner and associated outer teeth.
  • holding pins are used, which are supported on the engine-facing side of the retraction ball and forward the spring force to the retraction ball.
  • a disadvantage of this embodiment is that individual teeth must be milled out of the internal teeth of the engine. This is associated with a great deal of effort, since the internal teeth of the engine made of hardened material and the milling out of these teeth thus requires a very specific and very hard milling head.
  • the retraction ball itself consists of a very high quality material, which is due to the fact that the rotary connection between retraction ball and drive shaft is realized via a gear connection of an internal toothing of the retraction ball and an external toothing of the drive shaft.
  • the transmission of the torques occurring here via the internal toothing of the retraction ball places high material requirements on the retraction ball itself and requires the production of a solid material, preferably steel.
  • the invention describes an axial piston machine, in particular an axial piston pump, comprising: a drive shaft, an engine rotatably connected to a drive shaft and surrounds them in the circumferential direction, at least one engine piston, which is reciprocably received in a respective cylinder bore of the engine , a swash plate for pressing the engine piston into the cylinder bore when rotating the engine about the axis of rotation of the drive shaft, a return plate for extracting the engine piston from the cylinder bore when rotating the engine about the axis of rotation of the drive shaft, a retraction ball for Urging the return plate in the direction of the swash plate, a spring element for applying a spring force, and at least one retaining pin which transmits the spring force to the retraction ball, wherein the at least one retaining pin for passing the spring force to the retraction ball passes through a respective bore extending through the engine.
  • the engine has an engine recess for performing the drive shaft.
  • Engine recesses and the hole for a respective retaining pin are different openings.
  • the prior art milling step for milling one or more internal gear teeth of the engine can be skipped.
  • a retaining pin has a hole associated with the retaining pin.
  • Another advantage of the invention is that the assembly is considerably simplified compared to the prior art. By inserting the retaining pins in each associated hole a reliable assembly step is given, which can be easily reworked. Furthermore, it is possible to carry out the torsionally rigid connection generated via the internal teeth of the engine with the external teeth of the drive shaft less massive than that embodiment of the prior art, in which one or more teeth are milled out for performing the retaining pin. Because of the higher number of teeth is namely a less massive / less strong interlocking tooth connection possible with a constant maximum torque.
  • the respective bore is matched to the outer contour of the at least one retaining pin, preferably, the respective bore has a shape corresponding to the outer contour of the at least one retaining pin.
  • the bore can therefore also be circular.
  • the cross section of the retaining pin hexagonal so preferably the cross section of the bore is also hexagonal.
  • the inner diameter of the bore corresponds approximately or exactly to the outer diameter of the retaining pin.
  • the shape obtained in the cross section of the retaining pin is not limited to a circle or a hexagon. Other geometric shapes such as a quadrilateral, an ellipse, a pentagon or the like are also included within the scope of the invention.
  • the respective bore is radially spaced from the recess for passing the drive shaft. It is preferably provided that the bore extends parallel to the recess of the drive shaft.
  • the cross-sectional plane spanned transversely to the longitudinal direction of the drive shaft accordingly shows a bore which is radially spaced from the recess for passing through the drive shaft and which is designed to carry out a retaining pin.
  • the bore and the recess for carrying out the drive shaft are mutually independent openings of the engine.
  • the respective bore of the at least one retaining pin extends parallel or substantially parallel to the axial direction of the drive shaft.
  • the axial piston machine comprises a plurality of retaining pins with a respective bore, wherein the holes along a circle whose center is located in the axis of rotation of the drive shaft, are arranged.
  • the axis of rotation of the engine is identical to the axis of rotation of the drive shaft.
  • the plurality of holes in this case are equidistant from each other.
  • the retraction ball surrounds the drive shaft in its circumferential direction in a portion adjacent to the engine. In the radial direction, starting from the drive shaft to the retraction ball, preferably no further component is present. The same can apply to the drive shaft and the surrounding engine.
  • the at least one retaining pin is in contact with the retraction ball to cooperate therewith and to produce a rotationally fixed connection between the at least one retaining pin and the retraction ball upon rotation of the at least one retaining pin about the axis of rotation of the drive shaft.
  • the rotational connection of drive shaft and retraction ball is namely passed through the engine to the arranged in the at least one bore of the engine retaining pin and from this to the retreat ball.
  • the provision of an internal toothing on the retraction ball or an external toothing of the drive shaft engaging therein is no longer necessary. This simplifies the manufacture of both the drive shaft and the retraction ball and contributes to an overall less complex structure of an axial piston machine.
  • the end face of the at least one retaining pin engages on one of the drive shaft facing side of the retraction ball, so that a friction between the end face of the at least one retaining pin and the retraction ball is formed.
