EP1636459A1 - Moteur a pistons axiaux reversible a reglage longitudinal - Google Patents

Moteur a pistons axiaux reversible a reglage longitudinal

Info

Publication number
EP1636459A1
EP1636459A1 EP04724008A EP04724008A EP1636459A1 EP 1636459 A1 EP1636459 A1 EP 1636459A1 EP 04724008 A EP04724008 A EP 04724008A EP 04724008 A EP04724008 A EP 04724008A EP 1636459 A1 EP1636459 A1 EP 1636459A1
Authority
EP
European Patent Office
Prior art keywords
hollow cylinder
piston
actuating
machine according
opening
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
EP04724008A
Other languages
German (de)
English (en)
Other versions
EP1636459B1 (fr
Inventor
Günter Wanschura
Hakan Camurdan
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1636459A1 publication Critical patent/EP1636459A1/fr
Application granted granted Critical
Publication of EP1636459B1 publication Critical patent/EP1636459B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F04B1/26—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0035—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F01B3/0038—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0064—Machine housing
    • F01B3/0067—Machine housing cylinder barrel bearing means
    • 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

Definitions

  • the invention relates to a reversible axial piston machine with an adjusting device for adjusting the swivel angle of a swivel cradle of the reversible axial piston machine in both swivel directions.
  • the volume of hydraulic fluid delivered in one rotation of the drive shaft of an axial piston machine is dependent on the lifting height of the cylinders arranged in a cylinder drum of an axial piston machine during a compression or suction process.
  • the lifting height is set in relation to the axial alignment of the drive axis by inclining the inclined surface of a swivel cradle on which the individual cylinders are supported during their rotational movement about the drive axis.
  • the setting angle of the inclined surface for the axial alignment of the drive axis is adjusted by an adjusting device.
  • the adjusting device In principle, there are two embodiments for the arrangement of the adjusting device in relation to the arrangement of the drive axis of the axial piston machine.
  • the adjusting device In the transverse adjustment, the adjusting device carries out a translational movement for adjusting the pivoting cradle transversely to the arrangement of the drive axis of the axial piston machine.
  • the adjusting device carries out a translational movement for adjusting the swivel cradle in the longitudinal direction of the drive axis of the axial piston machine.
  • the longitudinal adjustment is preferable to the transverse adjustment, since this Variant has a smaller construction volume.
  • a not insignificant problem of adjusting devices is the exact setting of the zero position.
  • the pivoting cradle In the uncontrolled operating state of the adjusting device, for example when there is no signal pressure in a pressure-controlled adjusting device — depressurized operating state — the pivoting cradle has an adjusting angle of exactly zero degrees when the adjusting device is set to the zero position.
  • the inclined surface is exactly perpendicular to the longitudinal axis of the drive shaft. It is not possible for any of the pistons in all cylinders of the cylinder drum to perform a lifting movement.
  • DE 37 14 888 AI shows a reversible axial piston machine with an adjusting device that works according to the longitudinal adjustment variant.
  • the zero position of the swivel cradle in the uncontrolled operation of the axial piston machine cannot be adjusted and is undefined.
  • the adjustment angle actually set on the swivel cradle in this axial piston machine therefore generally does not exactly correspond to the specified adjustment angle.
  • the actual displacement volume thus generally deviates from the predefined displacement volume.
  • the invention is therefore based on the object of developing the reversible axial piston machine with longitudinal adjustment in accordance with the features according to the preamble of claim 1 in such a way that a displacement volume in the ' uncontrolled state is certainly not present.
  • the object of the invention is achieved by a reversible axial piston machine with the features of claim 1.
  • a zero position adjusting device is provided in the adjusting device according to claim 1.
  • the advantage of this zero position adjusting device can be seen in the fact that the zero position of the inclined surface can be set precisely and without play in the uncontrolled operation of the axial piston machine.
  • Another advantage of the zero position adjusting device lies in the use of a single compression spring, which is tensioned on the adjusting rod between two spring plates, and the adjusting piston, which can be displaced in the adjusting device, is subjected to the same pretensioning force in both adjusting directions. It is thus possible to position the actuating piston and the pivoting cradle coupled via a positive connection to the actuating piston in the adjustment process of the zero position determination with a prestressing force determined by the spring constant of the compression spring in both adjusting and pivoting directions.
  • An elaborate coordination of two oppositely acting compression springs, which in such applications usually generate a prestressing force for one direction of adjustment, with regard to spring constants of the same size and thus prestressing forces of the same size, can be dispensed with here.
  • the claimed reversible axial piston machine and the associated adjusting device also have the advantage that they can be limited by means of a second adjusting rod, which is also led out of the adjusting device or the axial piston machine, with respect to the adjustment path of the adjusting piston or the adjustment angle of the pivoting cradle.
  • the adjusting device claimed has the advantage that, due to its hollow cylindrical design, the adjusting piston, the zero position adjusting device and others can be assembled and disassembled relatively easily components located within the hollow cylinder of the adjusting device is possible.
