EP0066274A1 - Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin - Google Patents

Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin Download PDF

Info

Publication number
EP0066274A1
EP0066274A1 EP82104683A EP82104683A EP0066274A1 EP 0066274 A1 EP0066274 A1 EP 0066274A1 EP 82104683 A EP82104683 A EP 82104683A EP 82104683 A EP82104683 A EP 82104683A EP 0066274 A1 EP0066274 A1 EP 0066274A1
Authority
EP
European Patent Office
Prior art keywords
valve
channel
valve body
control
bore
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
EP82104683A
Other languages
German (de)
English (en)
Other versions
EP0066274B1 (fr
Inventor
Henry Friesen
John Rosbak
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Priority to AT82104683T priority Critical patent/ATE15253T1/de
Publication of EP0066274A1 publication Critical patent/EP0066274A1/fr
Application granted granted Critical
Publication of EP0066274B1 publication Critical patent/EP0066274B1/fr
Expired legal-status Critical Current

Links

Images

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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F15B2011/0243—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits the regenerative circuit being activated or deactivated automatically
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2544—Supply and exhaust type
    • Y10T137/2554—Reversing or 4-way valve systems

Definitions

  • the invention relates to a hydraulic control valve device with a feedback valve consisting of a valve housing with a valve bore; a first and a second control channel which open into the valve bore at different points within the valve housing; a first and second working channel, which open into the valve bore at different points within the valve housing; a first valve body which is displaceable within the valve bore between a closed position in which it interrupts the flow connection between the first control channel and the first working channel and an open position in which it opens this flow connection; a second valve body which is displaceable within the valve bore between a first valve position, in which it interrupts the flow connection between the second working channel and the first control channel or the first working channel, and a second valve position, in which it connects the flow connection between the second working channel and interrupts the second control channel, but releases the flow connection between the second working channel and the first control channel or the first working channel; and a first and second spring element, which are arranged in the valve bore and press the first and second valve bodies into their closed position and first valve position, respectively.
  • the first control channel forms, together with the first working channel, an extending channel which is guided through the valve housing and which connects a pressure fluid source, for example a pump, to an extending or head-side chamber of a hydraulic working cylinder.
  • the second control channel forms, together with the second working channel, a pull-in channel which is guided through the valve housing and which connects a liquid reservoir or a sump to a chamber of the hydraulic working cylinder on the pull-in or piston rod side.
  • the second working channel forms, together with the first working channel, a feedback channel which is guided through the valve housing and which connects the feed chamber of the hydraulic working cylinder to its extension chamber.
  • the two valve bodies are rigidly connected to one another and form a piston slide, which is acted upon on its opposite end faces by the two spring elements acting in the opposite direction. These hold the piston slide in its first valve position, in which the flow connection between the second control channel and the second working channel is interrupted by the second valve body.
  • a directional control valve is provided in this known control valve device, which is connected on the one hand to the pressure fluid source and the sump and on the other hand to one end of the two control channels.
  • the invention is therefore based on the object of improving the control valve device explained at the outset with regard to its functionality, in particular when the piston rod of a hydraulic cylinder under high load is extended.
  • the second valve body has a first end face and a second end face which are acted upon by the liquid pressure in the first control channel or in the second control channel such that an increase in the pressure in the first control channel via the pressure in the second control channel causes a shift in the causes the second valve body in its second valve position against the action of the second spring element, the second valve body displacing the first valve body in its open position during this displacement via a driving device.
  • the new feedback valve is simple and compact. It works absolutely reliably under all operating conditions.
  • a directional control valve can be provided, which is connected on the one hand to the pressure fluid source and the sump and on the other hand to one end of the two control channels.
  • this directional control valve the connections between the pressure fluid source and the sump on the one hand and the head-side and piston rod-side chamber of the hydraulic cylinder on the other hand can be exchanged, so that the double-acting hydraulic cylinder can be extended or retracted.
  • the hydraulic system shown in Figure 1 comprises a pump 12 and a sump 14 which are connected to a conventional four-way, three-position directional control valve 16.
  • a feedback or acceleration valve 18 is connected between this directional control valve 16 and a double-acting hydraulic working cylinder 20 or a hydraulic motor.
  • the feedback valve 18 consists of a valve housing 22 with a stepped valve bore 24, the wall of which forms a valve seat 26 and an annular shoulder 28 pointing in the axial direction. In the open end of the valve bore 24 is screwed this plug to the outside liquid-sealing plug 30.
  • a first control channel 32 and a second control channel 34 open into the valve bore 24 near the opposite ends of this valve bore and connect them to the corresponding outlets of the directional control valve 16.
  • a first working channel 36 is connected to the head-side chamber 42 of the hydraulic working cylinder 20 a section 40 opens into the valve bore 24 at the valve seat 26.
  • a second working channel 44 is connected to the piston rod-side chamber 48 of the hydraulic working cylinder 20, which has two branches 50, 52 which open into the valve bore 24 via an annular groove 54 or 56, which are separated from one another by an annular web 58.