  • the resulting friction is according to a variant of the invention so high that a torsionally rigid connection between the at least one retaining pin and the retraction ball is formed and the internal teeth of the retraction ball or the external teeth of the drive shaft can be omitted.
  • the at least one retaining pin engages in a respective recess in the retraction ball.
  • the recess is preferably formed so that it receives the protruding from the engine end of the at least one retaining pin. It can be provided for each retaining pin its own depression in the retraction ball.
  • the at least one retaining pin is pressed into a part in a recess of the retraction ball or shed with a protruding from the engine section with the retreat ball.
  • a torque connection between retraction ball and drive shaft takes place only via the at least one retaining pin and its associated bore through the engine.
  • a torsionally rigid connection between the retaining pin and retraction ball is provided.
  • the synchronous rotation of the retraction ball with the drive shaft is then via the torque path of drive shaft, toothing of the Drive shaft and engine, attacking the bore on the retaining pin inserted in the bore and the interaction of retaining pin and retraction ball ensured.
  • the retraction ball is made of plastic. So far, a production of retraction ball made of plastic was not possible because the direct connection of the retraction ball with the drive shaft, which has typically been implemented via an internal toothing on the retraction ball and engaging in the internal teeth external teeth of the drive shaft, a production of plastic did not allow. The internal toothing is in this case exposed to such great forces that a production of these made of plastic was out of the question. Due to the predictable torque path in the invention, a production of plastic is possible.
  • the spring element is a spiral spring, preferably a spiral spring, which cooperates with a drive shaft surrounding the drive shaft in the circumferential direction, acts on the side facing away from the coil spring side of the at least one retaining pin.
  • the coil spring may be one whose winding extends around the drive shaft.
  • the axial piston machine according to the invention further comprises a sliding block, which is connected to the protruding from the cylinder bore end of the engine piston and clamped between a swash plate and return plate, wherein preferably the swash plate and the return plate are aligned substantially parallel to each other.
  • Fig. 1 shows an axial longitudinal section with an identification of relevant to the understanding of the invention components.
  • the drive shaft 1 is with the so-called engine 2, which is a cylinder drum, in the drum turret several with hydraulic piston 3 (called engine piston 3) stocked cylinder bores 4 (called engine cylinder bores 4) incorporated are connected.
  • engine piston 3 hydraulic piston 3
  • engine cylinder bores 4 engine cylinder bores 4
  • each engine piston 3 In order for the said energy conversion can take place, a corresponding coordinated axial movement of each engine piston 3 must take place in the course of the rotation of the engine 2, so that it moves out of its engine cylinder bore 4 (until reaching an end position) as long as the corresponding cylinder with the Oil low-pressure side is connected and the engine piston 3 is then pressed back into the engine cylinder bore 4 when it is connected to the high-pressure oil side.
  • the high pressure or the low pressure via the so-called control plate, which is itself rotatably mounted and in the over the orbit of the engine cylinder bore 4 each over the angular range tuned holes are present, so that in the course of the rotation of the engine 2, the currently required connection between each respective Engine cylinder bore 4 and the two extreme oil pressure levels of the main oil circuit, d. H. the high pressure or the low pressure is present.
  • the amount of torque that can be absorbed by an axial piston pump in order to be able to deliver hydraulic power in conjunction with its rotational speed is determined by the stroke length traveled by the engine piston 3 per full revolution of the drive shaft 1.
  • the stroke length is defined by the oblique angle of the swashplate 5 (also called swivel cradle), which can be defined by means of an adjusting device when the hydraulic pump is operating and can be changed continuously.
  • the idling mode of the axial piston pump ie in the already mentioned zero position is an oblique angle of 0 ° before.
  • the axial Line of symmetry of the drive shaft 1 exactly perpendicular to the plane spanned by the support surface of the swash plate 5 level.
  • the swash plate 5 is fixed so that it does not participate in the rotational movement of the engine 2.
  • the drum pistons 3 arranged in drum turrets hold contact with the running surface of the swashplate 5 via the sliding shoes 14 fastened to them by the hydraulic cylinders 3 by means of a retraction mechanism over the retraction plate 6 rotating with the engine Applying contact pressure.
  • the engine 2 and the connecting plate 110 must be pressed against one another and at the same time the return plate 6 must be pressed in the direction of the swash plate 5 via the so-called retraction ball 7.
  • the pressing of the return plate 6 in the direction of the swash plate 5 takes place via the retraction ball 7.
  • This has a plurality of spring elements 8, which bear against an end face of the engine 2 and urge the retraction ball 7 in the direction of the swash plate 5.
  • Fig. 2 shows an enlarged view of an usual embodiment for the prior art.
  • the drive shaft 1 which is rotatable about its axis of rotation Rx.
  • the drive shaft 1 has an outer toothing 101, which is in engagement with a corresponding internal toothing of the engine 2 and with a corresponding internal toothing of the retraction ball 7.
  • Axialverschiebritt the retraction ball parallel to the axis of rotation is exerted by the plurality of spring elements 8.
