EP2179175A1 - Machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage - Google Patents

Machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage

Info

Publication number
EP2179175A1
EP2179175A1 EP08801631A EP08801631A EP2179175A1 EP 2179175 A1 EP2179175 A1 EP 2179175A1 EP 08801631 A EP08801631 A EP 08801631A EP 08801631 A EP08801631 A EP 08801631A EP 2179175 A1 EP2179175 A1 EP 2179175A1
Authority
EP
European Patent Office
Prior art keywords
piston
support ring
actuating
counter
swash plate
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
EP08801631A
Other languages
German (de)
English (en)
Other versions
EP2179175B1 (fr
Inventor
Herbert Dreher
Clemens Krebs
Timo Nafz
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2179175A1 publication Critical patent/EP2179175A1/fr
Application granted granted Critical
Publication of EP2179175B1 publication Critical patent/EP2179175B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04B1/26—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
    • 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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1204—Position of a rotating inclined plate
    • F04B2201/12041—Angular position
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1205—Position of a non-rotating inclined plate
    • F04B2201/12051—Angular position

Definitions

  • the invention relates to an axial piston machine in swash plate design with an adjusting device.
  • Axial piston machines have a plurality of pistons, which are arranged longitudinally displaceably in a rotatably mounted cylinder drum.
  • the pistons are supported on a swashplate or pivoting cradle whose angle of inclination is adjustable relative to the axis of rotation of the cylindrical drum. Depending on the angle of inclination, the displacement changes.
  • This adjusting device may for example consist of a control piston for changing the inclination angle in a first direction and an opposed piston for changing the inclination angle of the swash plate in the opposite direction.
  • the adjusting piston and / or the counter-piston are usually (in each case) acted upon by the force of a spring.
  • the swash plate is in the end position of the axial piston machine.
  • This rest position for example, in a two-way adjustable axial piston machine be a neutral position, in which thus a zero stroke of the piston occurs during rotation of the cylinder drum.
  • the return springs are usually arranged in a one-sided limited by the control piston or piston, pressurizable volume and thus act on the front side of the control piston or opposed piston.
  • the adjusting piston and the counter-piston are integrated into the axial piston machine, this results in an increase in the overall length of the entire machine.
  • Axial piston machine in swash plate design with an adjusting device to create in which the available space is used to advantage and can also be easily assembled.
  • the axial piston according to the invention is formed in a swash plate design with an adjusting device.
  • the adjusting device comprises an actuating piston and an opposing piston, wherein the effective direction of the actuating piston and that of the counter-piston with respect to a movement of the swash plate are opposite to each other. Both the actuating piston and the counter-piston cooperate at their first end with the swash plate and can transmit a thrust force to them. At their respective second end both the actuating piston and the counter-piston can be acted upon individually with a control force.
  • a rest position which may coincide with a neutral position but need not, is both on the actuating piston and on the opposite piston in each case one provided elastic element.
  • This preferably designed as a spiral spring elastic element, is supported on a first spring bearing, which is arranged on the side facing the swash plate of the adjusting piston and the counter-piston. At the end facing away from the elastic element is supported in each case on a second spring bearing.
  • either the second spring bearing of the actuating piston or the second spring bearing of the counter-piston depends on the abutment direction of the swash plate on a fixed abutment on the housing side.
  • the respective other second spring bearing of the counter-piston or actuating piston is supported on an abutment which is fixed on the piston side.
  • a support ring is preferably provided, which is penetrated by the adjusting piston or the counter-piston.
  • the inner diameter of the support ring is smaller than the radial extent of the respective second spring bearing.
  • This support ring can either be firmly mounted in the housing, provided that the diameter of the actuating piston or counter-piston penetrating it is small enough that such an assembly is possible.
  • an alternative embodiment which is used in particular for large piston diameters of the second end of the actuating piston or counter-piston, however, is between the support ring of the
  • Adjusting piston or opposed piston is penetrated, and arranged a hold-down spring the second spring bearing.
