EP0066274B1 - Ventilanordnung zur Erhöhung der Ausfahrgeschwindigkeit eines Arbeitszylinders - Google Patents
Ventilanordnung zur Erhöhung der Ausfahrgeschwindigkeit eines Arbeitszylinders Download PDFInfo
- Publication number
- EP0066274B1 EP0066274B1 EP82104683A EP82104683A EP0066274B1 EP 0066274 B1 EP0066274 B1 EP 0066274B1 EP 82104683 A EP82104683 A EP 82104683A EP 82104683 A EP82104683 A EP 82104683A EP 0066274 B1 EP0066274 B1 EP 0066274B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- passage
- fluid
- working
- 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.)
- Expired
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 valve arrangement for increasing the extension speed of a double-acting working cylinder with a single-sided piston rod or a double-acting differential cylinder, consisting of an unlockable check valve and a spring-loaded bypass valve displaced fluids in the piston-end cylinder chamber provided fluid return line have the bypass valve.
- Such a control device for a differential cylinder can be found in DE-B-2 648 608.
- a control device for a single- or multi-stage differential cylinder that can be pressurized with hydraulic fluid on both sides, with a piston that is not completely leak-free sealed, with an unlockable check valve in the pressure medium line leading to the piston side, with a check valve that opens towards the cylinder and is arranged in the pressure medium line on the piston rod side, and with a directional control valve for connecting the cylinder chambers when the piston side is pressurized.
- the directional control valve is designed as a 2/2-way valve, the control element of which is connected to the check valve element on the piston rod side.
- the directional control valve is open when the check valve is closed.
- the check valve member is acted upon in the closing direction by the piston-side pressure. This valve arrangement is intended to ensure that the cylinder spaces are always connected to one another except when the piston rod side is pressurized.
- the first control channel forms, together with the first working channel, an extension channel which is guided through the valve housing and which forms a pressure fluid source, e.g. B. connects a pump with the piston-side cylinder chamber of a working cylinder.
- the second control channel forms, together with the second working channel, an intake channel which is guided through the valve housing and which connects a liquid reservoir or a sump to the cylinder chamber of the working cylinder on the piston rod side.
- the second working channel forms, together with the first working channel, a fluid return channel which is guided through the valve housing and which connects the two cylinder spaces of the working cylinder mentioned to one another.
- valve bodies mentioned above 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, 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 object of the invention is to improve the functionality of the valve arrangement described at the outset, in particular when the piston rod of a working cylinder under high load is extended.
- this object is achieved according to the invention in that the check valve and the bypass valve are arranged coaxially. wherein the bypass valve member serves as an unlocking piston for the check valve, which prevents the suction of fluid from the first fluid line to the piston-side cylinder chamber in its closed normal position.
- bypass valve member has a first end face and a second end face which are acted upon by the liquid pressure in the first control channel or 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 causes the bypass valve member into its second valve position against the action of the second spring element, the bypass valve member displacing the check valve member into its open position during this displacement via a driving device.
- the new valve arrangement is simple and compact. It works absolutely reliably under all operating conditions.
- the driving device between the two valve members consists of a driving surface on the bypass valve member and a driving surface on the rear. there is a check valve that comes into mutual contact after a displacement of the bypass valve member.
- 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.
- 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 valve arrangement 18 for increasing the extension speed of the cylinder 20 is connected between this directional control valve 16 and a double-acting hydraulic working cylinder with a one-sided piston rod 20 or a differential cylinder.
- the valve arrangement 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, which is connected via a Section 40 at the valve seat 26 opens into the valve bore 24.
- 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 and 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 extends 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 is supported so that the spring 80 presses the valve head 72 against the valve seat 26.
- Both springs 68, 80 press 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 encloses 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 form a first and a second valve chamber 82, 84.
- the first valve chamber 82 communicates with the control channel 32 and via the section 40 with the first working channel 36, while the second valve chamber 84 is connected to the second control channel 34 and via the branch 50 and the annular groove 54 to the second working channel 44.
- the valve chambers 82, 84 are never in a fluid-exchanging connection with one another. This is ensured by the fact that only one of the two ring 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 can be connected via branch lines 37, 45 to other hydraulic motors or the like which are not shown in the drawing. These branch lines can be inside or outside the valve housing 22.
- the directional control valve 16 is actuated so 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 compared 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 motor or of the hydraulic working cylinder 20 is shifted to the left (refer to FIG.
- the control channel 32 are connected to the pump 12 and the control channel 34 to the sump 14 via the directional control valve 16.
- a high load in the direction of the extension of the cylinder piston leads to an increase in pressure in the chamber 48 on the piston rod side, which counteracts movement of the valve body 60 to the right in the valve chamber 84.
- the valve head 72 is still in contact with the valve seat 26 and thus prevents a flow outflow from the valve chamber 82.
- an increase in pressure is generated in this valve chamber 82 which very quickly rises in the valve chamber 84 prevailing pressure.
- 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. Under the effect of the 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. While the valve body 70 maintains its closing 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. As a result, 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.
- valve body 60 By moving the valve body 60 further to the right pushes, it strikes with its right end face against the flange 78 and takes the valve body 70 with it during its further displacement, 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 fluid return line, which is composed of sections of the working channel 44, the branch 52, the valve bore 24, the valve chamber 82 , 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 return 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 liquid also flows at the same time 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 during the extension of the piston, so that the extension of the hydraulic working cylinder 20 is accelerated.
Landscapes
- Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid-Pressure Circuits (AREA)
- Valve Device For Special Equipments (AREA)
- Actuator (AREA)
- Hydraulic Control Valves For Brake Systems (AREA)
- Forklifts And Lifting Vehicles (AREA)
- Compressor (AREA)
- External Artificial Organs (AREA)
- Chemical And Physical Treatments For Wood And The Like (AREA)
- Control Of Presses (AREA)
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 EP0066274A1 (de) | 1982-12-08 |
EP0066274B1 true EP0066274B1 (de) | 1985-08-28 |
Family
ID=23025843
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP82104683A Expired EP0066274B1 (de) | 1981-06-01 | 1982-05-28 | Ventilanordnung zur Erhöhung der Ausfahrgeschwindigkeit eines Arbeitszylinders |
Country Status (8)
Country | Link |
---|---|
US (1) | US4397221A (xx) |
EP (1) | EP0066274B1 (xx) |
AT (1) | ATE15253T1 (xx) |
CA (1) | CA1169742A (xx) |
DE (1) | DE3265820D1 (xx) |
ES (1) | ES512689A0 (xx) |
FI (1) | FI70302C (xx) |
ZA (1) | ZA823823B (xx) |
Families Citing this family (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4723476A (en) * | 1982-02-22 | 1988-02-09 | The Cessna Aircraft Company | Regenerative valve |
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 |
FR2726343B1 (fr) * | 1994-10-28 | 1997-01-24 | Kuhn Sa | Valve a quatre orifices de raccordement et deux positions |
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 |
JP3617841B2 (ja) * | 1996-02-28 | 2005-02-09 | ブーヘル・ヒドラウリクス・アクチェンゲゼルシャフト | 負荷保持制動弁 |
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 |
US20100090143A1 (en) * | 2008-08-28 | 2010-04-15 | Kot Norbert J | Dual locking valve |
US8262058B2 (en) * | 2008-08-28 | 2012-09-11 | Kot Norbert J | Balanced pilot operated check valve |
WO2014171953A1 (en) | 2013-04-19 | 2014-10-23 | Cascade Corporation | Clamping attachment with regenerative hydraulic circuit |
US9611871B2 (en) | 2013-09-13 | 2017-04-04 | Norbert J. Kot | Pneumatic valve assembly and method |
US11015624B2 (en) | 2016-05-19 | 2021-05-25 | Steven H. Marquardt | Methods and devices for conserving energy in fluid power production |
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 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4144947A (en) * | 1976-12-10 | 1979-03-20 | David Brown Tractors Limited | Power steering systems |
DE2648608B2 (de) * | 1976-10-27 | 1979-03-29 | Walter Hunger Kg, 8770 Lohr | Steuereinrichtung für einen Differentialzylinder |
Family Cites Families (26)
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 |
US2590454A (en) * | 1949-09-13 | 1952-03-25 | John S Pilch | Hydraulic by-pass system and valve therefor |
