EP1843048A2 - Dispositif de vérin - Google Patents

Dispositif de vérin Download PDF

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Publication number
EP1843048A2
EP1843048A2 EP07006623A EP07006623A EP1843048A2 EP 1843048 A2 EP1843048 A2 EP 1843048A2 EP 07006623 A EP07006623 A EP 07006623A EP 07006623 A EP07006623 A EP 07006623A EP 1843048 A2 EP1843048 A2 EP 1843048A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
piston
fluid cylinder
working chamber
line
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
EP07006623A
Other languages
German (de)
English (en)
Other versions
EP1843048B1 (fr
EP1843048A3 (fr
Inventor
Leopold Ing. Reisinger
Johan Ing. Schmollngruber
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.)
Weber Hydraulik GmbH Austria
Weber Hydraulik GmbH Germany
Original Assignee
Weber Hydraulik GmbH Austria
Weber Hydraulik GmbH Germany
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 Weber Hydraulik GmbH Austria, Weber Hydraulik GmbH Germany filed Critical Weber Hydraulik GmbH Austria
Publication of EP1843048A2 publication Critical patent/EP1843048A2/fr
Publication of EP1843048A3 publication Critical patent/EP1843048A3/fr
Application granted granted Critical
Publication of EP1843048B1 publication Critical patent/EP1843048B1/fr
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1466—Hollow piston sliding over a stationary rod inside the cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a fluid cylinder, in particular a double-acting hydraulic cylinder, as described in the preamble of claim 1.
  • a continuously lockable cylinder in which a piston rod has a longitudinal bore extending through the piston with a tooth-like or wave-like profiling of the inner wall into which a stationarily held tube is guided with a rod arranged displaceably therein, wherein the rod has at least one radial and Having parallel to the longitudinal extent of the rod extending ball circulation channel.
  • the object of the invention is to provide a fluid cylinder in which the fixing of the piston or the piston rod takes place in an equally reliable manner, as in the case of the
  • the prior art known solutions the fluid cylinder, however, simple and robust constructed and inexpensive to produce.
  • a fluid cylinder having the features of independent claim 1. It is advantageous that the third working chamber acts in addition to the first working chamber on the piston assembly and thereby replaces a mechanical locking device for fixing the piston.
  • the complex and therefore error-prone means for mechanical locking of the piston are not required in this hydraulically lockable cylinder, but only means that prevent unplanned or unforeseen outflow of pressure fluid from the first and the third working chamber.
  • Such valves for controlling or blocking a pressure medium drainage are proven many times, reliable and at the same time cost.
  • the first and third working chambers can secure each other in their holding function, i.
  • the invention also includes embodiments of the fluid cylinder in which a plurality of piston tubes are guided in corresponding cavities in the piston assembly.
  • the piston tube and the opening have a circular cross-section.
  • the circular cross-sectional shape can be produced with simple means and nevertheless with high accuracy, as a result of which the first working chamber can be reliably sealed against the third working chamber. Furthermore, in the case of a circular cross section, insertion of an additional piston tube seal is easily possible, as a result of which leakages between the first and third working chambers can be largely prevented.
  • the piston assembly is tubular. This is e.g. achievable by the piston rod is formed from a tube.
  • the volume of the third working chamber can be made relatively large, as a result of which the effective area of the third working chamber on the piston arrangement can also be made relatively large.
  • the first and third working chambers act in parallel on the piston assembly; if the pressure drops in one of the two working chambers, a load to be held must be held by the other working chamber, so it is advantageous if the active surfaces of the first and third working chambers on the piston assembly are not too different.
  • a further advantageous embodiment of the fluid cylinder is that the piston tube and the piston assembly are arranged coaxially.
  • the piston tube can also be arranged offset relative to the longitudinal axis of the piston arrangement or of the cylinder, it is advantageous for a uniform distribution of forces and the avoidance of transverse forces and bending moments on the piston arrangement to arrange the piston tube and piston arrangement coaxially.
  • the cross-sectional area of the opening is at least 33%, preferably about 40% of the cylinder cross-sectional area.
  • the pressure in the third working chamber may increase to a maximum of three times the nominal pressure when the outflow from the pressure medium is completely blocked.
  • Another advantage is an embodiment of the fluid cylinder according to another claim, according to which the mechanically limited maximum stroke of the piston assembly is shorter than the maximum effective immersion depth of the piston tube, measured from the opening or the piston tube seal to an end face of the piston tube.
  • the lines are connected to the working chambers via a directional control valve, in particular a 4/3-way valve with a hydraulic unit according to another claim.
  • a directional control valve in particular a 4/3-way valve with a hydraulic unit according to another claim.
  • Such directional valves are also in conventional working cylinders in use and therefore need not be replaced when replacing a conventional working cylinder against the fluid cylinder according to the invention.
  • the operation of the directional control valve is in many cases mechanically by the operator, but may also include other or additional actuators.
  • unlockable check valve in particular check valve is arranged.
  • This can flow to perform a stroke pressure medium into the first and third working chamber and prevents in case of a possible pressure drop, eg by hose breakage, an unforeseen retraction of the piston assembly under the load.
  • the piston assembly must be provided a way to create a flow path for the outflow of pressure medium from the first and third working chamber.
  • the check valve itself is preferably designed as a seat valve, whereby a largely leak-free sealing of the first and third working chamber takes place. Mainly for ball seat elements or cone seat elements are in use.
  • the check valve is unlocked via a control line leading to the second line. Since the second working chamber is pressurized via the second line for carrying out a retraction movement of the piston assembly, this pressure can be guided via a control line to the check valve and thereby a flow path for the pressure medium discharge from the first and third working chamber are released.
  • a control valve is arranged in the first line and in the third line between the cylinder and directional control valve, wherein the control valve in a rest position caused by a spring element a flow path with a toward the cylinder opening check valve forms and forms a flow path for the outflow of pressure medium from the first and the third working chamber in a switching position caused by an actuating element.
  • the actuating elements of the control valves can be acted upon by means of a control line with the pressure in the second line.
  • a throttle element can be installed in the control line be, whereby abrupt switching operations and resulting pressure peaks on the control valve can be avoided.
  • the control valves or the actuators in the first and third line synchronously from the rest position to the switch position, it is according to another claim advantageous if the actuators are formed by a common control piston.
  • control valves are designed as Senkbremsventile, which are proven many times and easily available.
  • check valves or control valves are installed in the cylinder bottom in the cylinder.
  • the cylinder bottom is thus formed as a valve block.
  • check valves or control valves can be designed as valve cartridges inserted in the cylinder bottom, whereby also a compact design of the fluid cylinder is given.
  • a pressure sensor is fluid-connected to the first working chamber and the third working chamber. Since failure of one of the two working chambers, the holding function is taken over by the second intact working chamber, the monitoring by means of pressure sensors is helpful to detect any pressure drop early and further determine which of the two working chambers is inoperative.
  • the pressure sensor emits a signal when falling below a threshold pressure.
  • This signal e.g. in optical or acoustic form can be detected directly by the operator of the fluid cylinder, but also be handed over in the form of a control signal of a control and monitoring device.
  • the pressure sensor comprises a connected to a preloaded spring, acted upon by the pressure in the line volumetric flask.
  • the signal can be generated according to another claim by an optical display element connected to the volumetric flask. If the pressure force acting on the volumetric flask exceeds the oppositely acting biasing force of the spring, which is the case with an intact working chamber, the volumetric flask is displaced against the spring force and an optical display element becomes visible to the operator. In the case of a pressure drop in a working chamber, the volumetric flask is displaced by the spring to its initial position and the change of the optical display element, e.g. a disappearance visually indicates a malfunction to the operator.
  • Another advantage is an embodiment according to a wide claim, according to which there is a signal connection between the pressure sensor and a control and monitoring device.
  • a corresponding control and monitoring device may additionally or alternatively to the operator in the event of a pressure drop in one of the two working chambers perform necessary measures or functions.
  • the signal connection comprises a radio transmission device.
