EP2215368B1 - Elektrohydraulischer verstärker - Google Patents

Elektrohydraulischer verstärker Download PDF

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Publication number
EP2215368B1
EP2215368B1 EP08848617.0A EP08848617A EP2215368B1 EP 2215368 B1 EP2215368 B1 EP 2215368B1 EP 08848617 A EP08848617 A EP 08848617A EP 2215368 B1 EP2215368 B1 EP 2215368B1
Authority
EP
European Patent Office
Prior art keywords
control
piston
sleeve
power stage
accordance
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
EP08848617.0A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2215368A2 (de
Inventor
Manfred Kurz
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.)
Hoerbiger Automatisierungstechnik Holding GmbH
Original Assignee
Hoerbiger Automatisierungstechnik Holding 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
Priority claimed from DE200710054533 external-priority patent/DE102007054533C5/de
Priority claimed from DE200710054774 external-priority patent/DE102007054774B3/de
Application filed by Hoerbiger Automatisierungstechnik Holding GmbH filed Critical Hoerbiger Automatisierungstechnik Holding GmbH
Publication of EP2215368A2 publication Critical patent/EP2215368A2/de
Application granted granted Critical
Publication of EP2215368B1 publication Critical patent/EP2215368B1/de
Not-in-force 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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/10—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which the controlling element and the servomotor each controls a separate member, these members influencing different fluid passages or the same passage
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric

Definitions

  • the present invention relates to an electrohydraulic amplifier with an electromechanical transducer and a connected to a pressure medium supply, a cylinder and a displaceable along the working axis piston having hydromechanical power stage, wherein the electromechanical transducer assigned to one of the hydromechanical power level, at least partially disposed in the interior of the piston , in a guide bore along the working axis slidably guided spool acts, which has two first control edges, which cooperate to form a hydraulic follow-up control with corresponding, provided on the guide bore second control edges.
  • Electrohydraulic amplifiers of the type specified above are known in various designs.
  • the prior art for example, referred to the EP 0296104 A1 and the DE 19757157 C2 , After EP 0296104 A1
  • the hydromechanical power stage is designed in one stage, in that the control spool, which is actuated by the electromechanical converter as the input stage, directly controls the admission of the hydraulic fluid to the piston.
  • the hydromechanical power stage is designed in two stages by the spool is designed as a pilot spool and controls the movement of a control chamber with hydraulic fluid displacement of a coaxial with the spool and movable control sleeve, the control sleeve in turn - over each other cooperating pairs of third and fourth control edges - controlling the pressurization of the piston with hydraulic fluid.
  • electrohydraulic amplifiers can be used, for example, as drives for machines or units of various types and various other applications.
  • the electrohydraulic amplifiers known from the prior art only satisfy (still) limited the increasing demands of the users, who attach particular importance to highest performance (for example forces of up to or even more than 30 t), economy and accuracy (reproducibility). From the point of view of economy, since this is sometimes of decisive importance for the production speed, the aspect of high dynamics (for example working frequencies of up to or even more than 20 working cycles per second) is particularly important.
  • the US-A 4,779,837 discloses a seat valve with a valve housing, a guided therein displaceable, designed as a hollow piston closing body and a slidably guided in the central cavity of the closing body control piston.
  • the latter is guided in the valve housing as well as the closing body and adjustable by means of an electromagnet, wherein the closing body in the sense of a follow-up control of the adjustment of the control piston follows.
  • the function of this valve requires for the adjustment of the closing body acting on the front side upstream of the valve seat pressure of the valve to through switching medium; a technical teaching independent of the valve function can not be found in this document.
  • the present invention is therefore an object of the invention to provide a generic electro-hydraulic amplifier, which meets the existing user-side technical requirements in a special way by it is characterized in particular by the possibility of high forces at the same time particularly high dynamics.
  • the guide bore in two parts with a cylinder-fixed first portion and a working position variable second section, which has the second control edges is executed, wherein further the first portion of Guide bore is carried out in a guide sleeve inserted into the cylinder or the cylinder component.
  • the guide sleeve can in particular enforce a filled with hydraulic fluid space, i. at least partially be lapped on its outer surface with hydraulic fluid.
  • Decisive for the electrohydraulic amplifier according to the invention is thus on the one hand that - instead of a one-piece guide bore for the spool - a two-part Fhakuhgsbohrung is provided, the two of the guide of the spool serving portions of the guide bore along the working axis relative to each other movable are by a first portion fixed to the cylinder and a second portion which has the second control edges, in the working direction of the piston is displaceable.
  • the overall length of the guide bore can be substantially reduced in this way.
  • the invention is capable of providing an electrohydraulic amplifier which can be used as drive in various fields of application, which is not only particularly efficient in the manner described above but is also comparatively robust, simple and reliable, and which is suitable for the implementation of defined working or operating conditions. Movement programs with the highest precision is suitable.
  • the return port of the hydromechanical power stage is arranged in the region of the end wall of the cylinder component, wherein the control slide of the hydromechanical power level is flowed through by the return flow.
  • electrohydraulic amplifier Another preferred development of the electrohydraulic amplifier according to the invention is characterized in that the electromechanical transducer, i. whose stator is mounted directly on the front wall of the cylinder component.
  • the resulting very short load paths are reflected in a particularly high precision of the electrohydraulic amplifier.
  • the direct mounting of the stator of the electromechanical transducer to the front wall of the cylinder of the hydromechanical power level can largely avoid influences that could adversely affect the precision of the machine.
  • the thus developed electrohydraulic amplifier is particularly compact.
  • an electric linear direct drive with parallel to the working axis, ie in the z-direction extending motor axis used, the rotor (lineator or linear actuator) acts directly on the spool as an electromechanical transducer.