  • a cylindrical valve body 60 is slidably mounted, which has a central axial bore 62 and an axially directed annular end face 64 which in the first valve position rests with its outer edge against the said annular shoulder 28.
  • an axially rising central section 66 is provided, on which a spring element 68 is inserted, which is supported at one end on this end face of the valve body 60 and at the other end on the sealing plug 30 and presses the valve body 60 with its annular end face 64 against the annular shoulder 28.
  • valve body 70 has a valve head 72 with a conical sealing surface 74 which, in the closed position of this valve body, bears against the valve seat 26.
  • the valve head 72 is coaxially attached to one end of a cylindrical valve rod 76 which extends through the axial bore 62 in the other valve body 60.
  • a cylindrical flange 78 with a recess 79 is fastened on the valve rod 76 in a section of smaller diameter such that the valve body 60 lies between the valve head 72 and the flange 78 of the valve body 70.
  • the radially outer portion of the flange 78 is flanged in the axial direction and directed away from the valve body 60, so that the flange 78 together with the valve rod 76 forms an annular socket for receiving one end of a spring 80, the other end of which rests against the sealing plug 30 supports so that the spring 80 against the valve head 72 presses the valve seat 26.
  • Both springs 68, 80 push the valve bodies 60, 70 to the left in relation to the figures.
  • the plug 30 has a blind bore 90 into which one end of the valve rod 76 is immersed and into which one end of the spring 80 is inserted.
  • An annular collar 92 surrounds the open end of the blind bore 90 and is overlapped by one end of the spring 68.
  • the two valve bodies 60, 70 together with the wall of the valve bore 24, the two valve bodies 60, 70 form a first and a second valve chamber 82, 84.
  • the first valve chamber 82 is connected to the control channel 32 and the working channel 40, while the second valve chamber 84 communicates with the second control channel 34 and communicates with the second working channel 44 via the branch 50 and the annular groove 54.
  • the valve chambers 82, 84 are never in fluid communication with one another. This is ensured by the fact that only one of the two annular grooves 54, 56, but never both, are opened at the same time via the valve body 60 with respect to the valve bore 24.
  • the working channels 36, 44 or the like can be connected via branch lines 37, 45 to other hydraulic motors, but not shown in the drawing. be connected. These branch lines can be inside or outside the valve housing 22.
  • the directional control valve 16 is actuated in such a way that the control channel 34 is connected to the pump 12 or to a pressure fluid source and the control channel 32 to the sump 14 or a fluid reservoir .
  • the relatively high fluid pressure in the control channel 34 relative to the control channel 32 holds the valve body 60 pressed against the annular shoulder 28, so that liquid can flow from the control channel 34 via the valve bore 24, the branch 50 and the working channel 44 into the piston rod-side chamber 48.
  • the hydraulic motor 20 is retracted; the piston of this engine or of the hydraulic working cylinder 20 is shifted to the left (refer to FIG.
  • valve head 72 is still in contact with valve seat 26 and is prevented such a flow outflow from the valve chamber 82.
  • valve chamber 82 This creates a pressure rise in this valve chamber 82 which very quickly exceeds the pressure prevailing in the valve chamber 84, since the valve chamber 84 is connected directly to the sump 14 via the control line 34 and the directional control valve 16.
  • the valve body 70 Under the effect of the resulting pressure difference between the end faces 64, 66 of the valve body 60, the latter is displaced in the valve bore 24 relative to the valve body 70 from its position shown in FIG. 1 to the right.
  • the valve body 70 While the valve body 70 maintains its closed position, the valve body 60 first slides over the annular groove 54 and thereby closes the branch 50, but at the same time keeps the branch 52 still closed.
  • the connection between the working channel 44 and the control channel 34 is interrupted, so that an outflow of liquid from the chamber 48 on the piston rod side is temporarily prevented.
  • valve chamber 84 is only connected to the sump 14 via the control channel 34, so that the pressure difference between the valve chambers 82, 84 increases further.
  • the valve body 60 strikes with its right end face against the flange 78 and takes the valve body 70 with it as it moves further, so that its valve head 72 lifts off the valve seat 27.
  • the valve body 60 releases the annular groove 56 and thereby opens a flow connection between the piston rod-side chamber 48 and the head-side chamber 42 via a feedback channel, which is composed of sections of the working channel 44, the branch 52, the valve bore 24, the valve chamber 82, of the channel section 40 and the working channel 36.
  • valve body 60 and thus also the valve body 70 to the right is prevented when the end of the valve rod 76 abuts against the bottom of the blind bore 90 in the sealing plug 30.
  • the two valve bodies 60, 70 are in their feedback position, in which the liquid coming from the pump 12 flows via the control channel 32, the valve chamber 82 and the working channel 40, 36 into the head-side chamber 42, into which the same at the same time, liquid flows out of the piston rod-side chamber 48 via the feedback channel.
  • the piston of the hydraulic cylinder 20 moves to the right, the liquid displaced from the chamber 48 on the piston rod side is returned directly to the chamber 42 on the head side.
  • This additional amount of liquid directed into the head-side chamber 42 compensates for the fact that the head-side chamber 42 has a larger volume than the piston rod-side chamber 48; this additional amount of liquid reduces the amount of liquid required by the pump 12 when the piston is extended, so that the extension of the hydraulic motor or the hydraulic piston 20 is accelerated.
EP82104683A 1981-06-01 1982-05-28 Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin Expired EP0066274B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82104683T ATE15253T1 (de) 1981-06-01 1982-05-28 Ventilanordnung zur erhoehung der ausfahrgeschwindigkeit eines arbeitszylinders.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US269110 1981-06-01
US06/269,110 US4397221A (en) 1981-06-01 1981-06-01 Regenerative valve