  • Figure 1 is a cross-sectional view of an axial piston machine according to the invention with an adjusting device according to the invention.
  • FIG. 2 shows a cross-sectional illustration of an adjusting device according to the invention
  • Fig. 3 is a cross-sectional view of another
  • FIG. 4 shows a three-dimensional view of an axial piston machine according to the invention with an adjusting device according to the invention connected via a positive connection.
  • FIG. 1 shows a cross section of a reversible axial piston machine 1 according to the invention.
  • This consists of a drive shaft 4 mounted in an axially aligned recess 2 of the housing 3.
  • a cylinder drum 5 is arranged on the drive shaft 4 in a rotationally fixed manner, in which a plurality of cylinder recesses are arranged at equal distances from one another on a concentric circle to the longitudinal axis 7 of the drive shaft 4.
  • a piston 6 is slidably guided, which is on the cylinder chamber opposite end has a ball head which is pivotally mounted in a sliding shoe and is supported against an inclined surface 8.
  • the pivoting cradle 9 and with it the inclined surface 8 can be pivoted in relation to a zero position axis 10, which is oriented at a right angle to the axis of rotation 7 of the cylinder drum 5, by positive adjustment angle ⁇ 1 and negative adjustment angle ⁇ .2 to the zero position axis 10.
  • the adjusting device 12 the cross section of which, in addition to the illustration in FIG. 1, is also shown in FIG. 2 on a slightly enlarged scale, consists of a hollow cylinder 13 serving as a housing and having a first step 14.
  • the second opening 18 of the hollow cylinder 13 opposite the first opening 15 is closed off with a closure cover 19.
  • the closure cover 19 has an annular web 20. The outer diameter of the annular web
  • the inside diameter of the annular web 20 of the sealing cover 19 corresponds to the inside diameter of the hollow cylinder 13 in
  • closure cover 19 is with an annular web 20 in the interior 17 of the closure cover 19
  • Hollow cylinder 13 introduced that a positive connection between the hollow cylinder 13 and the
  • annular grooves 22 On the inner lateral surface 21 of the hollow cylinder 13 between the first opening 15 and the first step 14 and on the inner circumferential surface 27 of the annular web 20 of the closure cover 19 are annular grooves 22 in which guide rings 23 made of brass, for example, are arranged. These guide rings 23 serve as guide bearings for the actuating piston 24, which is mounted in the interior 17 of the hollow cylinder 13 centrally to the longitudinal axis 11 and is displaceable in the direction of the longitudinal axis 11.
  • the actuating piston 24 essentially has a hollow cylindrical geometry. Approximately at half the cylinder height of the hollow cylindrical actuating piston 24, the actuating piston 24 has a flange-shaped extension 26 on its outer lateral surface 25. Since the width of this flange-shaped extension 26 corresponds to the width of the first step 14 of the hollow cylinder 13, the flange-shaped extension 26 of the actuating piston 24 is in contact with the inner lateral surface 27 of the hollow cylinder 13 between the first step 14 and the second opening 18.
  • a first actuating pressure chamber 28 and a second actuating pressure chamber 29 are formed in the interior 17 of the hollow cylinder 13.
  • First side surface 30 of the flange-shaped extension 26 of the actuating piston 24 serves as an engagement surface for an actuating pressure guided through the first actuating pressure opening 31 in the wall of the hollow cylinder 13 into the first actuating pressure chamber 28 for displacing the actuating piston 24 along its longitudinal axis 11 in the direction of the second opening 18 of the hollow cylinder 13.
  • the second side surface 32 of the flange-shaped extension 26 of the actuating piston 24, which is connected to the second actuating pressure chamber 29, serves as an engagement surface for an actuating device which is guided through the second actuating pressure opening 33 in the wall of the hollow cylinder 13 into the second actuating pressure chamber 29 jerk to the displacement of the actuating piston 24 along its longitudinal axis 32 in the direction of the first opening 15 of the hollow cylinder 13.
  • first and second actuating pressure chambers 28 and 29 against hydraulic fluid ', in the area of the inner lateral surfaces 21 and 27 of the hollow liner 13, the inner lateral surface 22 and the outer lateral surface 34 of the annular web 20 of the closure cover 19 and the end surface 35 of the flange-shaped extension 26 of the actuating piston 24 sealing rings 36 provided in grooves.
  • the hollow cylindrical actuating piston 24 has a multiply stepped recess 37, the largest third opening 38 of which points in the direction of the second opening 18 of the hollow cylinder 13.
  • a first adjustment rod 39 is guided into the multiply stepped recess 37 along the longitudinal axis 11 of the actuating piston 24.
  • This first adjusting rod 39 is led out of the adjusting device 12 via a bore 40 in the closure cover 19.
  • a first spring plate 43 and a second spring plate 44 are fixed on the adjusting rod 39 in the area between the second step 42 and the third opening 38 of the recess 37 of the actuating piston 24.
  • the first spring plate 43 is fixed on the adjusting rod 39 in that the spring plate 43 is pressed with the pretensioning force of a compression spring package 45 tensioned between the first spring plate 43 and the second spring plate 44 against the inside end face 46 of an end flange 47 fastened to the hollow cylinder end of the adjusting rod 39 becomes-.
  • the second spring plate 44 is fixed on the adjusting rod 39 in that the Spring plate 44 is pressed with the prestressing force of the compression spring package 45 against a sleeve 48 fixed on the adjusting rod 39 between the spring plate 44 and the closure cover 19.
  • the sleeve 48 has an annular groove on its inside, in which an annular body 55 is fixed, which is arranged in a groove of the first adjusting rod 39 and is supported on the inside end face 46a of the groove arranged in the adjusting rod 39.
