EP0695878A1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

Info

Publication number
EP0695878A1
EP0695878A1 EP95112101A EP95112101A EP0695878A1 EP 0695878 A1 EP0695878 A1 EP 0695878A1 EP 95112101 A EP95112101 A EP 95112101A EP 95112101 A EP95112101 A EP 95112101A EP 0695878 A1 EP0695878 A1 EP 0695878A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
piston
control
load
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
EP95112101A
Other languages
German (de)
English (en)
Other versions
EP0695878B1 (fr
Inventor
Rudolf Brunner
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.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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 Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Publication of EP0695878A1 publication Critical patent/EP0695878A1/fr
Application granted granted Critical
Publication of EP0695878B1 publication Critical patent/EP0695878B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a hydraulic control device, in particular for a hoist.
  • the magnitudes of the pressure fluctuations are known.
  • the damping throttle, the two check valves bypassing the damping throttle in opposite directions under certain operating conditions, and the bypass line with its throttle combination quickly dampen these pressure fluctuations on the control side of the load holding valve.
  • the load pressure acts on the valve closing element in the opening direction.
  • the greater the load the lower the pilot pressure for the load holding valve.
  • the pilot pressure can vary by a power of ten over the load range.
  • the pilot piston cannot be relieved quickly enough, especially when the load pressure is high, via the preloaded check valve that opens in the direction of control to bypass the damping throttle and / or the damping throttle. There is a dangerous wake of the hydraulic motor.
  • the invention has for its object to provide a hydraulic control device, in which pressure fluctuations are quickly dampened in their effect on the load holding valve, but follow-up movements of the hydraulic motor are avoided even under adverse operating conditions when the load is stopped intentionally.
  • the control device works properly. Pressure vibrations quickly subside on the control side of the load holding valve and also in the overall system. Caster movements occur when the load is stopped intentionally, even under extreme conditions Operating conditions no longer.
  • the response behavior of the damping device can be matched precisely to the known amplitudes of the pressure vibrations.
  • the guard locking valve allows the pressure medium to flow out bypassing the damping throttle damping the control movement in order to intentionally and reliably control the load holding valve when required, even in the event of an emergency shutdown of the system or when the pressure medium is cold.
  • the spring load of the valve closing element of the load holding valve which is unaffected by the load pressure, then either opens the hold-open valve used only for damping or the hold-open valve is relieved by means of the piston in order to stop the load precisely.
  • the damping device has, so to speak, a built-in intelligence that enables it to recognize whether damping or control is required in order to react accordingly.
  • pressure-relieved load-holding valves are known from DE-A1-32 37 103 and DE-A1-35 09 952.
  • the control piston has the same pressure surface as the valve closing element, so that only one damping device can be handled with one in the control direction Damping throttle can be used, the damping effect is inadequate, and which delays the activation of the load holding valve in the event of pressure fluctuations, cold pressure medium or in the event of an emergency shutdown.
  • the auxiliary damper is provided to prevent the load from suddenly stopping when the tumbler valve responds quickly, which could cause pressure fluctuations again. It is expediently adjustable in order to enable a fine adjustment to the operating conditions.
  • the locking valve does not allow any pressure medium flow from the pilot pressure line to the pilot piston, but only controls the relief of the pilot piston in order to stop the load precisely.
  • the locking valve forces the damping device to work in the shut-off position. In the open position, the damping device disables the precise control of the load holding valve.
  • the embodiment according to claim 4 is structurally simple and reliable.
  • the larger acting area of the piston compared to the acting area of the closing member ensures that the locking valve remains in the blocking position even during the pressure oscillations and forces the damping device to work as intended.
  • the area ratio is selected in view of the known magnitude of the amplitudes of the pressure vibrations in order to ensure that the locking valve essentially only opens the bypass line to the tank when the pressure drop in the pilot pressure line (via the directional control valve or in the event of a safety shutdown) is the required condition of stopping the load.