Publications (2)

Publication Number Publication Date
EP0066274A1 true EP0066274A1 (fr) 1982-12-08
EP0066274B1 EP0066274B1 (fr) 1985-08-28

Family

ID=23025843

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82104683A Expired EP0066274B1 (fr) 1981-06-01 1982-05-28 Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin

Country Status (8)

Country Link
US (1) US4397221A (fr)
EP (1) EP0066274B1 (fr)
AT (1) ATE15253T1 (fr)
CA (1) CA1169742A (fr)
DE (1) DE3265820D1 (fr)
ES (1) ES8306235A1 (fr)
FI (1) FI70302C (fr)
ZA (1) ZA823823B (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2522109A1 (fr) * 1982-02-22 1983-08-26 Cessna Aircraft Co Soupape a regeneration
EP0709577A1 (fr) * 1994-10-28 1996-05-01 Kuhn S.A. Valve à quatre orifices de raccordement et deux positions

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5014734A (en) * 1990-08-31 1991-05-14 Caterpillar Inc. Quick drop valve
US5251705A (en) * 1992-03-19 1993-10-12 Deere & Company Electrical trigger for quick drop valve
US5233909A (en) * 1992-07-21 1993-08-10 Decatur Cylinder, Inc. Integral regenerative fluid system
US5226348A (en) * 1992-12-14 1993-07-13 Caterpillar Inc. Electro-hydraulic quick drop circuit
US5370038A (en) * 1992-12-21 1994-12-06 Caterpillar Inc. Regeneration circuit for a hydraulic system
US6094910A (en) * 1995-12-22 2000-08-01 Maritime Hydraulics As Apparatus and method for raising and lowering a piston in a piston cylinder arrangement in a derrick
KR19990087371A (ko) * 1996-02-28 1999-12-27 모서 다니엘 내하중 브레이크 밸브
US5682955A (en) * 1996-09-06 1997-11-04 Caterpillar Inc. Blade control system for an earthmoving blade
US5960814A (en) * 1997-09-12 1999-10-05 Ngt, Llc. Counter balanced locking valve
KR100611713B1 (ko) * 2004-10-14 2006-08-11 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 재생기능을 구비한 유압제어밸브
US8262058B2 (en) * 2008-08-28 2012-09-11 Kot Norbert J Balanced pilot operated check valve
US20100090143A1 (en) * 2008-08-28 2010-04-15 Kot Norbert J Dual locking valve
WO2014171953A1 (fr) 2013-04-19 2014-10-23 Cascade Corporation Fixation de serrage à circuit hydraulique régénérateur
US9611871B2 (en) 2013-09-13 2017-04-04 Norbert J. Kot Pneumatic valve assembly and method
US10914322B1 (en) 2016-05-19 2021-02-09 Steven H. Marquardt Energy saving accumulator circuit
US10550863B1 (en) 2016-05-19 2020-02-04 Steven H. Marquardt Direct link circuit
US11015624B2 (en) 2016-05-19 2021-05-25 Steven H. Marquardt Methods and devices for conserving energy in fluid power production