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 |
US2890683A (en) * | 1952-02-06 | 1959-06-16 | John S Pilch | Fluid actuated control valve means for fluid 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 |
US3439583A (en) * | 1966-04-14 | 1969-04-22 | Parker Hannifin Corp | Flow control valve having a pressure limiting tubular valve member |
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 |
US3474708A (en) * | 1968-01-17 | 1969-10-28 | Parker Hannifin Corp | Valve assembly for fluid motors and the like |
US3474824A (en) * | 1968-01-17 | 1969-10-28 | Deere & Co | Dump valve for hydraulic control system |
US3497032A (en) * | 1968-07-01 | 1970-02-24 | Allis Chalmers Mfg Co | Balanced hydraulic steering system |
US3568707A (en) * | 1968-12-16 | 1971-03-09 | Int Harvester Co | Quick drop valve |
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 |
JPS5730483Y2 (xx) * | 1976-06-10 | 1982-07-05 | ||
US4216702A (en) * | 1978-05-01 | 1980-08-12 | Eaton Yale Ltd. | Pressure sensing regenerative hydraulic system |
-
1981
- 1981-06-01 US US06/269,110 patent/US4397221A/en not_active Expired - Lifetime
-
1982
- 1982-05-10 CA CA000402602A patent/CA1169742A/en not_active Expired
- 1982-05-24 FI FI821849A patent/FI70302C/fi not_active IP Right Cessation
- 1982-05-28 DE DE8282104683T patent/DE3265820D1/de not_active Expired
- 1982-05-28 AT AT82104683T patent/ATE15253T1/de not_active IP Right Cessation
- 1982-05-28 EP EP82104683A patent/EP0066274B1/de not_active Expired
- 1982-05-31 ES ES512689A patent/ES512689A0/es active Granted
- 1982-06-01 ZA ZA823823A patent/ZA823823B/xx unknown
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2648608B2 (de) * | 1976-10-27 | 1979-03-29 | Walter Hunger Kg, 8770 Lohr | Steuereinrichtung für einen Differentialzylinder |
US4144947A (en) * | 1976-12-10 | 1979-03-20 | David Brown Tractors Limited | Power steering systems |
Also Published As
Publication number | Publication date |
---|---|
US4397221A (en) | 1983-08-09 |
CA1169742A (en) | 1984-06-26 |
DE3265820D1 (en) | 1985-10-03 |
FI70302B (fi) | 1986-02-28 |
ZA823823B (en) | 1984-01-25 |
FI70302C (fi) | 1986-09-15 |
FI821849A0 (fi) | 1982-05-24 |
ES8306235A1 (es) | 1983-05-01 |
ES512689A0 (es) | 1983-05-01 |
ATE15253T1 (de) | 1985-09-15 |
EP0066274A1 (de) | 1982-12-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0066274B1 (de) | Ventilanordnung zur Erhöhung der Ausfahrgeschwindigkeit eines Arbeitszylinders | |
DE3323363C2 (xx) | ||
DE3913460C2 (de) | Hydraulisches Umsteuerventil | |
DE1576088A1 (de) | Schnellentlastungsventil fuer hydraulische Kraftzylinder | |
WO1989007065A1 (en) | Multiple-axle steering system | |
WO1985003992A1 (en) | Distributor valve | |
DE1901359A1 (de) | Steuervorrichtung mit Differentialkolben und Schieber | |
DE69405647T2 (de) | Internes Absperrventil | |
DE3213758A1 (de) | Pneumatischer dreistellungs-schaltantrieb, insbesondere zum schalten der stufen von wechselgetrieben | |
DE2403430A1 (de) | Steuerventil mit abgestuftem druckanstieg | |
EP0342409A2 (de) | Sicherheitsventil | |
DE2849704C2 (xx) | ||
DE3817122A1 (de) | Sicherheitsventil | |
DE3207571C2 (de) | Doppeltwirkender, in den Endlagen selbsttätig umsteuernder hydraulischer Druckwandler | |
AT394764B (de) | Hydraulischer druckuebersetzer | |
DE2123263C2 (de) | Hydraulischer Antrieb für Eilvorlauf, Arbeitshub und Eilrücklauf | |
DE3637345C2 (xx) | ||
DE2808477C2 (de) | Druckausgeglichenes Ventil für HFA-Flüssigkeiten | |
DE19757157C2 (de) | Hydraulischer Linearantrieb | |
DE2157347A1 (de) | Ventil, insbesondere für hydraulisch betätigbare Kraftfahrzeugbremsanlagen | |
DE102008059437B3 (de) | Hydraulisches Steuerventil mit zwei Steuerkolben für einen einseitig arbeitenden Differentialzylinder | |
DE3048229C2 (de) | Rückschlagventil für Grubenausbaustempel | |
DE976712C (de) | Steuereinrichtung mit hydraulisch entlastetem Drehschieber | |
DE3925298C2 (de) | Hydrostatisches Getriebe | |
EP0384157B1 (de) | Hydraulisch vorsteuerbares 2-Wege-Einbauventil in Sitzventilbauweise |
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 |