  • This hold-down spring holds the support ring in each position of the swash plate and thus of the actuating piston and of the spring occurring during operation of the axial piston machine
  • Opposite piston in contact with a trained in the housing of the axial piston contact surface has the advantage that a pre-assembly of the support ring in the housing of the axial piston machine is not required, and in particular a subsequent fixation after assembly of the actuating piston or counter-piston is also not required.
  • the support ring in this case preferably has a radial extent which is greater than the Stelltikkairaner malmesser the actuating piston or counter-piston and its passage opening, which is penetrated by the actuating piston or counter-piston is smaller than the second end of the associated actuating or counter-piston.
  • a centering device is formed on the second end of the actuating piston on a side facing the first end of the second actuating piston.
  • a corresponding geometry is provided, is held on the at a pre-assembly of the support ring by the hold-down spring in abutment. In this defined position, a simple mounting of the support ring by inserting the actuating piston or counter-piston in the designated bore of the housing is possible.
  • the centering device is provided at a position of the actuating piston, which at no time comes back in contact with the corresponding geometry of the support ring during operation of the machine, so that a secure fixation of the support ring is secured to the contact surface by the hold-down.
  • the support ring preferably partially closes a bore in which the second end of the control piston or the opposing piston is received, to form therein a control pressure chamber or a working pressure chamber.
  • a spring plate as a second spring bearing whose diameter is smaller than the diameter of the bore. By using such a smaller spring plate is required Movement created so that regardless of the position of the swash plate collision between the spring plate and the cylinder drum is safely excluded.
  • openings are preferably provided in the support ring, with respect to the second end of the
  • Adjusting piston or counter-piston rear volume in the bore with the remaining housing volume connects.
  • Such a diameter-reducing support ring is used in particular on the side of the adjusting piston, the diameter of which is generally larger than that of the counter-piston.
  • Piston diameter and an opposed piston with contrast significantly smaller diameter each at the second end. It is therefore shown below only for the actuator piston, that a support ring is used for piston diameter reduction to use a spring plate as a second spring bearing with a relatively small diameter can. However, it is also conceivable on the side of the counter-piston, that due to the diameter of the counter-piston, the diameter of the bore which receives it, is so large that even there a comparatively arranged and held by a hold-down spring support ring is used.
  • Fig. 2 is an enlarged view of the area of the actuating piston in a rest position of
  • FIG. 4 shows a first view of a support ring according to the invention.
  • Fig. 5 is a sectional view through a support ring of the axial piston according to the invention.
  • FIG. 1 shows a stepped section through an axial piston machine 1 according to the invention.
  • the upper half of FIG. 1 runs along a first section
  • Cutting plane which is parallel to the sectional plane of the lower half of the axial piston machine. Both sectional planes are perpendicular to a rotational axis of the swash plate, which is designed as a pivoting cradle 2 in the illustrated embodiment.
  • the adjusting device is arranged with a control piston 3 and an opposed piston 4 in a plane.
  • the adjusting piston 3 and the counter-piston 4 each have a first end, which is connected via a respective ball joint connection, each with a hold-down segment.
  • the hold-down segments are in turn firmly connected to the pivoting cradle 2, z. B. screwed.
  • the Control piston 3 is a thrust force on the pivoting cradle transferable, which leads to a rotation of the pivoting cradle 2 in the illustrated embodiment in the clockwise direction.
  • two blind holes 50 and 60 are provided in the housing of the axial piston machine.
  • a respective second end of the actuating piston 3 and the counter-piston 4 is arranged in the blind bores 50 and 60.
  • a control pressure chamber 5 is thus formed in the housing of the axial piston machine 1.
  • the diameter of the second end of the counter-piston 4 is smaller than the diameter of the
  • Control piston 3 While the working pressure chamber 6 is permanently connected, for example, with a delivery pressure of an axial piston machine 1 designed as a pump, the pressure prevailing in the control pressure chamber 5 is adjustable by means of a control valve 7. He can z. B. between a reduced from the working line pressure and the tank pressure can be adjusted.
  • Fig. 1 an electro-proportional adjustment is shown, in which the position of the pivoting cradle 2 via a return lever 8 and a feedback spring 9 is fed back to the control valve 7.
