EP2531721A2 - Machine à pistons axiaux et disque de commande - Google Patents

Machine à pistons axiaux et disque de commande

Info

Publication number
EP2531721A2
EP2531721A2 EP11701017A EP11701017A EP2531721A2 EP 2531721 A2 EP2531721 A2 EP 2531721A2 EP 11701017 A EP11701017 A EP 11701017A EP 11701017 A EP11701017 A EP 11701017A EP 2531721 A2 EP2531721 A2 EP 2531721A2
Authority
EP
European Patent Office
Prior art keywords
pressure
field
relief
axial piston
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11701017A
Other languages
German (de)
English (en)
Inventor
Josef Kopecki
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 EP2531721A2 publication Critical patent/EP2531721A2/fr
Withdrawn legal-status Critical Current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
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0647—Particularities in the contacting area between cylinder barrel and valve plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0655—Valve 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
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve 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
    • F04B1/2042—Valves

Definitions

  • the invention relates to an axial piston machine according to the preamble of
  • Claim 1 and suitable for such axial piston machine control mirror.
  • Axial piston machine is preferably designed to be adjustable and has a
  • Cylinder drum in which a plurality of cylinder bores is formed, in which pistons are guided axially displaceable.
  • end portions of the pistons abut against a swash plate, the
  • Swivel angle for adjusting the delivery / absorption volume can be made adjustable.
  • Each of the pistons delimits a cylindrical space in sections, which can be connected alternately to a high-pressure and low-pressure connection formed in a connecting plate via a control mirror abutting the cylindrical drum during rotation of the cylindrical drum.
  • Such axial piston machine can both as a hydraulic pump and as
  • the cylinder drum is pressed with a comparatively high force against the fixed control mirror, so that during operation of the
  • Axial piston machine carried out on the end face of the cylinder drum an axial projection, whose end face is subjected to high pressure, so that the
  • Cylinder drum is hydrostatically supported on the control mirror.
  • the face of the Ring projection thus acts as a relief field, which counteracts the contact force of the cylinder drum and thus reduces wear.
  • the relief fields are formed in different geometry as a pressure medium acted projections or grooves.
  • the cylinder drum may already lift off the control plate at low rotational speeds and thus cause a malfunction of the axial piston engine come.
  • the discharge field for a motor is smaller than that for a pump.
  • Operating conditions can be used as a motor.
  • the present invention seeks to provide an axial piston machine, which in wide operating ranges both as a motor and as a pump can be used.
  • Another object of the invention is to provide a control plate suitable for such an axial piston machine.
  • the axial piston machine has a rotatably mounted cylinder drum, in which a plurality of cylinder chambers is formed, which is bounded in each case by a piston.
  • the cylinder drum is located on the front side of a control mirror, via which the cylinder chambers during rotation alternately with high or low pressure can be connected. In the contact area between the cylinder drum and the
  • Control mirror is a relief field for reducing the surface pressure between the cylinder drum and control mirror provided. According to the invention this
  • control unit is designed with a switchable or continuously adjustable valve device via which the Relief field with low pressure, with high pressure or other pressure can be acted upon to provide the desired discharge.
  • a main relief field is provided in addition to the controllable discharge field, wherein the discharge field is switched without pressure in engine operation.
  • the sum of the effective areas of the relief field and the main relief field is slightly larger than that
  • these relief surfaces are formed on the control mirror. This has the advantage that the relief surface does not rotate and thus is stationary with respect to the high-pressure region, so that asymmetric relief field geometries can be realized, which are designed with regard to the optimal discharge.
  • Control mirror is executed, in which the high-pressure and low-pressure control kidneys open.
  • the relief field may then be arranged radially offset from the high-pressure control.
  • the pressure medium connection between main relief field and discharge field can also be done externally via the valve device.
  • each direction of rotation can be assigned a discharge field, which are then preferably arranged diametrically opposite each other.
  • control device with a device for detecting the pressure fluid flow direction and the position of the
  • control device can be detected whether the hydraulic machine runs in pump mode or in engine operation and then according to the discharge field with high pressure or low pressure are applied to control the appropriate discharge.
  • Another advantage of the invention is that the relief force can be steplessly controlled by appropriate pressure control and design of the relief surfaces, so that a leakage oil flow, the efficiency of
  • Hydraulic machine the wear of the hydraulic machine and the unwanted lifting of the cylinder in the sense of a "Condition Monitoring" monitored and the hydraulic machine can be controlled accordingly.
  • a cylinder lift-off protection can also be realized via the controllable relief field so that housing pressure peaks can be reduced or prevented.
  • Figure 1 is a schematic longitudinal section through an adjustable
  • Figure 2 is a control mirror of the axial piston machine of Figure 1 in a plan view and a sectional side view;
  • Figure 3 is a circuit diagram for controlling a discharge field of the control mirror of Figure 2;
  • Figure 4 shows a variant of a control mirror with appropriate control of
  • Figure 5 is a modification of the embodiment of Figure 4.
  • Figure 6 shows a variant of the embodiment of Figure 3 for the realization of a Zylinderabhebêt
  • Figure 7 shows a control mirror with two controllable discharge fields
  • FIG. 8 shows an electro-hydraulic control with the function of the embodiment of FIG. 7.
  • Figure 1 shows a highly simplified sectional view of an axial piston machine of the type A10VO, the structure of which is explained only to the extent necessary for the understanding of the invention.
  • the axial piston machine 1 according to FIG. 1 shows a highly simplified sectional view of an axial piston machine of the type A10VO, the structure of which is explained only to the extent necessary for the understanding of the invention.
  • the axial piston machine 1 according to FIG. 1 shows a highly simplified sectional view of an axial piston machine of the type A10VO, the structure of which is explained only to the extent necessary for the understanding of the invention.
  • the axial piston machine 1 according to FIG. 1 shows a highly simplified sectional view of an axial piston machine of the type A10VO, the structure of which is explained only to the extent necessary for the understanding of the invention.
  • the axial piston machine 1 according to FIG. 1 shows a highly simplified sectional view of an axial piston machine of the type A10VO, the structure of which is explained only to the extent necessary for the understanding of the invention.
  • the axial piston machine 1 has an engine 2 with a cylinder drum 4, in whose cylinder bores 6 each have a piston 8 is guided axially displaceable. Each piston 8 defines with the cylinder bore 6 a cylinder space 10.
  • End face 12 of the cylinder drum 4 is supported on a control plate 14, via whose high-pressure control kidneys 16 and low-pressure control kidneys 18 the cylinder chambers 10 alternate with one executed in a connection plate 20
  • High pressure port 22 and low pressure port 24 are connectable.
  • the engine 2 further has a shaft 26, depending on the operating mode as
  • the shaft 26 is rotatably connected to the cylinder drum 4 and mounted on a bearing assembly 28, for example, angular contact bearings in a housing 30 of the axial piston machine 1, the front side by the
  • Connection plate 20 is closed.
  • a piston foot 34 of each piston 8 is spherical and hingedly connected to a shoe 36, which slides on the obliquely inclined swash plate 32.
  • the adjustment of the angle of attack of the swash plate 32 and thus the stroke of the piston 8 is adjusted via an adjusting device 38, which consists essentially of a control cylinder 40 and a return device 42. The latter acts on the swash plate 32 in the direction of its maximum adjustment angle.
  • the adjustment of the swash plate 32 is carried out by pressurizing the actuating cylinder 40, so that the delivery / absorption volume can be adjusted by dividing the swash plate 32 in a position radially to the shaft axis to 0.
  • Swash plate 32 runs in pump mode. By pivoting the swash plate 32 beyond 0, then the pump operation can be adjusted, this
  • FIG. 2 shows a plan view of the cylinder drum 4 ago on an embodiment of the control mirror 14, as it is used in a construction according to Figure 1.
  • FIG. 2 shows a section along the line A-A, this sectional view not showing a true-to-scale view but being exaggerated in the vertical direction in relation to the real design in order to facilitate understanding.
  • the control mirror 14 is annular and surrounds with his
  • Terminal plate 20 is connected to the ND terminal 24.
  • Embodiment 5 five spaced apart HD-Steuoscopic 16
  • Transition region between the LP control kidney 18 and the web 46 and the HD control kidney 16 and the web 48 is formed in each case a damping slot 50 and 52, via which the Um tenuvorgang in the region of the webs 46, 48 is attenuated.
  • the pistons are in their upper and lower dead center.
  • annular projection 54 is formed in the region formed by the kidneys 16, 18, whose annular end face 56 forms a main relief field 56, along which the end face 12 of the cylinder drum 4 slides.
  • a relief field 58 projecting towards the cylinder drum 4 is formed in the region of the outer circumference of the control plate 14, which in the illustrated variant is designed as an approximately rectangular, slightly curved frame structure which encompasses a pocket 60.
  • the axial height of the relief field 58 corresponds to the axial height of the main relief field 56, so that the end face 12 of the cylinder drum 4 also slides along the relief field 58.
  • a pressure medium supply for the pocket 60 is indicated by a point 62.
  • a pressure medium supply for the pocket 60 is indicated by a point 62.