  • the locking valve nevertheless remains in the shut-off position and also with pressure fluctuations with the predetermined amplitudes. If the load holding valve is to be activated, the locking valve goes into the open position. The volume of pressure medium, which is displaced by the control piston, reaches the tank without resistance, so that there is no annoying traffic jam. In order to be able to cover the known range of the amplitudes of the pressure vibrations in such a way that the hold-open valve does not get into the passage position during the pressure vibrations, an area ratio of, for example, 1: 3 is advantageous in favor of the piston.
  • the tumbler valve is a spring-biased check valve which, like the tumbler valve with the piston, enables pressure relief of the control piston under critical operating conditions.
  • the preload must always be overcome so that a residual pressure may remain on the control piston, which is reduced via the damping throttle.
  • the low opening pressure is sufficient to intentionally control the load holding valve in critical situations.
  • the hydraulic control device can be very sensitively adapted to the respective operating conditions of the hoist.
  • the manufacturer does not have to provide any adjustability of the spring load, but will adjust the spring load from the outset to ensure that the control device functions optimally.
  • the load holding valve can be activated quickly and quickly without setting an extremely high pilot pressure with the directional control valve.
  • the large actuation area of the control piston results in a large control volume which is favorable for the rapid damping of the pressure oscillations.
  • a seat valve also absorbs large load pressures without leakage in the closed position. Since the spring load is selected without taking the respective load pressure into account, this results in a clean opening and closing behavior with effective damping for the load holding valve.
  • the volume control of the outflowing pressure medium is carried out sensitively via the metering holes, since the spool works with the fitting hole and the valve seat.
  • the control piston is outside the flow path of the working pressure medium and cooperates with the slide piston, which transfers the movement and force of the control piston when opening.
  • the valve closing element of the load holding valve is pressure-balanced with respect to the pressure introduced by the directional control valve.
  • an opening pressure results for the pilot piston which only varies within a very narrow range, e.g. depending on how far the valve closing element is lifted from the valve seat or which spring characteristic has the spring acting on the valve closing element in the closing direction and generating the spring load.
  • a small range of variation of the pilot pressure is favorable because pressure conditions are easily manageable under all operating conditions and the influence of the damping device can be precisely predetermined.
  • the relief to the tank avoids any disturbing influences of a dynamic pressure on the control function of the load holding valve.
  • clean control of the outflowing pressure medium is achieved if the differently sized metering bores in the piston slide are released depending on the stroke and determine a precisely predetermined course of the enlargement of the flow area.
  • a structurally simple, and compact embodiment emerges from claim 11.
  • the space available in the housing chamber is used for the check valve. There is enough space in use for generously dimensioned through openings that ensure low-loss flow through the open check valve.
  • the spool has an additional function because it is used to guide the circular ring in the housing chamber. It can be taken into account in a structurally simple manner that the load holding valve, which is pressure-balanced with respect to the load pressure, does not have a shock valve function can perform.
  • An additional shock valve then bypasses the controlled load holding valve to the tank.
  • the bypass line and possibly the bypass line are connected to the line leading from the shock valve to the tank.
  • the load pressure balanced load holding valve with the damping device, the hydraulic pilot ratio and the geometric area ratio between the pilot piston and the valve closing element as well as the response behavior of the tumbler valve can be designed precisely to the known pressure values of the pressure fluctuations in the pilot pressure line.
  • the interaction of the individual components results in a rapid damping of the pressure vibrations.
  • the overrun of the hydraulic motor is reliably prevented when the control is required.