  • control valve 7 With vanishing control signals, the control valve 7 is in a neutral position, in which in the control pressure chamber 5 a from the tank pressure and the reduced working pressure averaged pressure
  • the centering springs have only one function in the pressureless state. In the pressureless state, the pivoting cradle 2 is brought into a rest position due to the restoring force of a first return spring 10 or a second return spring 11.
  • the first return spring 10 is designed as a spiral spring and surrounds a part of the counter-piston 4. At the counter-piston 4, a first spring bearing 12 is formed for this purpose. This first spring bearing 12 is near the
  • Ball joint ie the first end of the opposed piston 4 is arranged.
  • the first spring bearing 12 is made for example by machining an opposed piston blank.
  • the first return spring 10 is supported on a second spring bearing 13.
  • On the opposing piston 4 is a radially tapered portion 14th formed over which the slotted executed second spring plate 13 can be pushed.
  • the opposing piston 4 Towards the second end of the counter-piston 4, the opposing piston 4 in turn expands radially, so that a piston-side abutment 15 for the second spring bearing 13 is formed on the counter-piston 4.
  • the second spring bearing 13 is displaceable over the radially tapered region 14 of the counter-piston 4 in the axial direction.
  • the distance between the first spring bearing 12 and the piston-side abutment 15 is dimensioned so that the first return spring 10 is biased in any position of the counter-piston 4.
  • a housing-side abutment is also provided.
  • This housing-side abutment is designed in the form of a support ring 16 which is fixed in the housing of the axial piston machine 1 (for example screwed).
  • An inner diameter of the support ring 16 is dimensioned such that, the second end of the opposed piston 4 can be inserted through the support ring 16 into the blind bore 60 to form the working pressure chamber 6.
  • Such a design is always possible if the diameter of the working pressure chamber 6 is so small that the second end of the counter-piston 4 can be inserted through the support ring 16 therethrough.
  • a first spring bearing 17 and a second spring bearing 18 are provided. Due to the diameter of the bore 50, in which is formed by the second end of the actuating piston 3 of the control pressure chamber 5, and the associated diameter of the second end of the actuating piston 3, however, the support ring 19 can not be designed here so that the second end of the Adjusting piston 3 can be inserted through the support ring 19 into the bore 50 in the housing of the axial piston machine 1. Such a large inner diameter of the support ring 19 would have the consequence that a very large second spring bearing 18 must be used. However, the size of the spring bearing 18 would then lead to its collision with the engine of the axial piston machine 1.
  • the bore 50 is partially covered by the support ring 19.
  • the second end of the actuating piston 3 now no longer through the support ring 19 can be inserted into the bore 50, a pre-assembly of the support ring 19 in the housing of the axial piston machine 1 before insertion of the actuating piston 3 is not possible.
  • the support ring 19 is therefore first pushed onto the control piston 3 from the first end of the control piston 3 ago.
  • a hold-down spring 20 is arranged, which keeps the support ring 19 permanently in abutment against a contact surface during operation of the axial piston 1, which is formed on the housing side of the axial piston machine 1. This will be explained below with reference to Fig. 2 in more detail.
  • the second end of the actuating piston 3 has a diameter which corresponds to the diameter of the bore 50 or an inner diameter of a bushing arranged therein.
  • the second end of the control piston 3 thus limits a control pressure chamber 5 in the bore 50.
  • the diameter of the control piston 3 tapers.
  • the support ring 19 When mounting the axial piston machine 1, the support ring 19 is first pushed from the first end of the actuating piston 3 forth on the actuating piston 3. Subsequently, the hold-down spring 20 is pushed over the control piston 3, followed by the second spring bearing 18.
  • the support ring 19 and the second spring bearing 18 each have an inner diameter which is larger than the first end of the control piston 3.
  • the inner diameter of the second spring bearing 18th is smaller than the inner diameter of the support ring 19.
  • a formed on the control piston 3 near the second end paragraph 28 thus forms a piston-side abutment for the second spring bearing 18.
  • the second return spring 11 After placing the second spring bearing 18 is the second return spring 11 is placed. Finally, the first spring bearing 17 is mounted.
  • a shoulder is formed as an abutment for the first spring bearing 17 and at the first end of the actuating piston 3.
  • the first spring bearing 17 is designed radially slotted in a conventional manner, so that it can be pushed into a central, radially tapered portion 29 of the actuating piston 3.