  • the with the retraction ball 7 in an operative connection withdrawal plate 6 is then pushed away correspondingly less of the engine 2.
  • the Figures 3 and 4 show a likewise known from the prior art other implementation.
  • the drive shaft 1 has an axis of rotation Rx and has on its outer circumference an external toothing 101. With this external toothing it is in engagement with an internal toothing of the engine 2 and with an internal toothing 72 of the retraction ball 7.
  • the displaceable along the axial direction of the drive shaft 1 retraction ball is with Help a spring element 8 and a retaining pin 9 pushed away from the engine 2.
  • the arrangement positions of the plurality of retaining pins 9 is made Fig. 4 refer to.
  • Fig. 4 is a view of an interior of a Axialmaschinengephaseuses facing side of an engine. 2
  • Fig. 5 shows a first embodiment of the present invention.
  • the drive shaft 1 with its axis of rotation Rx has an outer toothing 101 extending in the circumferential direction of the drive shaft 1. This is only in engagement with a correspondingly formed internal toothing 11 of the engine 2.
  • a spring element 8 is provided in the form of a spiral spring whose winding extends around the drive shaft , This acts on the drive shaft 1 in its circumferential direction surrounding washer 13, which passes on the spring force on a retaining pin 9.
  • the retaining pin 9 is guided through a bore 10 and protrudes from the engine 2 on a side remote from the spring element of the engine 2.
  • the remote from the spring element 8 end of the retaining pin 9 stands with the retraction ball 7 in contact.
  • the in Fig. 5 is shown, the protruding from the engine 2 end of the retaining pin 9 is inserted into a recess 71 of the retraction ball 7.
  • the retraction ball 7 has no internal toothing, so that rotation of the drive shaft 1 is not transmitted directly to the retraction ball 7. This is done according to the invention via the engagement portion of the drive shaft 1 with the engine 2 via the external teeth 101 and the associated internal toothing 11 of the engine.
  • the retaining pins 9 are arranged with the retraction ball 7 such that upon rotation of the retaining pins 9 about the rotation axis Rx, a corresponding rotation of the retraction ball 7 takes place.
  • the recesses 71 are preferably adapted to the shape or contour of the retaining pins 9.
  • the outgoing of the spring 8 force is transmitted to the retraction ball 7 via at least one retaining pin, preferably via at least two retaining pins.
  • the retaining pins can be uniformly distributed over the circumference, parallel to the drive shaft 1 and performed by the engine 2 by means of holes 10. It is possible that the bores 10 for passing the retaining pins 9 lie on a circle concentric with the engine axis Rx. In addition, the holes can be arranged equidistant from each other.
  • the recess 71 in the retraction ball 7 is also a bore.
  • the remote from the spring 8 end of the retaining pin 9 is locked accordingly in the retraction ball 7 and in the recess 71 of the retraction ball 7.
  • the other end meets a washer 13, on which a pressure is exerted by the spring 8.
  • Fig. 7 shows a further embodiment of the present invention. Equipped with the same reference numerals correspond to the previously defined components and are therefore not reintroduced. It should only be noted again that the retraction ball 7 has no internal teeth, which is directly connected to the drive shaft 1 in connection.
  • This in Fig. 7 illustrated embodiment shows a retaining pin whose outstanding from the engine 2 end is poured into a retraction ball 7.
  • a retaining pin offers the design of the retraction ball 7 made of plastic.
  • the retraction ball 7 facing the end of the retaining pin 9 have a closing element, which has a greater thickness in its cross section than the other components of the retaining pin 9. When pouring the retaining pin 9 in the retraction ball 7 increases the connection strength.
  • Fig. 8 shows a third embodiment of the present invention.
  • the end face of the protruding from the engine 2 retaining pins 9 is on the side facing the retraction ball 7 with the retraction ball 7 in contact.
  • the respective contact surfaces together have such a friction that a rotation of the engine 2 about the rotation axis Rx of the drive shaft 1 leads to a synchronous rotation of the retraction ball 7. This is achieved by the friction of the end face 91 on the abutting surface of the retraction ball. 7
  • Fig. 9 shows a view of an engine 2 of the present invention. It can be seen from the recess 12 for performing the drive shaft 1 radially spaced holes 10 which are arranged on a circle whose center is the axis of rotation Rx of the drive shaft and the engine 2.
  • the bores 10 are radially spaced from the recess 12 for performing the drive shaft 1, so that a guided by the holes 10 retaining pins 9 high torque can be transmitted can.
  • the holes 10 can be arranged equidistant from each other.
  • the retaining pins 9 of the present invention are preferably incorporated in precisely fitting holes 10, which allow a backlash-free or almost backlash-free torque transmission. This is advantageous because the moments of inertia are not insignificant with respect to the pin attachment or pin bearing. Speeds of such engines are typically well above 1000 1 / min to 1500 1 / min. The material of the engines is also relatively heavy. Switching consumers off and on results in rapid load jumps, which lead to corresponding rapid speed changes. Therefore, a non-accurate fit for the at least one retaining pin at sudden load changes would lead to very high peak torques on the retaining pins, whereby their fatigue strength is reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
EP16201457.5A 2016-02-25 2016-11-30 Machine à piston axial, en particulier pompe à pistons axiaux Withdrawn EP3211230A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH00262/16A CH712152A1 (de) 2016-02-25 2016-02-25 Axialkolbenmaschine, insbesondere Axialkolbenpumpe.