  • a hydraulic control device S for a hydraulic motor Z designed as a double-acting cylinder is supplied with pressure medium from a pressure source P from a tank T in order to adjust a piston 1 in the hydraulic motor V.
  • the control device S contains a directional control valve W, e.g. a 4/3-way control valve with pressure-relieved middle position, a load holding valve L and a damping device D.
  • the directional control valve W is connected via working lines 4, 5 to working spaces 3, 4 of the hydraulic motor V.
  • the working line 5 is divided into sections 5a, 5b, between which the load holding valve L is arranged.
  • the load holding valve L has a control side 6 in a housing 7, to which a control pressure line 8 is connected, which branches off from the working line 4.
  • the damping device D is arranged in the pilot pressure line 8 between sections 8a and 8b. It includes a, preferably adjustable, damping throttle 9, a check valve 10 opening in the flow direction to the control side 6, a hold-open valve Z opening in the flow direction from the control side 6 to the working line 4, for example a check valve 11 which is preloaded with a spring 12, and one bypass line 13 branching off from the pilot pressure line 8 to the tank T between the sections 8a and 8b.
  • a throttle passage 15 is provided, which is provided with an interference throttle passage 14 cooperates in the bypass line 13.
  • the interference throttle passage 14 is slightly larger than the throttle passage 15 (area ratio, for example, 0.6: 0.5 mm).
  • a line 16 branches off to the tank, in which a pressure-controlled pressure-limiting valve 17, which works as a shock valve, is contained.
  • the bypass line 13 is connected to the line 16 downstream of the pressure relief valve 17.
  • a spring chamber 18 is connected to a housing chamber 19 by a valve seat 20.
  • the line section 5b is connected to the spring chamber 18, while the line section 5a is connected to the housing chamber 19.
  • a valve closing element C arranged in the spring chamber 18 with a conical or spherical seat surface 21 cooperates with the valve seat 20. This is located in an insert 27, which is fixed removably by means of a spring housing 45.
  • the valve closing element C is acted upon by a spring 44 in the closing direction on the valve seat 20.
  • Part of the valve closing element C is a hollow slide piston 22, which is displaceably guided in a fitting bore 26 of the insert 27 and projects into a control chamber 32 with its free end 23 which penetrates a housing chamber wall 31 in a sealed manner.
  • metering holes 24 of different sizes are arranged near the seat surface, such that a plurality of smaller metering holes 24 are positioned closer to the seat surface 21 than a number of larger metering holes 24.
  • 22 passages 25 are formed in the casing of the piston valve 22.
  • a check valve R opening in the flow direction from the spring chamber 18 into the housing chamber 19 is contained in the housing chamber 19. This consists of several passages 28 and an annular disc 29 which is guided on the slide piston 22 and is acted upon by a spring 30 in the closing direction.
  • a control piston 35 is guided in a sealed, displaceable manner and cooperates with the free end 23 of the slide piston 22.
  • a part of the control chamber 32 is either connected to the spring chamber 18 via a channel 33 or to the tank via a channel 33 '.
  • the lower part of the control chamber 32, which is closed by a plug 36, is connected via a channel 34 to the control side 6 and the section 8b of the control pressure line 8.
  • the valve closing element C is pressure-balanced both with respect to the load pressure of the working chamber 2 prevailing in the housing chamber 19 because the load pressure acts radially on the outer circumference of the slide piston 22, and also via the channel 33 with respect to the pressure prevailing in the spring chamber 18 or via the channel 33 'to tank T.
  • Fig. 1 is the hydraulic motor V.
  • the load pressure in the working chamber 3 is received by the check valve R, by the spring 44 pressed on the valve seat 20 valve closing element C and by the pressure relief valve 17.
  • the directional control valve W is switched to the right position.
  • the working line 5 is connected to the pressure source P, while the working line 4 is connected to the tank T.
  • the pressure lifts the circular ring 29 from the passages 28, the pressure medium flows to the working space 3 essentially unthrottled.
  • the piston 1 is raised. Pressure medium is pressed out of the working space 2 via the working line 4 and the directional control valve W into the tank T.
  • the directional control valve W is adjusted to the central position.
  • the directional control valve W is switched to the left position, in which the working line 4 is connected to the pressure source and the working line 5 to the tank.
  • the check valve R blocks.