  • the sleeve 48 and the position of the groove arranged in the adjusting rod could also be designed such that the spring plate 44 is pressed directly against the annular body 55.
  • the compression spring package 45 is composed of the two compression springs 45A and 45B arranged in parallel, so that the compression spring package. 45 a compact design can be achieved.
  • a first spring plate 43 with its end face 49 facing away from the compression spring package 45 is in contact with the second step 42 of the recess 37 of the actuating piston 24.
  • the second spring plate 44 is in contact with its end face 50 facing away from the compression spring package 45 with a snap ring 51, which is arranged in an annular groove on the inner side surface of the recess 37 of the actuating piston 24 in the vicinity of the third opening 38.
  • a second adjustment rod 52 which is guided through a bore 53 in the closure cap 19 into the interior 17 of the hollow cylinder 13, serves as an adjustable limitation for the adjustment path of the actuating piston 24 along its longitudinal axis 32.
  • the second adjustment rod 52 can be screwed onto an adjustment nut 54 the thread of the second adjusting rod 52 outside the closure cover 19 can be changed in its position within the interior 17 of the hollow cylinder 13.
  • An adjustment of the swivel cradle 19 in the direction of a positive adjustment angle ⁇ l in the sense of a zero point adjustment is carried out by positioning the first adjusting rod 39 in the direction of the second opening 18 of the hollow cylinder 13 by actuating the first adjusting screw 41.
  • the zero position adjusting device 32 consisting of the first adjusting rod 19, the compression spring package 45, the first spring plate 43, the second spring plate 44 and the sleeve 48, moved in the direction of the second opening 18 of the hollow cylinder 13.
  • the force required for this displacement is provided by the end flange 47 of the adjusting rod 39, which is moved in the direction of the second opening 18 of the hollow cylinder 13, via its inside end face 46 onto the first spring plate 43, from the first spring plate 43 onto the compression spring package 45, and from the compression spring package 45 transferred to the second spring plate 44 and finally from the second spring plate 44 to the snap ring 51 which, positively fixed with the actuating piston 24, displaces the actuating piston 24 in the direction of the second opening 18.
  • the pivot cradle 19 is adjusted in the direction of a negative adjustment angle ⁇ 2 in the sense of a zero point adjustment by positioning the first adjustment rod 39 in the direction of the first opening 15 of the hollow cylinder 13 by actuating the first adjustment screw 41. In this way, the zero position device 32 becomes in the direction of the first opening 15 of the hollow cylinder 13 moved.
  • the power transmission takes place in this case from the sleeve 48, which is moved via the annular body 55 with the first adjusting rod 39 in the direction of the first opening 15 of the hollow cylinder 13, to the second spring plate 44, from the second spring plate 44 to the compression spring assembly 45, from Compression spring package 45 on the first spring plate 43 and finally from the first spring plate 43 to the second step 42 of the recess 37 of the actuating piston 24.
  • the power transmission to the actuating piston 24 causes the actuating piston 24 to be displaced in the direction of the first Opening 15 of the hollow cylinder 13.
  • the compression spring package 45 primarily has the task of generating a spring force proportional to the deflection of the actuating piston 24, which counteracts the actuating force which triggers the movement. This restoring spring force is identical for both directions of displacement of the actuating piston 24 due to the use of a single compression spring package 45.
  • the spring force of the compression spring assembly 45 also has a certain value in the zero position of the pivoting cradle 9, since the compression spring assembly 45 is held biased between the first spring plate 43 and the second spring plate 44 in each of the positions of the actuating piston 24.
  • the displacement of the actuating piston 24 in the direction of the second opening 18 of the hollow cylinder 13 results in the first spring plate 43 on its end face 49 from the second stage 42 of the hollow cylinder 13 a force which is transmitted to the second spring plate 44 via the compression spring package 45 and which leads to a displacement of the second spring plate in the direction of the second opening 18 of the hollow cylinder 13.
  • the second spring plate 44 rests with its end face 50 on the sleeve 48 and cannot be displaced in the direction of the second opening of the hollow cylinder 13 due to the local fixation of the adjusting rod 39 and with the sleeve 48.
  • the actuating piston 24 is displaced in the direction of the first opening 15 of the hollow cylinder 13. Via the displacement of the actuating piston 24 and thus in the Actuating piston 24 integrated snap ring 51 in the direction of the first opening 15 of the hollow cylinder 13, a force is transmitted to the second spring plate 44, which in turn is transmitted from the second spring plate 44 to the compression spring assembly 45.
  • the transmission of the axial movement of the actuating piston 24 along its longitudinal axis 11 into a pivoting movement of the pivoting cradle 9 takes place according to FIG. 4 via a sliding block 56 which is guided in a groove 57 of the adjusting device 12.
  • the sliding block 56 has a recess (not shown in FIG. 4) in which a pin (not shown in FIG. 4) shown) is rotatably mounted. This pin is attached to the side surface of a connecting arm 58, which in turn is fixed to the swivel cradle 9.
  • the one-dimensional axial movement of the adjusting piston 24 in the adjusting device 12 is consequently converted into a rotary pivoting movement of the pivoting cradle 9 via a one-dimensional sliding movement of the sliding block 56 in the groove 57 of the adjusting device 12 in combination with a rotary movement of the pin in the recess of the sliding block 56.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