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2590454A (en) * 1949-09-13 1952-03-25 John S Pilch Hydraulic by-pass system and valve therefor
US2890683A (en) * 1952-02-06 1959-06-16 John S Pilch Fluid actuated control valve means for fluid motors
US3439583A (en) * 1966-04-14 1969-04-22 Parker Hannifin Corp Flow control valve having a pressure limiting tubular valve member
US3568707A (en) * 1968-12-16 1971-03-09 Int Harvester Co Quick drop valve
GB1579287A (en) * 1976-06-10 1980-11-19 Sanyo Kiki Kk Speed-up devices for reciprocating cylinders

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR694928A (fr) * 1929-04-27 1930-12-09 Waterbury Tool Co Perfectionnements aux mécanismes de commande des machines-outils
US2379180A (en) * 1940-02-10 1945-06-26 Vickers Inc Hydraulic retractor control
US2267284A (en) * 1941-03-10 1941-12-23 Livers Carlos Benjamin By-pass valve
US2367682A (en) * 1943-04-09 1945-01-23 Adel Prec Products Corp Landing gear by-pass valve
US2376519A (en) * 1943-07-29 1945-05-22 French Oil Mill Machinery Valve control for presses and the like
US2694384A (en) * 1949-06-21 1954-11-16 Carroil L Evans Control mechanism for hydraulic rams with automatic and adjustable selfstopping mechanism
US2628731A (en) * 1949-09-17 1953-02-17 Bucyrus Erie Co Hydraulically operated tractor shovel
US2646025A (en) * 1951-02-07 1953-07-21 Bendix Aviat Corp By-pass valve for hydraulic motors
US3237636A (en) * 1962-01-22 1966-03-01 Hough Co Frank Controlled pressure by pass valve
US3234957A (en) * 1963-04-22 1966-02-15 Fawick Corp Adjustable, metered directional flow control arrangement
US3319653A (en) * 1963-11-21 1967-05-16 Borg Warner Flow control valves
US3267961A (en) * 1964-04-16 1966-08-23 New York Air Brake Co Valve
US3335739A (en) * 1964-12-03 1967-08-15 New York Air Brake Co Valve
US3448685A (en) * 1967-08-01 1969-06-10 Caterpillar Tractor Co Quick drop valve for bulldozer blade hydraulic controls
US3465788A (en) * 1967-09-01 1969-09-09 Koehring Co Hydraulic control valve with void prevention means
US3474824A (en) * 1968-01-17 1969-10-28 Deere & Co Dump valve for hydraulic control system
US3474708A (en) * 1968-01-17 1969-10-28 Parker Hannifin Corp Valve assembly for fluid motors and the like
US3497032A (en) * 1968-07-01 1970-02-24 Allis Chalmers Mfg Co Balanced hydraulic steering system
US3654835A (en) * 1970-05-25 1972-04-11 Ato Inc Regeneration valve
US3795177A (en) * 1971-11-04 1974-03-05 Caterpillar Tractor Co Fluid motor control circuit providing selective fast motion
DE2648608C3 (de) * 1976-10-27 1979-11-29 Walter Hunger Kg, 8770 Lohr Steuereinrichtung für einen Differentialzylinder
US4144947A (en) * 1976-12-10 1979-03-20 David Brown Tractors Limited Power steering systems
US4216702A (en) * 1978-05-01 1980-08-12 Eaton Yale Ltd. Pressure sensing regenerative hydraulic system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2590454A (en) * 1949-09-13 1952-03-25 John S Pilch Hydraulic by-pass system and valve therefor
US2890683A (en) * 1952-02-06 1959-06-16 John S Pilch Fluid actuated control valve means for fluid motors
US3439583A (en) * 1966-04-14 1969-04-22 Parker Hannifin Corp Flow control valve having a pressure limiting tubular valve member
US3568707A (en) * 1968-12-16 1971-03-09 Int Harvester Co Quick drop valve
GB1579287A (en) * 1976-06-10 1980-11-19 Sanyo Kiki Kk Speed-up devices for reciprocating cylinders

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2522109A1 (fr) * 1982-02-22 1983-08-26 Cessna Aircraft Co Soupape a regeneration
EP0709577A1 (fr) * 1994-10-28 1996-05-01 Kuhn S.A. Valve à quatre orifices de raccordement et deux positions
FR2726343A1 (fr) * 1994-10-28 1996-05-03 Kuhn Sa Valve a quatre orifices de raccordement et deux positions
US5749390A (en) * 1994-10-28 1998-05-12 Kuhn S.A. Valve having four connection ports and two positions