  • a pilot pressure is derived in the pilot pressure line 8, which lifts the pilot piston 35 and lifts the seat surface 21 from the valve seat 20 against the spring loading of the spring 44 via the piston slide 22.
  • Some of the metering openings 24 pass over the valve seat 20.
  • the pressure medium flows through the passages 25 and the exposed metering openings 24 into the spring chamber 18 and via section 5b of the working line 5 to the tank.
  • the directional control valve W is reset to the middle position shown.
  • the pilot pressure on the control piston 35 is reduced via the damping throttle 9, provided that the pressure difference of the damping throttle 9 remains below the biasing force of the spring 12.
  • the spring 44 presses the seat surface 21 onto the valve seat 20 so that the piston 1 is stopped and the load pressure is maintained. If the pressure difference across the damping throttle 9 exceeds the prestress of the spring 12 when the control is activated, the check valve 11 opens in the flow direction to the bypass line 13 and the working line 4, so that the load holding valve L controls properly.
  • the bias of the check valve 11 applied by the spring 12 is less than the pressure that can be generated by the spring loading of the spring 44 on the control piston 35, specifically by a value of approximately 2 to 15 bar, preferably approximately 3 bar.
  • the check valve 11 can open, for example, when the pressure medium is cold and viscous, if the pressure difference across the damping throttle 9 exceeds the pretension of the spring 12 when the pressure in section 8a is reduced, and also in the case of a so-called emergency shutdown in which the pressure in section 8a despite the fully open directional control valve W. abruptly falls and possibly also in the case of pressure fluctuations, such as typically arise when the piston 1 begins to move in the lowering direction under a load in the pilot pressure line 8 and in the entire system.
  • the control device is shown as a block diagram, the hydraulic motor V being loaded with a load V 1.
  • the pressures when controlling a movement of the piston in FIG. 2 to the left are tapped, which are shown in the pressure / time diagram in FIGS. 3 and 4.
  • the rod-side pressure p sta in the working line 4 is tapped off at the interface 37.
  • the control pressure p d prevailing between the throttle passage 15 and the damping throttle 9 is tapped at the interface 38.
  • the control pressure p stk effective on the control piston 35 is tapped.
  • the curve of the rod-side pressure p sta over time is shown as a solid curve.
  • the dash-dot-dot-dash curve above illustrates fluctuations in the load pressure and the load V 1.
  • the dashed curve represents the course of the control pressure p d .
  • the dash-dotted curve finally illustrates the course of the pilot pressure p stk when the spring 12 is set to a preload of 15 bar.
  • the pressure p sta initially rises steeply to approx. 80 bar and then drops again to approx. 22 bar within approx. 2 seconds. This first amplitude is followed by further weaker pressure waves within approx. 4 seconds, initially up to approx. 52 bar with a drop down to 45 bar, then again up to approx. 62 bar with a drop down to 30 bar. Thanks to the throttle passage 15 in the pilot pressure line 18, which cooperates with the interference throttle passage 14 in the bypass line 13, these pressure waves at the interface 38 are already significantly damped and reduced in effectiveness. The control pressure p d rises steeply up to 32 bar within about half a second and then drops to 10 bar within about 2 seconds.
  • This first amplitude is followed by further, smaller amplitudes, first up to 20 bar and then up to 25 bar, which end significantly dampened compared to curve p sta .
  • the pilot pressure p stk initially follows the control pressure p d up to approx. 32 bar.
  • the load holding valve is opened.
  • the piston 1 begins its movement. When the movement starts, the rod-side pressure Psta collapses, and the control pressure p d also drops as a result.
  • the damping throttle 9 is effective while the check valve 11 remains closed by the spring 12. Up to a region 40, the pilot pressure p stk drops gently due to the influence of the damping throttle 9.
  • the pressure difference across the damping throttle 9 exceeds the pretension of the spring 12.
  • the check valve 11 opens, the pilot pressure p stk drops to approximately 23 bar.
  • the check valve 11 closes in the area 41, so that only the damping throttle 9 acts and the pilot pressure p stk can drop slightly up to the area 42. From region 42, there is a further increase in the pilot pressure p stk from approximately 20 bar to 25 bar in region 43, because the control pressure p d also increases to approximately 25 bar. From region 43, the opening pressure p stk only drops slightly.
  • the diagram in FIG. 4 shows an optimized working behavior of the control device with a check valve 11 pretensioned to approximately 25 bar. Since the preload of the check valve 11 is greater than the pressure difference of the first amplitude of the control pressure p d , the check valve 11 does not respond.
  • the damping throttle 9 dampens the course of the opening pressure p stk from opening the load holding valve.
  • the rod-side pressure p sta and the control pressure p d fluctuate approximately as in FIG. 3.
  • the course of the opening pressure p stk ( dash-dotted ) is ideal, so that the pressure fluctuations cause the opening of the load holding valve do not affect.
  • the load pressure fluctuations V1 sound faster in Fig. 4 than in Fig. 3.
  • the spring loading of the spring 44 on the preload of the check valve 11 or vice versa can be adjusted very precisely in knowledge of the course of the pressure fluctuations in the control pressure p d in order to achieve optimal damping on the one hand and nevertheless to ensure the reliable control of the load holding valve on the other hand.
  • the hydraulic control ratio by means of the throttle passages 15 and 14 and the geometric area ratio between the control piston 35 and the valve closing element C can also be selected with a view to optimal damping of pressure fluctuations and to the control and activation of the load holding valve.
  • the separation between the valve closing element C and the control piston 35 results in structural simplifications.
  • the control piston 35 can be so large that a large amount of control pressure medium moves in the control line 8 with regard to the damping, and that the load holding valve can nevertheless be controlled with moderate pressure in the working line 4.
  • FIG. 4 also applies to the embodiment of the control device according to FIGS. 5 and 6, in the case of the guard locking valve Z a drain valve 11 'is provided, which does not respond in the lowering process shown in Fig. 4, but is held in a blocking position, by means of the pressure p d .
  • the locking valve Z, 11 'of FIG. 5 is seated in a bypass line 44 from the control side 6 or the line section 8b to the tank T.
  • the detailed structure of this locking valve Z is shown in FIG. 6.
  • the further structure of the control device corresponds to that of FIGS. 1 and 2.
  • the tumbler valve 11 has in a housing 45 a chamber 47 in which a piston 50 is displaceably and sealed in a bushing 48.
  • the piston 50 has an action surface Y on which the pressure of the pilot pressure line 8 (line section 8a) or the bypass line 13 is loaded.
  • the other side of the piston 50 and the chamber 47 is connected via a valve seat 51 to the control side 6 or the line section 8b and at the same time to the bypass line 44 to the tank.
  • a closing member 52 Associated with the valve seat 51 is a closing member 52 designed as a ball, the pressure surface of which is exposed to the pressure on the control piston 35 is indicated by X.
  • the closing member 52 can be pressed against the valve seat 51 by means of the piston 50 in the blocking position of the tumbler valve Z shown in FIG.
  • the application area Y is a multiple of the application area X, so that the shut-off position of the guard locking valve is maintained even if the pressures on the two application areas X, Y are equal.
  • the area ratio Y: X is approximately 3: 1, which means that the pressure in the pilot pressure line 8a can drop to a third of the pressure in the line section 8b without the shutoff position being relinquished.
  • the shut-off position and the through position are abandoned set in which the pressure medium flows from the control side 6 practically without resistance via the bypass line 44 to the tank.
  • the auxiliary damping throttle 46 is expediently connected upstream of the locking valve Z in order to avoid an abrupt stop of the load when the locking valve Z suddenly goes from the shut-off to the through position in the event of sudden pressure reduction in the line section 8a (for example in the case of a safety shutdown).
  • the piston 50 is acted upon by the pressure prevailing in the bypass line 13 between the throttle points 15 and 14, that is to say the pressure prevailing in the line section 8a downstream of the throttle passage.
  • the hold-open valve Z with FIGS. 5 and 6 would only be switched to the open position (with an area ratio Y: X of 3: 1) if the pressure p d was consciously reduced to 10 bar after two seconds , ie to a value to which the pressure p d does not drop under the pressure fluctuations in the system. 5 and 6 therefore remains in the shut-off position during the pressure fluctuations in order to allow the damping device D to come into effect as desired.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Lubricants (AREA)
  • Fluid-Damping Devices (AREA)
EP95112101A 1994-08-03 1995-08-01 Dispositif de commande hydraulique Expired - Lifetime EP0695878B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9412531U 1994-08-03
DE9412531U DE9412531U1 (de) 1994-08-03 1994-08-03 Hydraulische Steuervorrichtung

Publications (2)

Publication Number Publication Date
EP0695878A1 true EP0695878A1 (fr) 1996-02-07
EP0695878B1 EP0695878B1 (fr) 1999-12-01

Family

ID=6911961

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95112101A Expired - Lifetime EP0695878B1 (fr) 1994-08-03 1995-08-01 Dispositif de commande hydraulique

Country Status (3)

Country Link
EP (1) EP0695878B1 (fr)
AT (1) ATE187228T1 (fr)
DE (3) DE9412531U1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3015717B1 (fr) * 2014-10-31 2020-02-26 HAWE Hydraulik SE Plaque filetée pour une soupape
CN114278622A (zh) * 2020-09-28 2022-04-05 哈威液压股份公司 分离式液压阻尼模块和具有分离式液压阻尼模块的负载保持阀

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19940966B4 (de) * 1999-08-28 2005-04-07 Wessel-Hydraulik Gmbh Hydraulische Schaltungsanorndung zum Betrieb von zwei doppelt wirkenden Arbeitszylindern, insbesondere für die Schenkel einer Abbruchschere
EP2372167B1 (fr) * 2010-03-30 2012-11-14 Bosch Rexroth Oil Control S.p.A. Dispositif de contrôle de la pression de pilote, en particulier dans un robinet d'équilibrage

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2559029A1 (de) 1975-12-29 1977-07-07 Heilmeier & Weinlein Bremsventil
DE3216580A1 (de) 1981-05-07 1983-02-24 Hiab-Foco AB, 82401 Hudiksvall Lasthalte- und senkbremsventil
DE3234496A1 (de) 1982-09-17 1984-03-22 Wessel-Hydraulik Günther Wessel, 2940 Wilhelmshaven Hydraulisches sicherheitsventil
DE3237103A1 (de) 1982-10-07 1984-04-12 Wessel-Hydraulik Günther Wessel, 2940 Wilhelmshaven Sicherheitsventil als lasthalteventil in der hebezeughydraulik
DE8510560U1 (de) 1985-04-11 1986-08-28 Beringer-Hydraulik GmbH, Neuheim, Zug Leckfreies Brems-Sperrventil
DE3509952A1 (de) 1985-03-19 1986-10-02 Mannesmann Rexroth GmbH, 8770 Lohr Bremsventil
US4624445A (en) 1985-09-03 1986-11-25 The Cessna Aircraft Company Lockout valve
EP0499694A2 (fr) 1991-02-21 1992-08-26 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique
EP0503266A1 (fr) 1991-03-11 1992-09-16 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2559029A1 (de) 1975-12-29 1977-07-07 Heilmeier & Weinlein Bremsventil
DE3216580A1 (de) 1981-05-07 1983-02-24 Hiab-Foco AB, 82401 Hudiksvall Lasthalte- und senkbremsventil
DE3234496A1 (de) 1982-09-17 1984-03-22 Wessel-Hydraulik Günther Wessel, 2940 Wilhelmshaven Hydraulisches sicherheitsventil
DE3237103A1 (de) 1982-10-07 1984-04-12 Wessel-Hydraulik Günther Wessel, 2940 Wilhelmshaven Sicherheitsventil als lasthalteventil in der hebezeughydraulik
DE3509952A1 (de) 1985-03-19 1986-10-02 Mannesmann Rexroth GmbH, 8770 Lohr Bremsventil
DE8510560U1 (de) 1985-04-11 1986-08-28 Beringer-Hydraulik GmbH, Neuheim, Zug Leckfreies Brems-Sperrventil
US4624445A (en) 1985-09-03 1986-11-25 The Cessna Aircraft Company Lockout valve
EP0499694A2 (fr) 1991-02-21 1992-08-26 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique
EP0503266A1 (fr) 1991-03-11 1992-09-16 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3015717B1 (fr) * 2014-10-31 2020-02-26 HAWE Hydraulik SE Plaque filetée pour une soupape
CN114278622A (zh) * 2020-09-28 2022-04-05 哈威液压股份公司 分离式液压阻尼模块和具有分离式液压阻尼模块的负载保持阀

Also Published As

Publication number Publication date
DE59507312D1 (de) 2000-01-05
ATE187228T1 (de) 1999-12-15
EP0695878B1 (fr) 1999-12-01
DE9412531U1 (de) 1994-09-29
DE59506205D1 (de) 1999-07-22

Similar Documents

Publication Publication Date Title
DE4105459C2 (fr)
EP0883753B1 (fr) Soupape de frein a maintien de charge
EP1781952B1 (fr) Ensemble de commande hydraulique
DE4212550C2 (de) Ventilanordnung mit einem Wegeventil
LU88390A1 (de) Vorsteuerstufe fuer Druckbegrenzungsventile
EP1987278B1 (fr) Soupape pre-asservie de limitation de la pression
EP0503266B1 (fr) Dispositif de commande hydraulique
EP0902194B1 (fr) Soupape à maintien de charge
EP4019802A1 (fr) Agencement de soupape pour un amortisseur de vibrations
CH628117A5 (en) Brake-valve device
EP0695878B1 (fr) Dispositif de commande hydraulique
WO1999008029A1 (fr) Soupape de limitation de pression pilotee
EP0829794B1 (fr) Soupape de siège de réduction de pression
DE3341641A1 (de) Wegeventil mit bremskolben
EP0491155B1 (fr) Distributeur pour commande d'un moteur hydraulique
DE2833971C2 (de) Leitungsbruchsicherungs-Vorrichtung zur Anordnung zwischen einem hydraulischen Steuergerät und wenigstens einem Arbeitszylinder
DE19503943C2 (de) Bremsventilanordnung für einen reversierbaren hydraulischen Verbraucher
DE2104362A1 (de) Druckventil fuer hydraulische anlagen
EP0695877B1 (fr) Dispositif d'amortissement hydraulique
DE19913277A1 (de) Hydraulische Steueranordnung, insbesondere für eine Winde
DE102004016393B4 (de) Stauventil
EP0437717B1 (fr) Soupape à siège
DE19605173C2 (de) Hydraulische Sicherheitsventilanordnung
DE10006620A1 (de) Direktgesteuertes Druckbegrenzungsventil für hydraulische Anlagen
WO2003074883A1 (fr) Dispositif a soupapes

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

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19960313

17Q First examination report despatched

Effective date: 19980713

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE DK FR GB IT LI LU NL SE

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

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19991201

REF Corresponds to:

Ref document number: 187228

Country of ref document: AT

Date of ref document: 19991215

Kind code of ref document: T

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: PATENTANWALTSBUERO JEAN HUNZIKER

Ref country code: CH

Ref legal event code: EP

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19991202

REF Corresponds to:

Ref document number: 59507312

Country of ref document: DE

Date of ref document: 20000105

ITF It: translation for a ep patent filed

Owner name: SOCIETA' ITALIANA BREVETTI S.P.A.

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

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000301

ET Fr: translation filed
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20000724

Year of fee payment: 6

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

Ref country code: LU

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

Effective date: 20000801

Ref country code: AT

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

Effective date: 20000801

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

Ref country code: BE

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

Effective date: 20000831

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
BERE Be: lapsed

Owner name: HEILMEIER & WEINLEIN FABRIK FUR OEL-HYDRAULIK G.M

Effective date: 20000831

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: 20010801

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

Ref country code: SE

Payment date: 20010822

Year of fee payment: 7

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

Effective date: 20010801

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: 20020802

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

Ref country code: FR

Payment date: 20020820

Year of fee payment: 8

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

Ref country code: CH

Payment date: 20020903

Year of fee payment: 8

EUG Se: european patent has lapsed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

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

Effective date: 20030831

Ref country code: CH

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

Effective date: 20030831

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: 20040430

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050801

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

Ref country code: DE

Payment date: 20100929

Year of fee payment: 16

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: 20130301

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59507312

Country of ref document: DE

Effective date: 20130301