  • the diameter of the actuating piston 3 in this position is greater than the width of the slots, so that a radial offset during operation is excluded.
  • the second spring bearing 18 either on the piston-side abutment 28 or on the housing side in the form of the support ring 19 Abutment. Regardless of the position of the actuating piston 3 relative to the support ring 19 while the hold-down spring 20 ensures that the support ring 19 is always in contact with a contact surface 21 which is formed on the housing side.
  • the hold-down spring 20 has a much smaller spring constant than the return springs 10, 11.
  • centering device 26 is a frusto-conical portion which cooperates with a corresponding geometry 27 on the part of the support ring 19.
  • the corresponding geometry 27 is formed by a chamfer in the region of the passage opening 25 of the support ring 19.
  • FIG. 3 once again shows the enlarged region of FIG. 2 when the swashplate 2 has been pivoted clockwise from its rest position. Due to the force of the hold-down spring 20 of the support ring 19 remains in contact with the contact surface 21. At maximum adjustment of the pivoting cradle 2 in the clockwise direction still remains here Distance between the centering device 26 of the actuating piston 3 and the corresponding geometry 27 of the support ring 19. In this way it is ensured that an adjusting movement does not come to an accidental movement of the support ring 19 through the second end of the actuating piston 3. Both in the support ring 19 and in the second spring bearing 18 recesses for receiving the hold-down spring 20 are preferably provided.
  • Fig. 4 is a view of the first end of the actuating piston 3 facing side of the support ring 19 is shown. It can be seen that a plurality of compensation openings 24 are provided distributed over the circumference. These compensation openings 24 serve to connect the volume formed in the bore 50 on the side of the second end 2 facing the first end of the actuating piston 3 to the remaining housing volume. This can be done with a movement of the actuating piston 3 in the bore 50, a pressure equalization.
  • the second end of the actuating piston 3 is sealed, for example by means of a piston ring with respect to the bore 50.
  • a bushing is inserted into the bore 50, in which the adjusting piston 3 can slide with reduced friction.
  • all the spring bearings in the illustrated embodiment are designed so that they have an extension, with they engage in the return springs 10 and 11 designed as a spiral spring. In this way, an alignment of the return springs 11 and 12 with respect to the actuating piston 3 and the counter-piston 4 is achieved.
  • FIG. 5 shows a section through the support ring 19, which again shows the different diameters of the further shoulder 33, the passage opening 25 and the step 23 for receiving the hold-down spring 20.
  • a chamfer is formed as a corresponding geometry 27 to the conical centering device 26.
  • the invention is not limited to the illustrated axial piston machine. Rather, the features shown in particular in connection with the first control piston and the second control piston or the arrangement of the return spring can also advantageously combine with each other.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne une machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage. Le dispositif de réglage présente un piston de réglage (3) et un piston antagoniste (4). Le piston de réglage (3) et le piston antagoniste (4) sont reliés, respectivement, par leurs premières extrémités, avec le disque oscillant (2), cependant qu'une force agissant en direction de la première extrémité peut être appliquée, respectivement, sur leurs secondes extrémités. Pour le rappel du disque oscillant (2) en position de repos, il est prévu, aussi bien sur le piston de réglage (3) que sur le piston antagoniste (4), un élément élastique (10, 11) qui est supporté, respectivement, par une première butée élastique (12, 17) disposée sur un premier côté du piston de réglage (3) ou du piston antagoniste (4), faisant face au disque oscillant (2). En direction opposée, l'élément élastique (10, 11) est supporté, respectivement, par une seconde butée élastique (13, 18) qui est disposée sur l'extrémité du piston de réglage (3) ou du piston antagoniste (4), opposée au disque oscillant (2). Lorsque le disque oscillant (2) quitte sa position de repos, la seconde butée élastique (13, 18) du piston de réglage (3) ou du piston antagoniste (4) prend appui sur une contre-butée fixée du côté du boîtier, cependant que la seconde butée élastique (13, 18), respectivement, de l'autre piston de réglage (3) ou du piston antagoniste (4) prend appui sur une contre-butée fixée du côté du piston.
EP08801631A 2007-08-20 2008-08-20 Machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage Not-in-force EP2179175B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007039173 2007-08-20
PCT/EP2008/006850 WO2009024336A1 (fr) 2007-08-20 2008-08-20 Machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage

Publications (2)

Publication Number Publication Date
EP2179175A1 true EP2179175A1 (fr) 2010-04-28
EP2179175B1 EP2179175B1 (fr) 2013-02-27

Family

ID=39884939

Family Applications (2)

Application Number Title Priority Date Filing Date
EP08801632A Not-in-force EP2179176B1 (fr) 2007-08-20 2008-08-20 Système hydraulique avec une machine hydrostatique réglable
EP08801631A Not-in-force EP2179175B1 (fr) 2007-08-20 2008-08-20 Machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP08801632A Not-in-force EP2179176B1 (fr) 2007-08-20 2008-08-20 Système hydraulique avec une machine hydrostatique réglable

Country Status (6)

Country Link
US (2) US20100199838A1 (fr)
EP (2) EP2179176B1 (fr)
JP (1) JP5027303B2 (fr)
CN (2) CN101815865B (fr)
DE (2) DE102008038435A1 (fr)
WO (2) WO2009024337A1 (fr)

Families Citing this family (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006062065A1 (de) * 2006-12-29 2008-07-03 Robert Bosch Gmbh Axialkolbenmaschine mit einem einen radial erweiterten Innenraumabschnitt aufweisenden Gehäuse
EP2174010A1 (fr) * 2007-08-07 2010-04-14 Robert Bosch GmbH Machine hydrostatique avec dispositif de réglage avec élément de retour pour la commande d'une soupape de réglage
JP2013530346A (ja) * 2010-07-08 2013-07-25 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング ハイドロリック式のアキシャルピストン機械
DE102011105465B4 (de) * 2010-07-08 2021-05-27 Robert Bosch Gmbh Hydraulische Doppelaxialkolbenmaschine mit fluchtend zueinander ange-ordneten Stellkolben und an unterschiedlichen Anbauflächen des Gehäuses angebrachten Regelventilen
DE102010032649A1 (de) 2010-07-29 2012-02-02 Robert Bosch Gmbh Verstellbare Axialkolbenmaschine und Schwenkwiege
CN101956686B (zh) * 2010-10-21 2012-02-08 宁波广天赛克思液压有限公司 一种位置-弹簧-力反馈式电比例变量轴向柱塞泵
DE102011006102A1 (de) * 2011-03-25 2012-09-27 Zf Friedrichshafen Ag Stellvorrichtung eines Hydrostatmoduls
WO2013037582A1 (fr) 2011-09-16 2013-03-21 Robert Bosch Gmbh Dispositif de réglage pour une machine hydrostatique et machine hydrostatique
DE102011117543A1 (de) 2011-11-03 2013-05-08 Robert Bosch Gmbh Axialkolbenmaschine
DE102011121520A1 (de) 2011-12-16 2013-06-20 Robert Bosch Gmbh Verstelleinrichtung für eine Axialkolbenmaschine undAxialkolbenmaschine mit einer Verstelleinrichtung
DE102012001369B4 (de) * 2012-01-25 2021-12-16 Robert Bosch Gmbh Verstellbare Hydropumpe
DE102012104755A1 (de) * 2012-06-01 2013-12-05 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Verdrängermaschine
GB2502824A (en) * 2012-06-08 2013-12-11 Water Hydraulics Company Ltd Axial piston variable stroke hydraulic machine
DE102012015503A1 (de) 2012-08-04 2014-02-06 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
DE102012214373A1 (de) 2012-08-13 2014-05-15 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
DE102013214861A1 (de) * 2012-08-16 2014-05-22 Robert Bosch Gmbh Verstellvorrichtung für eine hydrostatische Pumpe und hydrostatische Pumpe
DE102012021320A1 (de) * 2012-10-31 2014-04-30 Robert Bosch Gmbh Verstellvorrichtung für eine hydrostatische Kolbenmaschine und hydrostatische Kolbenmaschine mit einer derartigen Verstellvorrichtung
DE102012022694A1 (de) * 2012-11-20 2014-05-22 Robert Bosch Gmbh Regelventil, insbesondere für eine elektroproportionale Schwenkwinkelregelung einer Hydromaschine
DE102012023272A1 (de) 2012-11-29 2014-06-05 Robert Bosch Gmbh Verstelleinrichtung für eine hydraulische Axialkolbenmaschine und hydraulische Axialkolbenmaschine
DE102013202615A1 (de) 2013-02-19 2014-08-21 Robert Bosch Gmbh Verstellbare Hydromaschine
DE102013206737A1 (de) 2013-04-16 2014-10-16 Robert Bosch Gmbh Axialkolbenmaschine in Schrägscheibenbauweise
CN105339657B (zh) * 2013-05-22 2018-01-12 贺德克传动中心有限公司 以斜盘式结构形式的轴向活塞泵
DE102013212199A1 (de) 2013-06-26 2014-12-31 Robert Bosch Gmbh Adaptiver Ansatz zur Regelung einer Axialkolbeneinheit mit EP-Verstellung
DE102013213883A1 (de) * 2013-07-16 2015-01-22 Robert Bosch Gmbh Verfahren und System zum Regeln eines Schwenkwinkels
DE102013216395B4 (de) * 2013-08-19 2019-01-17 Danfoss Power Solutions a.s. Steuereinrichtung für hydraulische verstellpumpen und verstellpumpe mit einer steuereinrichtung
DE102013225892A1 (de) 2013-12-13 2015-06-18 Robert Bosch Gmbh Schrägscheibenmaschine, Schrägscheibe und Verfahren zur hydrostatischen Entlastung einer Stellteilanbindung einer Schrägscheibenmaschine und zum Druckabbau eines Arbeitsmediums während eines Umsteuervorgangs der Schrägscheibenmaschine
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DE102015202406A1 (de) 2014-02-18 2015-08-20 Robert Bosch Gmbh Hydraulische Anordnung
DE102014211194A1 (de) * 2014-06-12 2015-12-17 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise und Lüfter mit einer hydrostatischen Axialkolbenmaschine
CN108431417B (zh) 2015-11-15 2019-12-06 伊顿智能动力有限公司 液压泵控制系统
DE102015224129A1 (de) * 2015-12-03 2017-06-08 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
CH714321A1 (de) * 2017-11-11 2019-05-15 Liebherr Machines Bulle Sa Verstellvorrichtung für eine Axialkolbenmaschine.
FR3093138B1 (fr) 2019-02-25 2022-07-15 Univ Versailles Saint Quentin En Yvelines Actionneur hydraulique à compensation de surpression
CN112343806B (zh) * 2019-08-08 2023-08-29 丹佛斯动力系统公司 用于开放回路可变排量泵的电动排量控制
US11644028B2 (en) * 2020-04-08 2023-05-09 Danfoss Power Solutions, Inc. Control arrangement for variable displacement pump
CN114382609B (zh) * 2021-12-13 2024-08-16 天津大学 往复式高低压自适应补偿密封装置
FR3131273A1 (fr) * 2021-12-23 2023-06-30 Safran Aircraft Engines Circuit de commande hydraulique de calage d’aubes de soufflante
FR3131274A1 (fr) * 2021-12-23 2023-06-30 Safran Aircraft Engines Circuit de commande hydraulique de calage d’aubes de soufflante