Also Published As

Publication number Publication date
US4397221A (en) 1983-08-09
FI70302B (fi) 1986-02-28
FI821849A0 (fi) 1982-05-24
ATE15253T1 (de) 1985-09-15
ES512689A0 (es) 1983-05-01
CA1169742A (fr) 1984-06-26
DE3265820D1 (en) 1985-10-03
FI70302C (fi) 1986-09-15
EP0066274B1 (fr) 1985-08-28
ES8306235A1 (es) 1983-05-01
ZA823823B (en) 1984-01-25

Similar Documents

Publication Publication Date Title
EP0066274B1 (fr) Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin
DE3323363C2 (fr)
DE2602050C3 (de) Hydraulisches Verstärkerventil, insbesondere für eine hydraulische Bremsanlage eines Kraftfahrzeuges
DE3913460C2 (de) Hydraulisches Umsteuerventil
DE1576088A1 (de) Schnellentlastungsventil fuer hydraulische Kraftzylinder
DE3013381C2 (de) Arbeitskolben-Zylinder-Einheit
DE102005035633A1 (de) Servomotor
EP0937206B1 (fr) Moteur de positionnement pneumatique ou hydraulique muni d'un dispositif de desenclenchement
WO1989007065A1 (fr) Direction a essieux multiples
DE3114243A1 (de) "kraftverstaerker fuer kraftfahrzeuge"
DE3207571C2 (de) Doppeltwirkender, in den Endlagen selbsttätig umsteuernder hydraulischer Druckwandler
DE2123263C2 (de) Hydraulischer Antrieb für Eilvorlauf, Arbeitshub und Eilrücklauf
AT394764B (de) Hydraulischer druckuebersetzer
EP1135614A1 (fr) Clapet de non retour pilote destine a un systeme de portes pressions
DE10108257B4 (de) Hydraulikzylinder
DE19757157C2 (de) Hydraulischer Linearantrieb
DE3048229C2 (de) Rückschlagventil für Grubenausbaustempel
DE102008059437B3 (de) Hydraulisches Steuerventil mit zwei Steuerkolben für einen einseitig arbeitenden Differentialzylinder
DE3925298C2 (de) Hydrostatisches Getriebe
DE19523420C1 (de) Hydraulische Formschließvorrichtung für eine Spritzgießmaschine
WO1994029158A1 (fr) Direction assistee pour automobiles
DE4228945A1 (de) Hydraulisches Ventil
EP0384157B1 (fr) Soupape à deux voies à commande pilotée hydrauliquement en manière à siège
EP1510699B1 (fr) Procédé et dispositif pour commuter un flux
DE102004024354A1 (de) Antrieb für eine Stanz- oder Umformmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE DE FR GB IT NL SE

ITCL It: translation for ep claims filed

Representative=s name: LENZI & C.

EL Fr: translation of claims filed
17P Request for examination filed

Effective date: 19821210

TCNL Nl: translation of patent claims filed
ITF It: translation for a ep patent filed

Owner name: LENZI & C.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): AT BE DE FR GB IT NL SE

REF Corresponds to:

Ref document number: 15253

Country of ref document: AT

Date of ref document: 19850915

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3265820

Country of ref document: DE

Date of ref document: 19851003

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

Free format text: ORIGINAL CODE: 0009261

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

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

26N No opposition filed
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19910502

Year of fee payment: 10

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

Ref country code: BE

Payment date: 19910522

Year of fee payment: 10

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

Ref country code: NL

Payment date: 19910531

Year of fee payment: 10

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

Ref country code: AT

Effective date: 19920528

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

Ref country code: BE

Effective date: 19920531

BERE Be: lapsed

Owner name: DEERE & CY

Effective date: 19920531

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

Ref country code: NL

Effective date: 19921201

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
EAL Se: european patent in force in sweden

Ref document number: 82104683.6

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

Ref country code: GB

Payment date: 19980427

Year of fee payment: 17

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

Ref country code: FR

Payment date: 19980515

Year of fee payment: 17

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

Ref country code: SE

Payment date: 19980518

Year of fee payment: 17

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

Ref country code: DE

Payment date: 19980725

Year of fee payment: 17

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

Ref country code: GB

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

Effective date: 19990528

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

Ref country code: SE

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

Effective date: 19990529

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

Effective date: 19990528

EUG Se: european patent has lapsed

Ref document number: 82104683.6

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

Ref country code: FR

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

Effective date: 20000131

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

Ref country code: DE

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

Effective date: 20000301

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST