EP3168469B1 - Hydrostatische axialkolbenmaschine in schrägachsenbauweise - Google Patents

Hydrostatische axialkolbenmaschine in schrägachsenbauweise Download PDF

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Publication number
EP3168469B1
EP3168469B1 EP16195273.4A EP16195273A EP3168469B1 EP 3168469 B1 EP3168469 B1 EP 3168469B1 EP 16195273 A EP16195273 A EP 16195273A EP 3168469 B1 EP3168469 B1 EP 3168469B1
Authority
EP
European Patent Office
Prior art keywords
piston
drive flange
ball
axis
axial piston
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.)
Not-in-force
Application number
EP16195273.4A
Other languages
German (de)
English (en)
Other versions
EP3168469A1 (fr
Inventor
Martin Bergmann
Lukas Krittian
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.)
Linde Hydraulics GmbH and Co KG
Original Assignee
Linde Hydraulics GmbH and Co KG
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
Priority claimed from DE102016100920.2A external-priority patent/DE102016100920A1/de
Application filed by Linde Hydraulics GmbH and Co KG filed Critical Linde Hydraulics GmbH and Co KG
Publication of EP3168469A1 publication Critical patent/EP3168469A1/fr
Application granted granted Critical
Publication of EP3168469B1 publication Critical patent/EP3168469B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining means
    • 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
    • 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
    • F01B3/0055—Valve means, e.g. valve plate
    • F01B3/0061—Conical valve means
    • 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
    • F01B3/0082—Details
    • F01B3/0085—Pistons
    • F01B3/0088—Piston shoe retaining means

Definitions

  • the invention relates to a hydrostatic axial piston machine in oblique-axis construction with a about a rotation axis rotatably disposed within a housing drive shaft, which is provided with a drive flange, and with a rotatable about a rotation axis disposed within the housing of the axial piston cylinder cylinder, wherein the cylinder drum is provided with a plurality Kolbenaus founded ausinskyept in each of which a piston connected to the drive flange is arranged longitudinally displaceable, wherein the pistons are hinged to the drive flange and for articulated attachment of the piston to the drive flange each a ball joint connection is provided, consisting of a hollow spherical receiving cup in an end face of the drive flange and a Ball head is formed on the piston, wherein the hollow spherical receiving shell in the end face of the drive flange is designed with a loop of greater than 180 ° degree of the ball head and on the S end face of the drive flange is formed
  • the piston arranged longitudinally displaceably in the cylinder drum are usually fastened by means of a ball joint to the drive flange of a drive shaft.
  • the piston forces are based here on the piston on the drive shaft located on the drive flange and generate a torque.
  • a ball and socket joint is used, which consists of a hollow spherical receiving shell in an end face of the drive flange and a ball head, which is arranged on the piston and is inserted into the receiving shell of the drive flange.
  • the ball heads of the pistons are to be locked in the respective receiving shell of the drive flange in order to secure the pistons from falling out of the receiving shell of the drive flange during operation of the axial piston machine in a bent-axis design.
  • the hollow spherical receiving shells are designed with a loop of greater than 180 ° degrees, so that the receiving shells of the drive flange wrap around the Kugeläquator the ball to the ball heads of the piston.
  • the piston In order to use the piston with the balls and thus the ball heads in the hollow spherical receiving shell of the drive flange, provided with the ball ball head of the piston with a cylindrical surface, for example by flattening or processing of the ball head, provided so that the ball head in a certain position can be introduced by means of the cylindrical surfaces in the kugelkalottenförmigen receiving tray and then secured by tilting in the receiving tray.
  • the manufacture of the components simplifies this and there is a simple assembly of the piston with the ball heads in the receiving shells of the drive flange.
  • the hollow spherical receiving shell is in this case limited by a circular opening, which in one parallel to the end face of the drive flange and with respect to the end face of the drive flange is set back by a small amount level.
  • the chamfer forms a conical surface, which connects the circular opening of the hollow spherical receiving tray with the end face of the drive flange.
  • the hollow spherical receiving tray with this limiting chamfer thus form a positive-locking in the drive flange, with which the pistons are secured against falling out.
  • the center of the chamfer and the center of the hollow spherical receiving tray to the axis of rotation of the drive flange on the same radial distance.
  • the chamfer is thus arranged symmetrically on the receiving tray, so that when viewed on the receiving tray over the circumference results in an equal conical surface.
  • the present invention has for its object to provide a hydrostatic axial piston machine in Schrägachsenbauweise of the aforementioned type, in which the strength of the piston can be increased in a simple manner.
  • the hollow spherical receiving cup limiting bevel to the hollow spherical receiving tray is displaced radially outward, wherein the center of the chamfer is radially spaced from the center of the hollow spherical receiving tray with respect to the axis of rotation of the drive flange.
  • the chamfer on the hollow spherical receiving shells which limits the corresponding hollow spherical receiving shell on the drive flange, moved radially outward.
  • a displacement of the hollow spherical receiving bowl defining bevel radially outward can be achieved in a simple manner, when the center of the chamfer is radially spaced from the center of the hollow spherical receiving tray with respect to the axis of rotation of the drive flange.
  • the piston has a conical section with which the piston is arranged inside the piston recess, wherein a cylindrical section is formed between the conical section and the ball head.
  • the ball head is provided according to a preferred embodiment of the invention with a cylindrical surface which is arranged in the region of the equator of the ball head.
  • the axial piston machine has a swivel angle of up to 40 ° or a swivel angle of more than 40 °.
  • the enlargement of the diameter of the cylindrical portion of the piston due to the radially outwardly shifted bevel on the hollow spherical receiving shells of the drive flange makes it possible, with sufficiently high strength of the piston even with an axial piston machine with a swivel angle of up to 40 ° or a swivel angle of more as 40 ° still a corresponding clearance between the piston and the positive down device is ensured on the drive flange.
  • FIG. 1 a hydrostatic axial piston machine 1 of the prior art in a bent-axis design is shown in a longitudinal section.
  • the axial piston machine 1 designed as a bent-axis machine has a housing 2 in which a drive shaft 4 provided with a drive flange 3 is rotatably mounted about a rotation axis 6 by means of a bearing device 5.
  • a cylinder drum 7 is arranged in the housing 2, which is arranged rotatably about a rotation axis 8 with a plurality of concentric with a rotation axis 8 of the cylinder drum 7 arranged KolbenausEnglishept 9, in each of which a piston 10 is arranged longitudinally displaceable.