L'invention concerne un moteur à pistons axiaux réversible (1) composé d'un tambour de cylindre (5) tournant autour d'un axe de rotation (7), dans lequel des pistons (6) peuvent être déplacés dans des cylindres (5), lesdits pistons s'appuyant contre une surface inclinée (8). L'angle de réglage ( alpha 1, alpha 2) de la surface inclinée (8) peut être réglé au moyen d'un dispositif de réglage (12). L'angle de réglage ( alpha 1, alpha 2), pouvant être réglé dans les deux sens de pivotement, est réglé au moyen d'un piston de réglage (24) du dispositif de réglage (12), s'étendant essentiellement perpendiculairement par rapport à la direction de l'axe de rotation (7) du tambour de cylindre (5). La position nulle du réglage de la surface inclinée (8) peut être réglée sans jeu au moyen d'un dispositif de réglage de position nulle (32).
EP04724008A 2003-06-06 2004-03-29 Moteur a pistons axiaux reversible a reglage longitudinal Expired - Lifetime EP1636459B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10325842A DE10325842A1 (de) 2003-06-06 2003-06-06 Reversierbare Axialkolbenmaschine mit Längsverstellung
PCT/EP2004/003323 WO2004109060A1 (fr) 2003-06-06 2004-03-29 Moteur a pistons axiaux reversible a reglage longitudinal