  • the fluid cylinder according to the invention can advantageously according to three further claims for positioning and fixing a tiltable or liftable construction on a vehicle, for moving and fixing an access ramp, in particular on a flatbed trailer or a passenger car transporter, as a lifting cylinder or support cylinder for positioning and fixing of movable Platforms, especially lifts and platforms, are used on vehicles.
  • Fig. 1 is a section through a fluid cylinder 1 according to the invention connected thereto, shown symbolically shown controls schematically and simplified.
  • the fluid cylinder 1 serves, for example, for positioning and fixing a tiltable or liftable structure on a vehicle, for moving and fixing an access ramp, in particular on a flatbed trailer or a passenger car transporter, as a lifting cylinder or support cylinder for positioning and fixing movable platforms, in particular lifting platforms and platforms, on vehicles - the integration of a working cylinder in these applications is known from the prior art and not explained or illustrated in consequence.
  • the fluid cylinder 1 is in particular a hydraulic cylinder 2 with a hydraulic fluid as the working medium.
  • the fluid cylinder 1 comprises a cylinder 3 with a longitudinal axis 4, with which a piston assembly 5 is mounted adjustably in the direction of the longitudinal axis 4.
  • the cylinder 3 is formed in the embodiment of a cylinder tube 6, which in the direction of the longitudinal axis 4 by a cylinder bottom 7 and a Cylinder cover 8 is limited.
  • the cylinder bottom 7 is welded to the cylinder tube 6, while the cylinder cover 8 is preferably bolted to the cylinder tube 6.
  • the piston assembly 5 comprises the actual piston 9, which divides the interior of the cylinder 3 into a first working chamber 10 and a second working chamber 11. To the piston 9, a piston rod 12 connects, which leads through the cylinder cover 8 sealed from the cylinder interior to the outside.
  • the piston assembly 5 has in its interior a cavity 13 which is open through an opening 14 in the form of a bore in the direction of the cylinder bottom 7.
  • the clear cross-section of the cavity 13 may coincide with the clear cross-section of the opening 14, thus e.g. can be made by a bore of constant diameter, but the diameter of the cavity 13 may also, as shown in Figure 1, be greater than the diameter of the opening 14.
  • the cavity 13 is formed in the embodiment by a tubular piston rod 12 which is pressure-tight at its free end by a lid 15 and at the opposite end by the piston 9 with the opening 14.
  • the piston assembly 5, as shown in simplified form in Figure 1, be made in one piece, but is also composed for reasons of ease of manufacture of the piston 9, the tubular piston rod 12 and the lid 15.
  • a piston tube 16 into the cavity 13.
  • the length of the cavity 13 and the piston tube 16 in the direction of the longitudinal axis 4 is chosen so that an end portion 17 of the piston tube 16 also at maximum extended plunger assembly 5 protrudes at least into the opening 14, ie the maximum effective depth of immersion of the piston tube 16 is greater than the maximum stroke of the piston assembly 5.
  • the piston tube 16 is sealed through the opening 14, said sealing by a tight fit between a Outer diameter 18 of the piston tube and the clear diameter of the opening 14 can be effected.
  • the opening 14 may be provided with a piston tube seal 19 which seals the passage of the piston tube 16 through the opening 14 in the piston 9.
  • the cavity 13 is thus sealed from the first working chamber 10 at the opening 14 by the piston tube 16 itself or the piston tube seal 19 and forms a third working chamber 20.
  • the piston tube 16 is concentric with the longitudinal axis 4 of the piston assembly 5 and the cylinder in the illustrated embodiment 3, but can if necessary, also be arranged offset to the longitudinal axis 4, for example, if an inventive fluid cylinder 1 is required with a continuous piston rod 12.
  • the first working chamber 10 of the fluid cylinder 1 is bounded by the cylinder inner wall 21, a cylinder bottom 7 facing the second piston surface 22 and an outer shell 23 of the piston tube 16, that is annular in the embodiment and has to inflow or outflow of pressure medium to a first line connection 24
  • the piston rod side second working chamber 11 is bounded by the cylinder inner surface 21, a cylinder cover 8 facing the second piston surface 25 and the outer shell 26 of the piston rod 12, as in a conventional working cylinder annular, and has to inlet and outlet of pressure medium, a second line connection 27th on.
  • the third working chamber 20 is bounded by an inner surface 28 of the cavity 13, an outer jacket 29 of the piston tube 16, which is identical to the outer jacket 23 of the piston tube 16 in the first working chamber 10, and an end face 30 of the piston tube 16 and is to Zu or Outflow of pressure medium via a channel 31 in the piston tube 16 connected to a third line connection 32.
  • the piston 9 is additionally provided with a piston seal 33, for sealing the second working chamber 11 in the passage of the piston rod 11 to the outside, the cylinder cover 8 is provided with a piston rod seal 34.
  • the piston tube seal 19, the piston seal 33 and the piston rod seal 34 are movement seals and, for example, performs as a mechanical seal, as sealing material all known in the art materials are conceivable.
  • the piston tube 16 is guided in the direction of the longitudinal axis 4 through the piston head 7, but it is also possible to guide the piston tube 16 laterally through the cylinder tube 6, as long over the entire stroke of the piston assembly 5 at the opening 14, the seal between first working chamber 10 and third working chamber 20 is given and a displacement of the piston tube 16 relative to the cylinder 3 is prevented for example by a support.
  • the piston assembly 5 By the inflow of pressure medium via the first line connection 24 and the third line connection 32 in the first working chamber 10 and the third working chamber 20, the piston assembly 5 is moved relative to the cylinder 3 in the extension direction 36, while at the same time via the second line connection 27 pressure medium from the second working chamber 11 flows.
  • To move the piston assembly 5 in the retraction 37 of the second working chamber 11 is supplied via the second line connection 27 pressure medium and simultaneously removed via the third line port 32 pressure fluid from the third working chamber 20 and the first line port 24 pressure fluid from the first working chamber 10.
  • the control of these pressure medium flows by means of a valve assembly 38, the structure and operation is shown below.
  • a supply unit for example, a hydraulic unit pressurized pressure medium.
  • a pressure port 39 through which the pressure medium to the fluid cylinder 1 can flow, and a return port 40 is guided via the pressure fluid from the fluid cylinder 1 back to the hydraulic unit is arranged.
  • the movement of the fluid cylinder 1, ie extension, retraction or stoppage of the piston assembly 5 is, as applied in conventional working cylinders, controlled by means of a directional control valve 41, in particular a 4/3-way valve 42.
  • the three possible positions of the 4/3-way valve 42 cause the extension movement, the retraction or the stoppage of the piston assembly 5.
  • the pressure port 39 fluidly connected to a first working port 43 to the valve assembly 38, to carry out the Retraction, the pressure port 39 is fluidly connected to a second working port 44.
  • a first line 45 leads to the first line connection 24 of the first working chamber 10, from the second working connection 44 a line 46 to the second line connection 27 of the second working chamber 11, and from the first working connection 43 a third line 47 to the third line connection 32 of the third working chamber 20. Since the flow of pressure medium into or out of the first working chamber 10 must always take place simultaneously with the flow of pressure medium into or out of the third working chamber 20, the first line 45 and the third line 47 can be combined in at least a partial section in a single line.
  • the lines 45, 46, 47 may be formed at least in sections as separate pipelines or as drilled channels in solid valve blocks, in particular the cylinder base 7 executed.
  • An important function of the fluid cylinder 1 according to the invention is to be able to reliably hold a load acting on the piston rod 12 in the retraction direction 37 and to prevent an uncontrolled retraction of the piston assembly 5.
  • This setting of the piston assembly 5 in the cylinder 3 can be effected by selecting the blocking position on the directional control valve 41, since thereby the pressure medium inflow or outflow via the first working port 43 and the second working port 44 is prevented.
  • a reliable fixation of the piston assembly 5 is not guaranteed, since on the one hand at the directional control valve 41 by leakage, a pressure drop in the control system of the fluid cylinder 1 may occur or, for.
  • a first safety valve 48 is arranged in the first line 45 to the first working chamber 10, and arranged in the third line to the third working chamber 20, a second safety valve 49.
  • These safety valves 48, 49 allow an inflow of pressure medium to the first working chamber 10 and the third working chamber 20 at a correspondingly high pressure at the first working port 43, but prevent drainage of pressure medium from the first working chamber 10 and the third working chamber 20, so long as the directional control valve 21 a retraction movement of the piston assembly 5 is triggered.
  • the safety valves 48, 49 are designed as control valves 50 in the form of two-way valves and form in each case in a rest position caused by a spring element 51 a secured by a check valve 52 flow path and in an actuated by an actuator 53, eg as a control piston switching position by a throttle element 54 throttled flow path in the first conduit 45 and the third conduit 47.
  • the actuators 53 are each fluidly connected via a control line 55 to the second conduit 46, so hydraulically triggered as soon as triggering the retraction position on the directional control valve, the pressure in the second Line 46 is increased to the second working chamber 11.
  • the pressure medium which is delayed by the throttle elements 54, can flow out of the first working chamber 10 and the third working chamber 20 and reach the return port 40, thus retracting the piston arrangement 5.
  • the actuators 53 may additionally be fluidly connected via further control lines 56 to the conduits 45, 47 between the control valves 50 and the line ports 24, 32.
  • control valves 50 can be operated at very high pressures, e.g. be overloaded at an overload on the piston rod 4, which would damage the system, and thus the load, delayed by the throttle elements 54, drop.
  • the control valves 50 can also be embodied as unlockable shut-off valves, in particular check valves 52, which open in the direction of the fluid cylinder 1. For a secure holding of the load, these are designed as seat valves due to the negligible leakage losses, e.g. with ball seat or conical seat.
  • control valves 50 may be embodied as lowering brake valves, which have proven themselves many times and are available in many embodiments.
  • the fluid cylinder 1 can be referred to as a two-circuit cylinder due to its design with two secure supply lines to the working chambers 10, 20.
  • a pressure sensor 57 comprises a pressure piston in the working chamber 10, 20 applied to the volumetric piston 58, which is displaced by a pressure overcoming the spring bias against the force of a biased spring 59, whereby an optically visible display element 60 is visible outside of the pressure sensor 57 , If the display element 60 is not visible, this indicates an undershooting of a definable by the spring bias limit pressure in the associated working chamber 10, 20, whereby the operator is made aware of this condition and can take appropriate measures to enter to prevent a dangerous situation.
  • the safety valves 48, 49 or control valves 50 are installed in the cylinder 3 in the cylinder 3 in the region of the cylinder bottom.
  • the cylinder bottom 7 is thus formed as a stable valve block and may contain the entire valve assembly 38.
  • the cross-sectional area of the piston tube 16 or the opening 15 defined by the outer diameter 18 of the piston tube 16 is approximately 40%, but at least 33% of the cylinder cross-sectional area determined by the cylinder bore diameter 61. This is achieved by cylindrical cylinder 6, piston rod 12 and piston tube 16 are formed as three with a small clearance nested tubes.
  • FIG. 2 shows a possible embodiment of the safety valves 48, 49 in a simplified, schematic sectional view.
  • the two safety valves 48, 49 are formed in this embodiment by two control valves 50, which are designed substantially as a pilot-operated check valves 52.
  • a control piston 62 By pressure in the fluidically connected to the second line 46 control line 55, a control piston 62 is pressed from the illustrated rest position against the force of the spring member 51 in a switching position, not shown, whereby blocking elements 63 of the check valves 52, the flow path for the Abfie- ⁇ en of pressure medium the first working chamber 10 and the third working chamber 20 release.
  • the embodiment describes and shows a possible embodiment of the fluid cylinder 1, wherein it should be noted that the invention is not limited to the specific embodiment of the variant shown, but rather various combinations of the individual embodiments described with each other are possible and this variation possibility due to Teaching for technical action by objective invention in the skill of those working in this technical field is the expert. So are all conceivable embodiments, which are possible by combinations of individual details of the illustrated and described embodiment variant, includes the scope of protection.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
EP20070006623 2006-04-07 2007-03-30 Dispositif de vérin Ceased EP1843048B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT6082006A AT503408B1 (de) 2006-04-07 2006-04-07 Fluidzylinder-anordnung

Publications (3)

Publication Number Publication Date
EP1843048A2 true EP1843048A2 (fr) 2007-10-10
EP1843048A3 EP1843048A3 (fr) 2008-07-09
EP1843048B1 EP1843048B1 (fr) 2010-07-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070006623 Ceased EP1843048B1 (fr) 2006-04-07 2007-03-30 Dispositif de vérin

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Country Link
EP (1) EP1843048B1 (fr)
AT (1) AT503408B1 (fr)
DE (1) DE502007004365D1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103357671A (zh) * 2012-03-26 2013-10-23 苏州泰克诺机电有限公司 压力流量闭环可调的液压系统
WO2015117240A1 (fr) * 2014-02-06 2015-08-13 Ensign Drilling Partnership Système de vérin de levage hydraulique a déplacements multiples
AU2013200736B2 (en) * 2012-02-13 2015-08-20 Schlumberger Technology B.V. Adaptive hydraulic cylinder with floating seal interface
CN108999836A (zh) * 2018-09-30 2018-12-14 中船重工重庆液压机电有限公司 活塞杆进油双作用多级液压缸
CN115126741A (zh) * 2022-05-14 2022-09-30 西派格(南通)电液控制科技有限公司 多腔体可变控制面积数字式液压执行器
CN116079783A (zh) * 2023-02-28 2023-05-09 上海交通大学 负压驱动关节及多自由度负压驱动机械臂

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RU2665762C2 (ru) * 2016-08-11 2018-09-04 Российская Федерация, от имени которой выступает Государственная корпорация по атомной энергии "Росатом" Гидропривод

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DE3807669A1 (de) 1988-03-09 1989-09-21 Andexser Lucie Stufenlos verriegelbarer arbeitszylinder
DE4405938A1 (de) 1994-02-24 1995-08-31 Werner Prof Dr Ing Moeller Kolben-Zylinder-Einheit
AT4094U1 (de) 1999-12-07 2001-01-25 Weber Hydraulik Gmbh Linearverstellantrieb

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2013200736B2 (en) * 2012-02-13 2015-08-20 Schlumberger Technology B.V. Adaptive hydraulic cylinder with floating seal interface
US9435359B2 (en) 2012-02-13 2016-09-06 Schlumberger Technology Corporation Adaptive hydraulic cylinder with floating seal interface
CN103357671A (zh) * 2012-03-26 2013-10-23 苏州泰克诺机电有限公司 压力流量闭环可调的液压系统
CN103357671B (zh) * 2012-03-26 2015-06-17 苏州泰克诺机电有限公司 压力流量闭环可调的液压系统
WO2015117240A1 (fr) * 2014-02-06 2015-08-13 Ensign Drilling Partnership Système de vérin de levage hydraulique a déplacements multiples
US10246951B2 (en) 2014-02-06 2019-04-02 Ensign Drilling Inc. Hydraulic multi-displacement hoisting cylinder system
US10519725B2 (en) 2014-02-06 2019-12-31 Ensign Drilling Inc. Hydraulic multi-displacement hoisting cylinder system
CN108999836A (zh) * 2018-09-30 2018-12-14 中船重工重庆液压机电有限公司 活塞杆进油双作用多级液压缸
CN108999836B (zh) * 2018-09-30 2024-05-24 中船重庆液压机电有限公司 活塞杆进油双作用多级液压缸
CN115126741A (zh) * 2022-05-14 2022-09-30 西派格(南通)电液控制科技有限公司 多腔体可变控制面积数字式液压执行器
CN116079783A (zh) * 2023-02-28 2023-05-09 上海交通大学 负压驱动关节及多自由度负压驱动机械臂

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AT503408B1 (de) 2008-06-15
EP1843048A3 (fr) 2008-07-09
AT503408A1 (de) 2007-10-15
DE502007004365D1 (de) 2010-08-26

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