  • the axis of rotation 6 of the drive shaft 4 intersects the axis of rotation 8 of the cylinder drum 7 at the point of intersection SP.
  • the cylinder drum 7 abuts with an end face 7a on a control body 12 provided with a control surface 11. Between the control surface 11 of the control body 12 and the end face 7a of the cylinder drum 7, a sliding bearing is formed, wherein the cylinder drum 7 rotates about the axis of rotation 8 in the operation of the oblique axis machine at about the rotation axis 8 rotating cylinder drum 7 with the end face 7a on the control surface 11 of Housing 2 arranged control body 12 along.
  • kidney-shaped control recesses are formed to control the supply and discharge of pressure medium in the displacers V formed by the KolbenausEnglishept 9 and the piston 10, the inlet port 13 and an outlet port 14 of the axial piston machine. 1 form.
  • the cylinder drum 7 is provided with a control opening 15 on each piston recess 9.
  • the in the FIG. 1 illustrated axial piston machine 1 is designed as a constant machine with a constant displacement volume.
  • the inclination angle of the rotation axis 8 of the cylinder drum 7 with respect to the rotation axis 6 of the drive shaft 4 is fixed.
  • the cylinder drum 7 is supported on a support pin 20 hingedly connected to the drive flange 3 by a ball joint, wherein on the support pin 20, a spring 21 is further supported, which presses the cylinder drum 7 provided with the control surface 11 control body 12.
  • the support pin 20 is arranged concentrically to the axis of rotation 8 of the cylinder drum 7 and arranged in a corresponding receiving bore 22 of the cylinder drum 7.
  • the drive shaft 4 provided with the drive flange 3 is mounted in the housing 2 in a flying manner by means of the bearing device 5.
  • the bearing device 5 comprises two rolling bearings 5a, 5b, which are arranged in the axial direction between the drive flange 3 and a protruding from the housing 2 shaft end of the drive shaft 4.
  • the drive shaft 4 is provided with a torque transmission means 23, for example a spline.
  • the rolling bearing 5a is in this case arranged facing the cylinder drum 7.
  • the rolling bearing 5b is arranged facing the protruding from the housing 2 shaft end of the drive shaft 4.
  • the pistons 10 are each hinged to the drive flange 3.
  • a ball joint 30 formed as a spherical joint is respectively formed between the respective piston 10 and the drive flange 3.
  • the ball-and-socket joint 20 is formed by a spherical ball head 10a of the piston 10 and a hollow spherical receiving shell 3a in the cylindrical drum 7 facing end surface 3b of the drive flange 3, in which the piston 10 is fixed to the ball head 10a.
  • the pistons 10 each have a conical section 10b with a lateral surface formed as a conical surface, with which the piston 10 is arranged in the piston recess 9 of the cylinder drum 7. Between the cone portion 10b and the spherical ball head 10, the piston 10 has a cylindrical portion 10c.
  • a sealing means 33 for example a piston ring or a plurality of piston rings, is arranged on the conical section 10b of the piston 10.
  • a hold-down plate 35 with openings 36 for the ball heads 10a of the pistons 10 and rings adapted specifically to the ball heads 10a of the pistons 10 are provided.
  • the rings 37 are inserted into a groove 38 which is formed on the receiving dish 3a of the drive flange 3, and held in the groove 38 via the hold-down plate 35.
  • the hold-down plate 35 is fastened thereto by means of screw 39 to the drive flange 3.
  • FIG. 2 shows a section of a further axial piston machine 1 of the prior art in the area of the articulated fastening of the pistons 10 on the drive flange 3.
  • the axial piston machine 1 of FIG. 2 differs from the axial piston 1 of the FIG. 1 by the hold-down device with which the pistons 10 are secured against falling out of the hollow spherical receiving dish 3a of the drive flange 3 during operation of the axial piston machine 1 in a bent-axis design.
  • a positive holding-down device in which the hollow spherical receiving dish 3a in the end face 3b of the drive flange 3 is designed with a wrap of greater than 180 ° degree of the ball head 10a of the piston 10.
  • the provided with the ball ball head 10a of the piston 10 with a cylindrical surface 40 for example, by flattening or processing of the ball head, provided, so that the ball head 10 b can be inserted in a certain position by means of the cylindrical surfaces 40 in the spherical cap-shaped receiving tray 3 a and then secured by tilting in the receiving tray 3 a.
  • the cylindrical surface 40 is arranged symmetrically to an equatorial line 45 of the ball on the ball head 10 a of the piston 10.
  • a hollow spherical receiving cup 3a defining bevel 50.
  • the chamfer 50 generates with the inner edge of a hollow spherical receiving dish 3a delimiting circular opening 51, which is parallel to the end face 3b of the drive flange 3 and opposite the end face 3b of the drive flange 3 by a small amount back plane E1.
  • the diameter of the circular opening 51 is smaller than the diameter of the ball of the ball head 10a of the piston 10.
  • the chamfer 50 forms a conical surface 52 which connects the circular opening 51 of the hollow spherical receiving tray 3a with the end face 3b of the drive flange 3.
  • the hollow spherical receiving dish 3a with this limiting chamfer 50 thus form a positive-locking in the drive flange 3, with which the pistons 10 are secured against falling out.
  • the center MP1 of the chamfer 50 and the center MP2 of the hollow spherical receiving shell 3a have the same radial distance from the axis of rotation 6 of the drive flange 3 in the radial direction R.
  • the chamfer 50 is thus arranged symmetrically on the receiving tray 3a, so that on the receiving tray 3a - seen in the circumferential direction of the circular opening 51 - results in an equal sized conical surface 52.
  • the diameter D1 of the cylindrical portion 10c of the piston 10 is limited by the conical surface 52 on the receiving tray 3a, to allow a clearance between the cylindrical portion 10c of the piston 10 and the conical surface 52, which forms part of the positive-locking down, during operation of the axial piston machine 1, to ensure the drive flange 3 and to avoid striking the piston 10 with the cylindrical portion 10c on the conical surface 52 of the drive flange 3.
  • the axial piston machine 1 of the prior art has a pivot angle ⁇ of 40 °.
  • a large swivel angle ⁇ results in a small diameter D1 of the constricted cylindrical portion 10c of the piston 10 to still ensure a corresponding clearance between the piston 10 and the conical surface 52 on the drive flange 3.
  • FIGS. 3 to 6 an axial piston machine 1 according to the invention is shown. With the FIGS. 1 and 2 the same components are provided with the same reference numerals.
  • the axial piston machine 1 of the invention FIGS. 3 to 6 is with one positive-locking device for the piston 10 analogous to the FIG. 2 provided and different from the FIG. 2 by the arrangement of the chamfer 50.
  • FIGS. 3 to 6 is analogous to the FIG. 2 a positive holding-down device is provided, in which the hollow-spherical receiving dish 3a in the end face 3b of the drive flange 3 is designed with an encircling greater than 180 ° degree of the ball head 10a of the piston 10.
  • the provided with the ball ball head 10a of the piston 10 with a cylindrical surface 40 for example, by flattening or processing of the ball head, provided, so that the ball head 10 b can be inserted in a certain position by means of the cylindrical surfaces 40 in the spherical cap-shaped receiving tray 3 a and then secured by tilting in the receiving tray 3 a.
  • the cylindrical surface 40 is arranged symmetrically to an equatorial line 45 of the ball on the ball head 10 a of the piston 10.
  • the bevel 50 which limits the hollow spherical receiving dish 3a, as in the Figures 3 . 4 and 6 is shown in more detail - moved to the hollow spherical receiving tray 3a in the radial direction R of the axis of rotation 6 of the drive flange 3 seen radially outward.
  • the chamfer 50 is thus arranged eccentrically and off-center on the receiving tray 3a.
  • the midpoint MP1 of the chamfer 50 is in each case in the middle life ME of the corresponding receiving tray 3a.
  • the chamfer 50 is thus arranged eccentrically and off-center on the receiving tray 3a.
  • the chamfer 50 which is displaced in a radially outward direction, produces with the inner edge a circular opening 51 delimiting the hollow spherical receiving dish 3a, which lies in a plane E2 inclined to the plane in which the end face 3b of the drive flange 3 is arranged.
  • the diameter of the circular opening 51 is smaller than the diameter of the ball of the ball head 10 a of the piston 10.
  • the chamfer 50 which is displaced radially outwards, forms a conical surface 52, which connects the circular opening 51 of the hollow-spherical receiving dish 3a to the end face 3b of the drive flange 3.
  • the hollow spherical receiving dish 3a with this limiting chamfer 50 thus form a positive-locking in the drive flange 3, with which the pistons 10 are secured against falling out.
  • the conical surface 52 which is generated by the radially outwardly shifted bevel 50, is - as in the FIG. 6 is more apparent - viewed differently on the receiving tray 3a in the circumferential direction of the circular opening 51.
  • the displacement of the chamfer 50 with respect to the hollow spherical recess 3a in the radially outward direction causes the conical surface 52 at the recess 3a in the radially inner region, ie the area facing the axis of rotation 6 is smaller than in the radially outer region, ie the Rotation axis 6 remote area.
  • the enlarged conical surface 52 in the radially outer region of the hollow spherical recess 3a allows the diameter D2 of the cylindrical portion 10c of the piston 10 of the axial piston machine 1 according to the invention, which is bounded by the conical surface 52 on the receiving shell 3a, to be opposite the diameter D1 of the axial piston machine 1 of the prior art according to the FIG. 2 can be increased to a clearance between the cylindrical portion 10c of the piston 10 and the conical surface 52, which forms part of the positive-locking down, in the operation of the axial piston machine 1, on the To ensure drive flange 3 and to avoid striking the piston 10 with the cylindrical portion 10c on the conical surface 52 of the drive flange 3.
  • the increased diameter D2 on the cylindrical portion 10c of the pistons 10 increases the strength of the pistons 10 at this area.
  • the axial piston machine 1 has a pivot angle ⁇ of 40 °. With such a large pivoting angle ⁇ , the increased diameter D2 results in increased strength of the pistons 10 in the constricted cylindrical section 10c.
  • the axial piston machine 1 Due to the increased diameter D2 on the cylindrical portion 10c of the piston 10 and the associated increased strength of the piston 10, the axial piston machine 1 according to the invention can be released in inclined axis design for increased internal and external excitations, causing torsional vibrations between the drive flange 3 and the cylinder drum 7.
  • the axial piston machine 1 according to the invention can be designed as a pump or as a motor.
  • the axial piston machine 1 according to the invention can be designed as a constant machine with a constant displacement volume or as an adjusting machine with a variable displacement volume.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Claims (4)

  1. Machine à pistons axiaux hydrostatique (1) de type à axe oblique comprenant un arbre d'entraînement (4) disposé à l'intérieur d'un boîtier (2) de manière à pouvoir tourner autour d'un axe de rotation (6) qui est pourvu d'une bride d'entraînement (3), et comprenant un tambour de cylindre (7) disposé à l'intérieur du boîtier (2) de la machine à pistons axiaux (1) de manière à pouvoir tourner autour d'un axe de rotation (8), le tambour de cylindre (7) étant pourvu de plusieurs évidements de piston (9) dans lesquels un piston (10) connecté à la bride d'entraînement (3) est à chaque fois disposé de manière déplaçable longitudinalement, les pistons (10) étant fixés de manière articulée à la bride d'entraînement (3) et pour la fixation articulée des pistons (10) à la bride d'entraînement (3), étant à chaque fois prévue une liaison à articulation sphérique (30) qui est formée d'une coque de réception en forme de sphère creuse (3a) dans une surface frontale (3b) de la bride d'entraînement (3) et d'une tête sphérique (10b) sur le piston (10), la coque de réception en forme de sphère creuse (3a) dans la surface frontale (3b) de la bride d'entraînement (3) étant réalisée avec un enveloppement supérieur à 180° degrés de la tête sphérique (10b) et au niveau de la surface frontale (3b) de la bride d'entraînement (3) étant réalisé un biseau (50) limitant la coque de réception en forme de sphère creuse (3a), caractérisée en ce que le biseau (50) limitant la coque de réception en forme de sphère creuse (3a) est déplacé vers la coque de réception en forme de sphère creuse (3a) dans la direction du rayon de l'axe de rotation de la bride d'entraînement vers l'extérieur et est donc disposé de manière excentrique et décentrée au niveau de la coque de réception, le centre (MP1) du biseau (50) étant espacé radialement vers l'extérieur par rapport au centre (MP2) de la coque de réception en forme de sphère creuse (3a) par rapport à l'axe de rotation (6) de la bride d'entraînement (3).
  2. Machine à pistons axiaux hydrostatique selon la revendication 1, caractérisée en ce que le piston (10) présente une portion conique (10b) avec laquelle le piston (10) est disposé à l'intérieur de l'évidement de piston (9), une portion cylindrique (10c) étant réalisée entre la portion conique (10b) et la tête sphérique (10a).
  3. Machine à pistons axiaux hydrostatique selon la revendication 1 ou 2, caractérisée en ce que la tête sphérique (10b) est pourvue d'une surface cylindrique (40) qui est disposée dans la région de l'équateur (45) de la tête sphérique (10b).
  4. Machine à pistons axiaux hydrostatique selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la machine à pistons axiaux (1) présente un angle de pivotement (α) allant jusqu'à 40° un angle de pivotement (α) de plus de 40°.
EP16195273.4A 2015-11-11 2016-10-24 Hydrostatische axialkolbenmaschine in schrägachsenbauweise Not-in-force EP3168469B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015119474 2015-11-11
DE102016100920.2A DE102016100920A1 (de) 2015-11-11 2016-01-20 Hydrostatische Axialkolbenmaschine in Schrägachsenbauweise

Publications (2)

Publication Number Publication Date
EP3168469A1 EP3168469A1 (fr) 2017-05-17
EP3168469B1 true EP3168469B1 (fr) 2019-06-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP16195273.4A Not-in-force EP3168469B1 (fr) 2015-11-11 2016-10-24 Hydrostatische axialkolbenmaschine in schrägachsenbauweise

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EP (1) EP3168469B1 (fr)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4429053C1 (de) 1994-08-16 1995-11-02 Brueninghaus Hydromatik Gmbh Kugelkopf zur Abstützung eines Kolbens einer hydrostatischen Axial- oder Radialkolbenmaschine an deren Hubkörper
EP1631744B1 (fr) 2003-06-11 2007-02-28 Brueninghaus Hydromatik Gmbh Machine a pistons axiaux comportant un element de positionnement decale et came de commande pour une telle machine a pistons axiaux
DE102014104951A1 (de) * 2014-04-08 2015-10-08 Linde Hydraulics Gmbh & Co. Kg Axialkolbenmaschine in Schrägachsenbauweise

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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