Publications (2)

Publication Number Publication Date
EP1636459A1 true EP1636459A1 (fr) 2006-03-22
EP1636459B1 EP1636459B1 (fr) 2007-07-18

Family

ID=33494887

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04724008A Expired - Lifetime EP1636459B1 (fr) 2003-06-06 2004-03-29 Moteur a pistons axiaux reversible a reglage longitudinal

Country Status (6)

Country Link
US (1) US7367258B2 (fr)
EP (1) EP1636459B1 (fr)
KR (1) KR101138855B1 (fr)
CN (1) CN1798904B (fr)
DE (2) DE10325842A1 (fr)
WO (1) WO2004109060A1 (fr)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009024337A1 (fr) * 2007-08-20 2009-02-26 Robert Bosch Gmbh Système hydraulique à machine hydrostatique réglable
US8677886B2 (en) * 2009-10-26 2014-03-25 Caterpillar Inc. High response hydraulic actuator
DE102010026157A1 (de) * 2010-07-06 2012-01-12 Robert Bosch Gmbh Hydrostatische Maschine, insbesondere Axialkolbenmaschine
DE102010062950A1 (de) * 2010-12-13 2012-06-14 Zf Friedrichshafen Ag Stellvorrichtung eines Hydrostatmoduls
US8845303B2 (en) * 2010-12-22 2014-09-30 Eaton Corporation Torque control for open circuit piston pump
DE102011006102A1 (de) * 2011-03-25 2012-09-27 Zf Friedrichshafen Ag Stellvorrichtung eines Hydrostatmoduls
DE102011088364A1 (de) * 2011-12-13 2013-06-13 Zf Friedrichshafen Ag Stellvorrichtung eines Hydrostatmoduls
DE102012222936A1 (de) * 2012-12-12 2014-06-12 Robert Bosch Gmbh Axialkolbenmaschine
DE102014215024A1 (de) * 2013-09-06 2015-03-12 Robert Bosch Gmbh Im Hubvolumen verstellbare hydrostatische Axialkolbenmaschine, inbesondere im Hubvolumen verstellbarer hydrostatischer Axialkobenmotor
CN103573616B (zh) * 2013-11-08 2016-03-02 无锡威孚精密机械制造有限责任公司 柱塞泵的变量缸结构
JP6248844B2 (ja) * 2014-07-16 2017-12-20 株式会社豊田自動織機 可変容量型ピストンポンプ
DE102014218420A1 (de) * 2014-09-15 2016-03-17 Robert Bosch Gmbh Verstelleinrichtung für eine hydrostatische Axialkolbenmaschine
DE102015203962A1 (de) 2015-03-05 2016-09-08 Robert Bosch Gmbh Anordnung zur Dichtung und Führung
US10145396B2 (en) * 2016-12-15 2018-12-04 Caterpillar Inc. Energy recovery system and method for hydraulic tool
DE102017213457A1 (de) * 2017-08-03 2019-02-07 Robert Bosch Gmbh Hydrostatische Verstelleinrichtung für eine hydrostatische Verdrängermaschine und hydrostatische Verdrängermaschine
DE102018218547A1 (de) * 2018-10-30 2020-04-30 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
DE102020211285A1 (de) * 2020-02-13 2021-08-19 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulischer Lüfterantrieb
DE102022211921A1 (de) * 2022-11-10 2024-05-16 Robert Bosch Gesellschaft mit beschränkter Haftung Filtervorrichtung mit schwenkbarer Filterpatrone