  • the piston is displaceable in a cylinder along the working axis, and an input stage in the form of a genuine electric linear direct drive are provided, the rotor on the slidably guided in a two-part guide bore in the z direction control slide hydromechanical power level acts.
  • the spool has two first control edges, which cooperate with formed on the second portion of the guide bore second control edges, wherein due to the interaction of the first and the second control edges in the sense of a hydraulic follow-up control displacement of the spool in the z-direction in the result - directly or indirectly (see below) - an adjustment of the piston of the hydromechanical power stage by the identical path entails.
  • the displacement of the control spool by means of the linear electric direct drive along the z-direction is thus converted 1: 1 into a corresponding movement of the piston of the hydromechanical power level identical to the direction and the magnitude.
  • stator of the electric linear direct drive can be firmly connected to an end wall of the cylinder of the hydromechanical power stage. This applies in particular when, according to a again preferred development of the invention, the rotor of the electric linear direct drive is connected firmly to the spool via a coupling rod penetrating the end wall of the cylinder.
  • the coupling rod described above which firmly connects the rotor of the electric linear direct drive with the control slide, particularly preferably passes through a low pressure space of the cylinder of the hydromechanical power stage that is essentially acted upon by the return pressure. In this way, only relatively small demands are placed on the sealing of the coupling rod relative to the cylinder. Accordingly, no appreciable frictional forces act on the coupling rod in the region of the seal, which has a favorable effect both in terms of the dynamics of the electrohydraulic amplifier and with regard to its precision (reproducibility of the piston movement).
  • a particularly preferred embodiment of the invention is in the field of implementation of the coupling rod through the end wall of the cylinder at all no sealing provided. Rather, here is the rotor of the electric linear direct drive in a sealingly connected to the cylinder component of the hydromechanical power stage connected to the stator of the electric linear direct drive passing bush, the interior of which is connected to a hydraulic fluid-containing low-pressure chamber of the hydromechanical power stage.
  • a similar effect can be achieved if, instead of (only) accommodating the rotor of the electric linear direct drive in the manner described above in a bush filled with hydraulic fluid, the electric linear direct drive as a whole in one with the cylinder component of the hydromechanical power stage sealed housing is housed, the interior of which is connected to a hydraulic fluid-containing low-pressure chamber of the hydromechanical power stage.
  • the hydromechanical power stage can be designed in one stage or in two stages.
  • the second control edges are arranged piston-fixed. In this way, the piston of the hydromechanical power stage immediately follows the movement of the spool.
  • the hydromechanical power stage in contrast, carried out in two stages, so the - actuated by the electromechanical transducer - spool is a pilot spool, and the second control edges are executed on a displaceably guided in the piston along the working axis control sleeve, which in turn has two third control edges, which Formation of a hydraulic follow-up control with two corresponding fourth control edges of the piston cooperate.
  • the piston of the hydromechanical power stage follows the movement of the spool only indirectly, by the control sleeve follows the movement of the spool and the piston of the movement of the control sleeve.
  • the cooperating first and second control edges control in this way only a comparatively small flow of hydraulic fluid, namely the volume flow which is required for the adjustment of the control sleeve.
  • To adjust the piston of the hydromechanical power level serving volume flow is controlled in contrast by the cooperating third and fourth control edges.
  • two stops are preferably provided, which limit the movement of the control sleeve relative to the piston in the direction of the working axis to a certain proportion of the maximum working stroke of the piston.
  • Such stops are particularly advantageous in that they allow (at a given maximum stroke of the piston) a shorter overall length of the hydromechanical power stage, compared with an embodiment without such stops.
  • the entire range of movement of the control sleeve relative to the piston to a proportion of 5% to 25%, more preferably 10% to 15% of the maximum stroke of the piston are limited, so that, for example, with a designed to 40mm maximum Piston stroke, the control sleeve from a zero position in which the third and fourth control edges are ideally aligned, in both directions by 2.5mm (6.25% of the piston stroke) can be moved relative to the piston.
  • an asymmetrical limitation of the possibility of movement of the control sleeve can be provided relative to the piston by means of said stops.
  • an electrohydraulic amplifier 6 is provided on which the numerical control 3 acts .
  • the electrohydraulic amplifier comprises as main components an input stage in the form of an electromechanical transducer 2, which is designed as an electric linear direct drive 7, and a hydromechanical power stage 10, which has a (two-part) cylinder 8 and a piston 9 slidably guided therein along the working axis 5 ,
  • the electric linear direct drive 7, the motor axis 11 extends in the z-direction, is such controlled directly by the numerical control 3 that its rotor 12 occupies a defined position in the z-direction according to the respective control by the numerical control 3.
  • the - connected between the rotor 12 of the electric linear direct drive 7 and the element 1 - hydro-mechanical power stage 10 is connected to a pressure medium supply 13, which in known manner a motor 14, a driven by this, hydraulic fluid from the tank 15 sucking pump 16, a check valve 17 and a pressure accumulator 18 includes.
  • a pressure medium supply 13 which in known manner a motor 14, a driven by this, hydraulic fluid from the tank 15 sucking pump 16, a check valve 17 and a pressure accumulator 18 includes.
  • a pressure medium supply 13 which in known manner a motor 14, a driven by this, hydraulic fluid from the tank 15 sucking pump 16, a check valve 17 and a pressure accumulator 18 includes.
  • a pressure medium supply 13 which in known manner a motor 14, a driven by this, hydraulic fluid from the tank 15 sucking pump 16, a check valve 17 and a pressure accumulator 18 includes.
  • the piston is designed in the sense as a differential piston, as in the z-direction determined, the first working space 19 limiting total end face 21
  • the second working chamber 20 in order to effect a movement of the piston 9 along the z-direction, as described in detail below controlled either fluidically connected to the pressure medium supply 13, so that in him the operating pressure of the pressure medium supply prevails and the piston 9 is moved together with the element 1 down, or fluidly connected to the tank 15, whereby in he the return pressure prevails and the piston 9 is moved together with the element 1 upwards.
  • a control slide 23 is provided, which is arranged in the interior of the piston 9 of the hydromechanical power stage 10 and along the working axis 5, that is displaceable in the z-direction.
  • the spool 23 is guided in a guide bore, with an upper collar 24 in an upper, first portion 25 of the guide bore and with a lower collar 26 in a lower, second portion 27 of the guide bore.
  • the first portion 25 of the guide bore is designed to be cylinder-tight by being formed by the inner surface 28 of a guide sleeve 29 inserted into the cylinder 8.
  • the second section 27 of the guide bore is piston-solid in that it is formed by the lower inner surface 30 of a stepped blind bore 31 arranged in the piston 9.
  • the outer surface 32 of the guide sleeve 29 is in contrast sealingly in the upper inner surface 33 of the stepped blind bore 31 of the piston 9 at.
  • a high-pressure chamber 36 is defined. This is over a plurality of radial bores 37, of which for reasons of clarity, only one is shown, constantly with the first working space 19 connected, so that in him constantly the operating pressure of the pressure medium supply 13 prevails.
  • the projection in the z-direction of the area of the high-pressure space 36 defined by paragraph 35 is substantially nonexistent than the projection in the z-direction of the end face 21 of the piston 9 delimiting the first working space 19.
  • first control edges 38 namely an upper first control edge 38 a and a lower first control edge 38 b are formed. These act together with corresponding to them second control edges 39, namely an upper second control edge 39a and a lower second control edge 39b, which are executed on a arranged in the region of the lower inner surface 30 of the blind bore 31 in the piston annular groove 40.
  • the annular groove 40 is permanently connected to the second working space 20 via a plurality of axial bores 41, of which only one is shown for reasons of clarity.
  • a defined in particular by the upper collar 24 of the spool 23 and the above the upper collar 24 of the spool area of the inner surface 28 of the guide sleeve 29 limited cavity 42 of the hydromechanical power stage 10 is disposed over a radial bore 43 with a in the region of the end wall 44 of the cylinder 8 , connected to the tank 15 return connection 45 for the hydraulic fluid in combination. It thus represents an upper low-pressure space 46 in which substantially the return pressure prevails.
  • the spool 23 is in the longitudinal direction pierced; the corresponding longitudinal bore 47, which is connected via apertures 54 to the upper low-pressure chamber 46, opens at the lower end of the spool 23 in a lower low-pressure chamber 48, which in particular by the lower collar 26 of the spool 23, lying below the lower collar of the spool area the lower inner surface 30 of the blind bore 31 and the end face 49 of the blind bore 31 is limited.
  • the return pressure is essentially the same.
  • the stator 52 of the linear electric direct drive 7 is fixedly connected to the end wall 44 of the cylinder 8 of the hydromechanical power stage 10.
  • the electric linear direct drive 7 is further surrounded by a sealed to the cylinder 8 housing 49.
  • the rotor 12 of the electric linear direct drive 7 is connected via a coupling rod 50, which passes through the end wall 44 of the cylinder 8 and the upper low-pressure chamber 46, fixed to the spool.
  • the provided in the end wall 44 of the cylinder 8 bore 51, through which the coupling rod 50 emerges from the cylinder is dimensioned so that an exchange of hydraulic fluid between the upper low-pressure chamber 46 and the interior of the housing 49 is possible.
  • the piston 8 is moved due to the prevailing in the first working chamber 19 operating pressure of the pressure medium supply 13 upwards.
  • the movement of the piston 8 is identical identical to the measure by which the spool 23 has been moved upwards; because the upward movement of the piston ends when the lower first control edge 38b and the lower second control edge 39b are aligned again and close the annular gap described above again.
  • the displaced during the corresponding upward movement of the piston 8 from the second working chamber 20 hydraulic fluid flows through the axial bores 41, the annular groove 40, the lower low-pressure chamber 48, the longitudinal bore 47 of the spool 23, the upper low-pressure chamber 46 and the radial bore 43 back into the tank 15 , At the same time, hydraulic fluid flows from the pressure medium supply 13 into the first working space 19.
  • the second control edges 39 are not formed in this embodiment by edges of the annular groove 40; Rather, the sleeve 58 has radial openings 59, the upper second control edges 39a and the lower second Control edges 39b are formed by corresponding edges of the openings 59. Again, this manufacturing advantages are in turn connected.
  • the embodiment detects Fig. 2 in the field of implementation of the coupling rod 50 through the end wall 44 of the cylinder 8 a separate insert E, which may be adapted to the specific requirements regarding a possible sealing and / or guidance of the coupling rod 50.
  • Fig. 3 again in turn substantially corresponds to the embodiment Fig. 2 , In that regard, reference is made to the above statements to avoid repetition. It should be emphasized with regard to Fig. 3 only one noteworthy modification. Namely, the return port 60 is not arranged in the region of the end wall 44 of the cylinder 8, but rather in the region of the lower end of the cylinder 8. Accordingly, the lower low-pressure chamber 48 here in the piston 9 arranged radial bores 61, which - at Each position of the piston 9 relative to the cylinder 8 - are fluidically connected to an arranged in the cylinder annular groove 62, connected to the opening into the annular groove 62 return port 60.
  • the spool 23 is not flowed through by the resulting in the upward movement of the piston 9 return flow of the hydraulic fluid. Rather, here has the control slide passing through the longitudinal bore 63 alone the task of providing a pressure equalization between the lower low-pressure chamber 48 and the upper low-pressure chamber 46. A (compensatory) flow within the longitudinal bore 63 adjusts itself only in accordance with and during the displacement of the spool 23 in the guide bore.
  • the embodiment differs according to Fig. 3 from those after the Fig. 1 and 2
  • a constant exchange of hydraulic fluid instead.
  • a bellows-shaped compensating member is indicated, which can deform in accordance with the movement of the rotor 12, so that the dynamics of the movement of the rotor is not affected by the existing hydraulic fluid in the sleeve.
  • a bead 173 is formed on which on the one hand a substantial sealing of the guide sleeve 129 relative to the upper portion of the outer surface 187o of the control sleeve 171 and on the other hand a substantial sealing of the guide sleeve 129 relative to the inner surface 175 of the piston sleeve 172.
  • an inner high pressure upper space 176 is defined. This is connected via a bore 177 constantly connected to the pressure medium connection 178, so that in him constantly the operating pressure of the pressure medium supply 113 prevails.
  • the operating pressure of the pressure medium supply 113 constantly prevails in an inner lower high pressure chamber 179, which passes through the lower inner surface 180 of the control sleeve 171, an upper stopper 181, the lower inner surface 182 of the piston sleeve 172, a lower stopper 183 and the end face 184 of the control sleeve 171 is limited.
  • an inner low-pressure chamber 191 which is connected via the spool 123 passing through longitudinal bore 147 to the upper low pressure chamber 146, which in turn communicates via a bore 192 with the return port 145. In this way, prevails in the inner low-pressure chamber 191 is substantially the return pressure.
  • the return pressure prevails in the annular lower low-pressure chamber 148, the inner surface 175 of the piston sleeve 172, the central collar 189 and the lower collar 193 of the control sleeve 171 and lying between the central collar 189 and the lower collar 193 lower portion of the outer surface 187u the control sleeve 171 is limited and via the piston sleeve 172 and the piston 109 passing through radial bores 194 and an annular groove 195 is connected to the return port 145.
  • a control chamber 196 is provided which is bounded by the inner surface 175 of the piston sleeve 172, the upper collar 188 of the control sleeve 171, the above the upper collar 188 lying upper portion of the outer surface 187o of the control sleeve 171 and the bead 173 and in which the control sleeve 171 radially penetrating inner control apertures 197 open.
  • first control edges 138 namely an upper first control edge 138a and a lower first control edge 138b are formed. These act together with corresponding to them second control edges 139, namely upper second control edges 139a and lower second control edges 139b, which are executed on the inner control apertures 197 of the control sleeve 171.