  • This relief is essentially determined by the annular surface of the projection 54, so that a comparatively simple adjustment of the unloading force by variation of the inner and outer diameter of the projection 54 is possible.
  • the much smaller relief surface 58 can also be acted upon by the indicated own pressure medium supply 62 or by the pressure medium connection to the main relief field 56 with high pressure, so that this much smaller discharge field also contributes to the relief of the cylinder drum 4.
  • the relief field 58 via a suitable
  • Valve device are switched depressurized in engine operation, so that then only the main relief field 56 contributes to cylinder relief and thus the above-mentioned lifting the cylinder drum 4 can be avoided.
  • FIG. 3 shows a variant in which the pressure applied to the HP control 16 is picked off via a supply channel 64 between a constant throttle 66 and an adjustable throttle 72 (pressure divider), which are connected in series.
  • the pressure in the supply line 64 which leads to the relief field 58 more precisely into the pocket 60 gripped by the latter, can be adjusted.
  • This pressure may correspond to the high pressure (variable throttle 72 is fully closed) or may occupy almost any pressure that is less than the high pressure and greater than the low pressure ND.
  • the pressure in the supply channel 64 can be displayed via a pressure indicator 68.
  • a discharge channel 70 which is connected to a low-pressure pressure chamber leading ND and in which the variable throttle 72 is arranged.
  • a relief valve 74 is arranged, which is designed in this embodiment as a 2/2-way valve and is biased by a spring into an open position and mechanically switchable to a blocking position to the
  • FIG. 1 A concrete solution to this concept is shown in dashed lines in FIG.
  • the return cylinder 42 is extended in the pump operation in the direction "-a" in Figure 1.
  • the swash plate 32 is pivoted on retraction of the return cylinder 32 in the direction "-a”.
  • a piston 41 retracts.
  • the cylinder-side end portion of the piston 41 is shown in dashed lines in the illustration in FIG. Its end face 43 is limited inside the
  • Supply channels 64 is shut off to the HD. D. h., The piston 41 of the
  • Restoring cylinder 42 takes over in cooperation with the radial bore 47, the function of the switching valve shown in Figure 3 74.
  • the pressure medium connection of the relief field 58 is interrupted to high pressure and the pressure medium can flow through the relief throttle 72 to the low pressure.
  • the above-described channels 64, 70 may be formed in any way in the control mirror 14, the cylinder drum 4, the connection plate 20 or in the housing 30. Of course, it is also possible to perform the switching of the relief valve 74 in other ways, for example electrically / electro-hydraulically via a controller.
  • FIG 4 shows an embodiment of the control mirror 14, in which the
  • Main discharge field 56 is connected directly to the discharge field 58, i.
  • the right in Figure 2 right inner circumferential wall of the frame-shaped relief field 58 coincides with the corresponding portion of
  • the discharge channel 70 opens in this variant directly into the pocket 60 a.
  • the pocket 60 is filled with pressure medium over the region of the relief field 58 which faces the high pressure side. The pressure medium discharge takes place over the
  • the relief valve 74 is disposed in the discharge channel 70 in this embodiment and biased by the spring in a locking position to the
  • Relief field 58 to be pressurized in pump mode with high pressure.
  • the relief valve 74 is switched to the open position, so that the
  • Relief field 58 is relieved of pressure, while the main relief field 56 continues to be acted upon by the HD-Steu Schlieren 16 high pressure.
  • an electrically or electro-hydraulically operated relief valve 74 may be used. This is in the illustrated embodiment, a proportionally adjustable pressure limiting valve for controlling the pressure in the discharge channel 70 and thus the discharge field 58. Of course, such a proportionally adjustable control valve can also be used in the other solutions described here.
  • Control mirror 14 In this case, the cylinder drum 4 tilts due to the frictional forces of the extending piston 8 on the low pressure side to the high pressure side, i. 2, 3 and 4 left side of the control mirror 14. This tilting movement is mitigated by the relief effective at pump discharge area 58, so that the cylinder drum 4 is hydrostatically supported and thus the Abhebeloomiere is shifted upwards.
  • FIG. 6 shows a modification of the exemplary embodiment according to FIG. In this variant, the supply channel 64 via a message channel 80 on the
  • the hydraulic units which are preferably designed as constant units, are operated in 4-quadrant operation. This means that when reversing high-pressure and low-pressure side at the connections of the hydraulic machine and also change according to the flow direction in the hydraulic machine. For the solution according to the invention this requires, accordingly, to detect the flow direction and the high-pressure / low-pressure side and, depending on these characteristics, the
  • FIG. 7 shows a hydraulic embodiment of such a solution.
  • the control mirror 14 with two diametrically opposed discharge fields 58a, 58b executed, the basic structure of the
  • control kidney arranged on the right in the figures is not a comparatively long circle segment section but like the HD control kidneys 16 by a plurality of smaller spaced-apart ones
  • 58a depressurized. This can be done for example by a circuit according to Figure 7, which has a symmetrical structure.
  • the control kidneys 16, 18 are connected via the connection plate 20 shown in Figure 1 with the two terminals A, B, said pressure medium connection via channels 84, 86 takes place, in which respective apertures 88, 90 are arranged.
  • the pressure in the channels 84, 86 is fed to the inputs of a shuttle valve 91, whose Output is connected to the supply channel 64, in which the throttle 66 is arranged.
  • the supply channel 64 branches into two supply channel branches 64a, 64b, which each lead to the inlet of a relief valve 74a, 74b. This is designed as a 3/2-way valve, wherein an output terminal A via a channel portion 92 a, 92 b with the respective
  • Relief field 58a, 58b or more specifically the embraced pocket 60a, 60b is connected.
  • the third port T is connected to the low pressure ND.
  • the relief valve 74a, 74b is biased to a home position in which the
  • Pressure port P is shut off and the channel portion 92 a, 92 b is connected to the low pressure ND (tank).
  • the two relief valves 74a, 74b are each acted upon by the pressure in the associated channel 84, 86, which is tapped off via a control line 96a, 96b.
  • bypass passage 98 a, 98 b which bypasses the respective aperture 88, 90 and in which a pilot-operated check valve 100 a, 100 b is arranged, by the pressure in the other Bypass channel 98b, 98a is unlocked.
  • the check valve 100a, 100b allows fluid flow toward the ports A and B, respectively, bypassing the respective orifice 88, 90.
  • Bypass channels 98a, 98b in the working channel 84, 86 is tapped via a control channel 102a, 102b and reported to a closing direction effective control surface of the other relief valve 74a, 74b.
  • the supply channel 64 is connected to the low pressure ND (tank) downstream of the branch to the channel sections 64a, 64b via the variable throttle 72.
  • the axial piston machine 1 runs in the pump mode, wherein the high pressure is applied to the port A and the port B is the suction side (ND). Due to the higher pressure in the channel 84, the relief valve 74 a is switched to its passage position in which the supply channel section 64 a with the Channel section 92a is connected. The pressure medium can then from the high pressure side via the shuttle valve 91, the supply channel 64 and the
  • controlled check valve 100b is applied to both sides of the relief valve 74b, the same control pressure, so that it is biased by the force of the spring in its basic position in which the relief field 58b is relieved to the ND out.
  • the direction of flow is detected by the pressure drop across the orifice 88 (or 90).
  • Pressure side changes and flow direction changes (pump / motor) designed.
  • the relief surfaces 58 a, 58 b are controlled.
  • FIG. 8 shows an electrohydraulic solution with respect to FIG.
  • the structure of the control mirror 14 is the same as in the embodiment of FIG. 7, i. two relief fields 58a, 58b are provided and the high-pressure or low-pressure side control kidneys 16, 18 are implemented by a total of five comparatively small kidneys located on a common pitch circle. Depending on the mode of operation of the axial piston machine, these relief fields 58a, 58b can be controlled via a controller.
  • the ports A, B are again connected via channels 84, 86 in the connection plate 20 with the high pressure side and the low pressure side.
  • the pressure in these two Ducts 84, 86 is applied to the inputs of the shuttle valve 91, whose output is connected via the supply channel 64 and the throttle 66 to the supply channel branches 64a, 64b, which lead to one of the discharge fields 58a, 58b.
  • the supply channel branches 64a, 64b are connected to the ND via the discharge channel 70 and the variable throttle 72.
  • electrohydraulically adjustable relief valve 74a, 74b provided in
  • Operating mode is controlled to pressurize or relieve the respective discharge field 58a, 58b with pressure.
  • the activation of the relief valves 74a, 74b can also take place in order to prevent tilting or lifting of the cylinder drum 4 or at least into higher ones
  • the two relief valves 74a, 74b are also designed as 2/2-way valves, the relief fields 58a, 58b are placed in the spring-biased home position of these relief valves 74a, 74b to low pressure. In line with each
  • Relief valve 74a, 74b, a 2/2-way switching valve 102a, 102b is provided, which is biased into a closed position and which is switchable via the pressure in the channels 84, 86. This pressure is tapped via a control channel 104a, 104b.
  • the switching valve 102a is switched and the relief field 58a is changed over the shuttle valve 91, the throttle 66, the supply port 64, the
  • Supply channel section 64a as well as the controlled via the control
  • the flow direction of the pressure medium is on the direction of rotation of the
  • Cylinder drum 4 determined. This is detected by a suitable sensor and reported to the controller, so that these depending on the direction of rotation or more specifically, from the fluid flow direction and operating state, it can deliver an appropriate signal to the supply valves 74a, 74b.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

L'invention concerne une machine à pistons axiaux comportant une zone de décharge pouvant être commandée en fonction du mode de fonctionnement.
EP11701017A 2010-02-05 2011-01-20 Machine à pistons axiaux et disque de commande Withdrawn EP2531721A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010006895 DE102010006895A1 (de) 2010-02-05 2010-02-05 Axialkolbenmaschine und Steuerspiegel
PCT/EP2011/000228 WO2011095280A2 (fr) 2010-02-05 2011-01-20 Machine à pistons axiaux et disque de commande

Publications (1)

Publication Number Publication Date
EP2531721A2 true EP2531721A2 (fr) 2012-12-12

Family

ID=44316456

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11701017A Withdrawn EP2531721A2 (fr) 2010-02-05 2011-01-20 Machine à pistons axiaux et disque de commande

Country Status (3)

Country Link
EP (1) EP2531721A2 (fr)
DE (1) DE102010006895A1 (fr)
WO (1) WO2011095280A2 (fr)

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JP5982115B2 (ja) * 2011-11-25 2016-08-31 Ｋｙｂ株式会社 斜板式ピストンポンプ
DE102013208454A1 (de) 2013-05-08 2014-11-13 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit einer Zylindertrommel mit schräg zu deren Axialrichtung gelagerten Arbeitskolben und einem ebenen Steuerspiegel
JP6246582B2 (ja) * 2013-12-16 2017-12-13 日立建機株式会社 液圧回転機械
DE102014206911A1 (de) 2014-04-10 2015-10-15 Robert Bosch Gmbh Schrägscheibenmaschine
DE102015120767A1 (de) 2015-11-30 2017-06-01 Robert Bosch Gmbh Axialkolbenmaschine
DE102015224129A1 (de) 2015-12-03 2017-06-08 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
DE102015224132A1 (de) 2015-12-03 2017-06-08 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit Steuerscheibe
DK3417171T3 (da) * 2016-06-06 2019-12-02 Daniel Dyminski Hydraulisk pumpe med indløbsskærm
DE102017210010A1 (de) * 2017-06-14 2018-12-20 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine und Steuerplatte für die Axialkolbenmaschine
CN107859609A (zh) * 2017-12-08 2018-03-30 徐工集团工程机械有限公司 配流盘、轴向柱塞泵及轴向柱塞马达
DE102024203426A1 (de) * 2024-04-15 2025-10-16 Robert Bosch Gesellschaft mit beschränkter Haftung Hydromaschine mit hydrostatisch entlastetem Gleitlager

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Also Published As

Publication number Publication date
DE102010006895A1 (de) 2011-08-11
WO2011095280A2 (fr) 2011-08-11
WO2011095280A3 (fr) 2012-03-08

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