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE40492C (de) S. MORATH in Ueberlingen Hydraulischer Zahnheber
DE3346000A1 (de) * 1982-12-21 1984-06-28 Linde Ag, 6200 Wiesbaden Hydraulische stelleinrichtung fuer eine hydrostatische maschine
DE3714888C2 (de) * 1987-05-05 1994-10-06 Linde Ag Einstellbare Axialkolbenmaschine
DE3935800C2 (de) * 1989-10-27 1997-03-27 Linde Ag Einstellbare Axialkolbenmaschine in Schrägscheibenbauweise
DE4018494A1 (de) * 1990-06-09 1991-12-12 Teves Gmbh Alfred Verfahren fuer die einstellung einer kolbenzylinderanordnung
US5226349A (en) * 1992-07-15 1993-07-13 Eaton Corporation Variable displacement hydrostatic pump and improved gain control thereof
KR970044601A (ko) * 1995-12-29 1997-07-26 전성원 회전형 피스톤
DE19755386C2 (de) * 1997-12-12 1999-10-21 Brueninghaus Hydromatik Gmbh Hydrostatische Maschine mit einer drehbar gelagerten Zylindertrommel und einer einstellbaren Schwenkscheibe
DE10037482C1 (de) * 2000-08-01 2002-02-28 Sauer Danfoss Neumuenster Gmbh Hydrostatische Verstellpumpe mit außerhalb des Servozylinder-Druckraumes angeordneten Federn

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004109060A1 *

Also Published As

Publication number Publication date
US20060123984A1 (en) 2006-06-15
US7367258B2 (en) 2008-05-06
DE10325842A1 (de) 2005-01-05
KR101138855B1 (ko) 2012-05-15
KR20060025548A (ko) 2006-03-21
DE502004004376D1 (de) 2007-08-30
EP1636459B1 (fr) 2007-07-18
CN1798904A (zh) 2006-07-05
CN1798904B (zh) 2011-04-20
WO2004109060A1 (fr) 2004-12-16

Similar Documents

Publication Publication Date Title
WO2004109060A1 (fr) Moteur a pistons axiaux reversible a reglage longitudinal
DE3942189C1 (fr)
DE2340663A1 (de) Servogesteuerte, hydraulische kraftuebertragungsvorrichtung
EP2145105B1 (fr) Machine à pistons axiaux
EP2092192A1 (fr) Machine à piston axial hydrostatique
DE19504220A1 (de) Verstellbare hydrostatische Pumpe
DE102007022568A1 (de) Niederhaltesegment
DE10043451B4 (de) Einteilige Proportionalregelung
EP2145106B1 (fr) Machine à pistons axiaux pourvue d'un dispositif de rappel
EP1058771A1 (fr) Moteur a pistons axiaux
DE19755386C2 (de) Hydrostatische Maschine mit einer drehbar gelagerten Zylindertrommel und einer einstellbaren Schwenkscheibe
EP0525507B1 (fr) Dispositif de réglage d'un actionneur pour régler la cylindrée d'une machine hydrostatique
DE3503437C2 (de) Axial-Kolbenmaschine
DE19620654B4 (de) Verstellbare Axialkolbenmaschine in Schrägscheibenbauweise
DE4202631C2 (de) Axialkolbenmaschine, insbesondere Hydropumpe der Schiefscheibenbauart oder der Schrägachsenbauart, deren Durchsatzvolumen durch eine Einstellvorrichtung einstellbar ist
DE3935800C2 (de) Einstellbare Axialkolbenmaschine in Schrägscheibenbauweise
DE3430362A1 (de) Radialkolbenmotor
EP4104966B1 (fr) Dispositif de serrage
EP1156212A2 (fr) Machine à piston alternatif avec des chemises de cylindre pour les pistons
DE2731497A1 (de) Radialkolbenmaschine mit verstellbarem exzenter
DE2437681A1 (de) Vorrichtung zum einstellen des oeffnungsweges der traegerplatte fuer die bewegliche formhaelfte einer kunststoffgiessmaschine
DE2630617C2 (de) Steuerventil für hydraulische Hilfskraftlenkungen
DE2851022C2 (de) Hydraulische Hilfskraftlenkung für Fahrzeuge
EP0074496A1 (fr) Dispositif de vanne, en particulier pour machine à moulage sous pression
DE102021124684A1 (de) Axialkolbenmaschine mit Steuerventil zur Einstellung des Schrägwinkels der Schrägscheibe

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

17P Request for examination filed

Effective date: 20051018

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE SK

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT SE SK

17Q First examination report despatched

Effective date: 20060614

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE SK

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20070718

REF Corresponds to:

Ref document number: 502004004376

Country of ref document: DE

Date of ref document: 20070830

Kind code of ref document: P

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070718

26N No opposition filed

Effective date: 20080421

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071018

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20120327

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20130318

Year of fee payment: 10

Ref country code: FR

Payment date: 20130329

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20140523

Year of fee payment: 11

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20140329

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20141128

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140331

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140329

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140329

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004004376

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151001