Publications (1)

Publication Number Publication Date
EP3211230A1 true EP3211230A1 (fr) 2017-08-30

Family

ID=57442573

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16201457.5A Withdrawn EP3211230A1 (fr) 2016-02-25 2016-11-30 Machine à piston axial, en particulier pompe à pistons axiaux

Country Status (2)

Country Link
EP (1) EP3211230A1 (fr)
CH (1) CH712152A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108916037B (zh) * 2018-10-23 2019-02-19 江苏恒立液压科技有限公司 具有斜盘座定位装置的液压柱塞泵

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3743125A1 (de) * 1987-12-18 1989-07-06 Brueninghaus Hydraulik Gmbh Axialkolbenpumpe
DE19706263C1 (de) 1997-02-18 1998-07-23 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit drehzahlabhängiger Anpressung der Zylindertrommel
DE10312242B3 (de) * 2003-03-19 2004-12-02 Brueninghaus Hydromatik Gmbh Druckstift und Axialkolbenmaschinen mit diesem Druckstift
DE102008009815A1 (de) 2008-02-19 2009-08-20 Robert Bosch Gmbh Rückzugkugel für eine hydrostatische Kolbenmaschine
DE102010055657A1 (de) 2010-12-22 2012-06-28 Robert Bosch Gmbh Axialkolbenmaschine
DE102012014538A1 (de) * 2012-07-21 2014-01-23 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine und Rückzugplatte