  • third control edges 198 are executed, namely an upper third control edge 198a and a lower third control edge 198b. These cooperate with corresponding fourth control edges 199, namely upper fourth control edges 199a and lower fourth control edges 199b, which are formed on outer control apertures 200, which pass through the piston sleeve 172 and communicate with an annular groove 140 arranged in the piston 109, which in turn communicate over several Axial bores 141, of which for clarity, only one is shown, with the second working space 120 is in communication.
  • the movement which the control sleeve 171 executes in total coincides identically with the dimension by which the spool valve 123 has been displaced; because the downward movement of the control sleeve ends when the upper first control edge 138a and the upper second control edge 139a are aligned again and close the openings described above again.
  • hydraulic fluid flows from the annular outer high-pressure space 186 through the outer control passages 200 through the annular groove 140 and the axial bores 141 into the second working space 120, thereby moving the piston 108 downward.
  • the movement of the piston 108 coincides identically with that measure by which the spool 123 and accordingly the control sleeve 171 has been displaced; because the downward movement of the piston ends when the upper third control edge 198a and the upper fourth control edges 199a are aligned again and again close the openings described above.
  • the control sleeve 171 is displaced upward due to the pressure prevailing in the inner lower high pressure chamber 179 operating pressure of the pressure medium supply 113.
  • For this movement of the control sleeve 171 upwards (with unpressurized control chamber 196) is sufficient that the projection in the z direction of the lower high-pressure chamber 179 limiting end face 184 of the control sleeve 171 and the upper plug 181 is greater than the projection in the z-direction the upper high-pressure chamber 176 limiting end face of the control sleeve 171.
  • the movement of the control sleeve 171 is identical identical to that measure by which the spool 123 has been moved upwards; because the upward movement of the control sleeve 171 ends when the lower first control edge 138b and the lower second control edges 139b are aligned again and close the openings described above again.
  • the movement of the piston 108 coincides identically with that dimension by which the spool 123 and accordingly the control sleeve 171 have been displaced upwards; because the upward movement of the piston 108 ends when the lower third control edge 198b and the lower fourth control edges 199b are aligned again and again close the openings described above.
  • control sleeve 171 on the movement relative to the piston sleeve 172 upwardly or downwardly limiting stop, the control sleeve 171 and the piston 109 a part of the up or down directed movement together.
  • the inner upper high-pressure chamber 176 is subjected to the operating pressure of the pressure medium supply 113 via a plurality of axial bores 201 passing through the control sleeve 171 from the annular outer high-pressure chamber 186.
  • This can be the after Fig. 4 provided, the cylinder member 108 passing through hole 177 avoid.
  • the movement of the piston 108 coincides identically with that measure by which the spool 123 and accordingly the control sleeve 171 has been displaced; because the downward movement of the piston ends when the upper third control edge and the upper fourth control edges are aligned again and close the openings described above again.
  • control sleeve 171 is moved due to the pressure prevailing in the annular outer high-pressure chamber 186 operating pressure of the pressure medium supply 113 up.
  • the piston 108 is moved due to the prevailing in the first working chamber 119 operating pressure of the pressure medium supply 113 up.
  • the displaced during the corresponding upward movement of the piston 108 from the second working chamber 120 hydraulic fluid flows through the axial bores 141, the annular groove 140, the lower low pressure chamber 148 and the radial bores 194 back into the tank 115.
  • hydraulic fluid flows from the pressure medium supply 113 into the first working space 119.
  • Fig. 5 Also shown in Fig. 5 two stops, which limit the movement of the control sleeve 171 relative to the piston sleeve 172 in both directions, in each direction to about 2% to 3% of the total maximum stroke of the piston 109, which in the design of the working stroke to 40mm a possibility of movement of the control sleeve 171 relative to the piston 109 of 2mm to 3mm from the zero position of the spool shown in the drawing corresponds.
  • Those attacks are the two fixed in the lower portion of the bore of the piston sleeve rings on which the central collar 189 of the control sleeve 171 can strike.
  • the central collar 189 of the control sleeve 171 For the function of these attacks apply the explanatory notes to the Fig. 4 in a similar way.
  • Another design or arrangement of the stops, which is suitable to protect the arranged on the central collar 189 third control edges, recognizable for the expert is also possible.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
  • Actuator (AREA)
  • Reciprocating Pumps (AREA)
  • Multiple-Way Valves (AREA)
  • Magnetically Actuated Valves (AREA)
  • Braking Systems And Boosters (AREA)
EP08848617.0A 2007-11-15 2008-11-10 Elektrohydraulischer verstärker Not-in-force EP2215368B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE200710054533 DE102007054533C5 (de) 2007-11-15 2007-11-15 CNC-Stanzmaschine
DE200710054774 DE102007054774B3 (de) 2007-11-16 2007-11-16 Elektrohydraulischer Verstärker
PCT/EP2008/009467 WO2009062649A2 (de) 2007-11-15 2008-11-10 Elektrohydraulischer verstärker

Publications (2)

Publication Number Publication Date
EP2215368A2 EP2215368A2 (de) 2010-08-11
EP2215368B1 true EP2215368B1 (de) 2016-01-27

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08848617.0A Not-in-force EP2215368B1 (de) 2007-11-15 2008-11-10 Elektrohydraulischer verstärker

Country Status (6)

Country Link
US (1) US8074557B2 (ja)
EP (1) EP2215368B1 (ja)
JP (1) JP5286365B2 (ja)
DE (1) DE202008017285U1 (ja)
ES (1) ES2562552T3 (ja)
WO (1) WO2009062649A2 (ja)

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Publication number Priority date Publication date Assignee Title
DE102012013098B4 (de) * 2012-06-30 2014-08-07 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
DE102015218576B4 (de) * 2015-09-28 2022-03-31 Danfoss Power Solutions Gmbh & Co. Ohg Steuereinheit
CN108362167B (zh) * 2018-04-12 2023-07-28 陕西航天机电环境工程设计院有限责任公司 快开发射装置及强冲击动力发生系统
CN108757877B (zh) * 2018-08-23 2023-04-25 桂林航天工业学院 摩擦轮柔性机械式反馈装置
CN111219377A (zh) * 2018-11-26 2020-06-02 徐州徐工液压件有限公司 一种智能液压缸装置及控制方法

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US4907492A (en) 1987-06-16 1990-03-13 Sig Schweizerische Industrie-Gesellschaft Apertured valve disposed in hollow piston rod of follower-type motor
DE3805735A1 (de) * 1988-02-24 1989-09-07 Bosch Gmbh Robert Bremskraftverstaerker
JP2538434Y2 (ja) * 1990-07-26 1997-06-18 住友重機械工業株式会社 電油サーボアクチュエータ
JP3437603B2 (ja) * 1992-06-29 2003-08-18 株式会社エスジー 流体圧アクチュエータ及びその位置決め制御システム
DE19757157C2 (de) * 1997-12-20 2003-06-12 Ipm Ingenieur Und Projektman G Hydraulischer Linearantrieb

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US8074557B2 (en) 2011-12-13
EP2215368A2 (de) 2010-08-11
JP2011503482A (ja) 2011-01-27
DE202008017285U1 (de) 2009-06-18
ES2562552T3 (es) 2016-03-04
US20100224059A1 (en) 2010-09-09
WO2009062649A2 (de) 2009-05-22
WO2009062649A3 (de) 2009-11-12
JP5286365B2 (ja) 2013-09-11

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