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3234889A (en) * 1963-02-07 1966-02-15 New York Air Brake Co Hydraulic device
DE3213958A1 (de) * 1981-08-21 1983-03-03 Robert Bosch Gmbh, 7000 Stuttgart Elektrohydraulische verstelleinrichtung fuer eine hydrostatische maschine
DE3733625A1 (de) * 1987-07-23 1989-02-02 Bosch Gmbh Robert Axialkolbenmaschine
EP0367476A1 (fr) * 1988-11-02 1990-05-09 Vickers Systems Limited Pompes à déplacement variable
JPH02140468A (ja) * 1988-11-18 1990-05-30 Daikin Ind Ltd 可変容量形液圧装置
DE3935800C2 (de) * 1989-10-27 1997-03-27 Linde Ag Einstellbare Axialkolbenmaschine in Schrägscheibenbauweise
DE4203619C2 (de) * 1992-02-07 1996-07-25 Rexroth Mannesmann Gmbh Hydrauliksystem
DE4229007C2 (de) * 1992-08-31 2002-06-13 Linde Ag Axialkolbenmaschine in Schrägscheibenbauweise
DE19653165C2 (de) * 1996-12-19 2002-04-25 Brueninghaus Hydromatik Gmbh Verstelleinrichtung zur Verstellung des Fördervolumens einer Axialkolbenpumpe
DE19705598A1 (de) * 1997-02-14 1998-08-20 Bosch Gmbh Robert Elektromechanischer Doppelhubmagnet
US5794515A (en) * 1997-04-03 1998-08-18 Bethke; Donald G. Swashplate control system for an axial piston pump
DE19807443A1 (de) * 1998-02-24 1999-08-26 Kleinedler Axialkolbenmaschine
DE19949169C2 (de) 1999-10-12 2001-10-11 Brueninghaus Hydromatik Gmbh Verstellvorrichtung
DE10136416A1 (de) 2001-07-26 2003-02-13 Brueninghaus Hydromatik Gmbh Ventilblock für eine Regelvorrichtung, insbesondere für eine hydrostatische Maschine
US6705203B2 (en) * 2001-11-28 2004-03-16 Sauer-Danfoss Inc. Extended male slipper servo pad arrangement for positioning swashplate and method assembling same
DE10313426B3 (de) * 2003-03-25 2004-11-11 Sauer Bibus Gmbh Verstellpumpeneinheit
DE10325842A1 (de) * 2003-06-06 2005-01-05 Brueninghaus Hydromatik Gmbh Reversierbare Axialkolbenmaschine mit Längsverstellung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009024336A1 *

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CN101815865A (zh) 2010-08-25
US20100206161A1 (en) 2010-08-19
DE102008038435A1 (de) 2009-02-26
DE102008038455A1 (de) 2009-02-26
CN101815865B (zh) 2012-06-27
US20100199838A1 (en) 2010-08-12
JP5027303B2 (ja) 2012-09-19
WO2009024336A1 (fr) 2009-02-26
JP2010537108A (ja) 2010-12-02
WO2009024337A1 (fr) 2009-02-26
EP2179175B1 (fr) 2013-02-27
EP2179176A1 (fr) 2010-04-28
CN101842590B (zh) 2012-12-05
US8006610B2 (en) 2011-08-30
CN101842590A (zh) 2010-09-22
EP2179176B1 (fr) 2013-04-03

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