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1945434A1 (de) * 1969-09-08 1971-03-11 Linde Ag Axialkolbenmaschine
US7546797B2 (en) * 2006-04-21 2009-06-16 Sauer-Danfoss, Inc. One piece slipper holddown device
DE102013101986B4 (de) * 2013-02-28 2023-06-22 Linde Hydraulics Gmbh & Co. Kg Hydrostatisches Axialkolbentriebwerk in Schrägscheibenbauweise mit drei unterschiedlichen Federeinrichtungen zur Anpressung der Zylindertrommel an die Steuerfläche und zur kraftschlüssigen Niederhaltung der Triebwerkskolben an der Schrägscheibe

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3743125A1 (de) * 1987-12-18 1989-07-06 Brueninghaus Hydraulik Gmbh Axialkolbenpumpe
DE19706263C1 (de) 1997-02-18 1998-07-23 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit drehzahlabhängiger Anpressung der Zylindertrommel
DE10312242B3 (de) * 2003-03-19 2004-12-02 Brueninghaus Hydromatik Gmbh Druckstift und Axialkolbenmaschinen mit diesem Druckstift
DE102008009815A1 (de) 2008-02-19 2009-08-20 Robert Bosch Gmbh Rückzugkugel für eine hydrostatische Kolbenmaschine
DE102010055657A1 (de) 2010-12-22 2012-06-28 Robert Bosch Gmbh Axialkolbenmaschine
DE102012014538A1 (de) * 2012-07-21 2014-01-23 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine und Rückzugplatte

Also Published As

Publication number Publication date
CH712152A1 (de) 2017-08-31

Similar Documents

Publication Publication Date Title
DE3621187C2 (fr)
WO2007118624A1 (fr) Machine a piston hydrostatique avec disque de commande rotatif
EP2464894B1 (fr) Vis à billes comprenant des repères pour la butée et procédé de montage pour une telle vis à billes
WO2014187518A1 (fr) Dispositifs d'articulation
DE102009036884A1 (de) Kugelgewindetrieb, mit axial abgestützter Gewindespindel
DE3909910C2 (fr)
DE102008046821B4 (de) Kurbelwelle für eine Brennkraftmaschine mit varibaler Verdichtung und Brennkraftmaschine mit variabler Verdichtung
EP3208164A1 (fr) Vis d'entrainement a bille
DE602005006042T2 (de) Vorrichtung zur Umwandlung einer rotierenden Bewegung in eine lineare Bewegung.
EP3211230A1 (fr) Machine à piston axial, en particulier pompe à pistons axiaux
DE102017107613A1 (de) Reibflächenkupplung und Nebenaggregat eines Kraftfahrzeugs
DE3322881A1 (de) Zahnrad-schaltvorrichtung
DE112018002225B4 (de) Linearer aktuator und kupplungsaktuator
EP3339602B1 (fr) Bielle pour un moteur à combustion interne à compression variable
DE2658612A1 (de) Einrichtung zur metallbearbeitung durch walzen
DE3109622A1 (de) Servolenkvorrichtung fuer kraftfahrzeuge
EP3042104B1 (fr) Transmission à variation continue
DE102014114146A1 (de) Kurbeltrieb
EP4204717B1 (fr) Transmission coaxiale
EP2848806B1 (fr) Machine à piston axial hydrostatique dans une construction à axe oblique dotée d'un joint homocinétique destiné à l'entraînement d'un tambour cylindrique
DE2705331A1 (de) Keilwelle
DE2017861A1 (de) Einrichtung zur Verhinderung von totem Spiel bzw. Lose bei Getriebeanordnungen
DE2152096A1 (de) Hydraulische Maschine
EP3211229A1 (fr) Machine à piston axial, en particulier pompe à pistons axiaux
EP2835531A2 (fr) Machine à piston axial hydrostatique dans une construction à axe oblique

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20180301