EP1915538B1 - Circuit for controlling a double-action hydraulic drive cylinder - Google Patents

Circuit for controlling a double-action hydraulic drive cylinder Download PDF

Info

Publication number
EP1915538B1
EP1915538B1 EP20060701053 EP06701053A EP1915538B1 EP 1915538 B1 EP1915538 B1 EP 1915538B1 EP 20060701053 EP20060701053 EP 20060701053 EP 06701053 A EP06701053 A EP 06701053A EP 1915538 B1 EP1915538 B1 EP 1915538B1
Authority
EP
European Patent Office
Prior art keywords
valve
control valve
directional control
drive cylinder
hydraulic oil
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 - Fee Related
Application number
EP20060701053
Other languages
German (de)
French (fr)
Other versions
EP1915538A1 (en
Inventor
Ivan Hristov
Josef ZÜRCHER
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.)
Bucher Hydraulics AG
Original Assignee
Bucher Hydraulics AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to CH13662005 priority Critical
Application filed by Bucher Hydraulics AG filed Critical Bucher Hydraulics AG
Priority to PCT/CH2006/000057 priority patent/WO2007019712A1/en
Publication of EP1915538A1 publication Critical patent/EP1915538A1/en
Application granted granted Critical
Publication of EP1915538B1 publication Critical patent/EP1915538B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003Systems with load-holding valves
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B66HOISTING; LIFTING; HAULING
    • B66FHOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075Constructional features or details
    • B66F9/20Means for actuating or controlling masts, platforms, or forks
    • B66F9/22Hydraulic devices or systems
    • EFIXED CONSTRUCTIONS
    • E02HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02FDREDGING; SOIL-SHIFTING
    • E02F9/00Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20Drives; Control devices
    • E02F9/22Hydraulic or pneumatic drives
    • E02F9/2203Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024Systems 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/021Valves for interconnecting the fluid chambers of an actuator
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30505Non-return valves, i.e. check valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30505Non-return valves, i.e. check valves
    • F15B2211/3051Cross-check valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30505Non-return valves, i.e. check valves
    • F15B2211/30515Load holding valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30525Directional control valves, e.g. 4/3-directional control valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/3056Assemblies of multiple valves
    • F15B2211/30565Assemblies 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
    • F15B2211/3058Assemblies 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/31Directional control characterised by the positions of the valve element
    • F15B2211/3122Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127Floating position connecting the working ports and the return line
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/31Directional control characterised by the positions of the valve element
    • F15B2211/3144Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/315Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/315Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31588Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and multiple output members
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/32Directional control characterised by the type of actuation
    • F15B2211/329Directional control characterised by the type of actuation actuated by fluid pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/35Directional control combined with flow control
    • F15B2211/351Flow control by regulating means in feed line, i.e. meter-in control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/35Directional control combined with flow control
    • F15B2211/353Flow control by regulating means in return line, i.e. meter-out control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/505Pressure control characterised by the type of pressure control means
    • F15B2211/50509Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/55Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/80Other types of control related to particular problems or conditions
    • F15B2211/88Control measures for saving energy

Abstract

The invention relates to a circuit for controlling a double-action hydraulic drive cylinder (1), which is controlled by a directional control valve (5) equipped with working connections (A, B). Hydraulic fluid can be fed to a piston chamber (11), whereas hydraulic oil simultaneously discharges from a rod chamber (12), and hydraulic fluid can be fed to a rod chamber (12), whereas hydraulic oil simultaneously discharges from a piston chamber (11). The invention is characterized in that: the piston chamber (11) is connected to the rod chamber (12) via a parallel connection consisting of a pressure limiting valve (21) and of a controllable load maintaining valve (26) and via an automatic regeneration check valve (22) arranged parallel thereto; a first pretensioning valve (24) and an automatic by-pass check valve (28) situated antiparallel thereto are arranged between the connection point between the pressure limiting valve (21), load maintaining valve (26), the regeneration control valve (22) and the working connection (A) of the directional control valve (5); and another pretensioning valve (30; 45) is arranged inside a line between the rod chamber (12) and a tank in a series connection with the directional control valve (5). The invention enables a regeneration from the piston chamber (11) to the rod chamber (12) whereby reducing the power requirement for operating the pump.

Description

  • The invention relates to a circuit for controlling a double-acting hydraulic drive cylinder according to the preamble of claim 1.
  • In devices for lifting and lowering of loads often double-acting drive cylinders are used. In one direction of movement hydraulic oil is fed into the piston chamber of the drive cylinder, while hydraulic oil must be removed from the rod space of the drive cylinder. Because the cross-sections of piston and rod space are different sizes, the amounts of injected and discharged hydraulic oil are different sizes. In the aforementioned first direction of movement, more hydraulic oil must be supplied to the piston chamber than flows away on the rod chamber. In the other direction of movement this is the other way around.
  • If the inflow and outflow of hydraulic oil are only controlled by a directional control valve, then, for example, the entire hydraulic oil to be delivered into the piston chamber has to be pumped by a pump. The hydraulic oil flowing out of the rod space flows via the directional control valve to the tank.
  • From the publication " The hydraulic trainer, Volume 2 - Proportional and Servovalve technique "(Mannesmann Rexroth GmbH, 1st edition, ISBN 3-8023-0898-0 ), a differential circuit is known in which a spring-loaded check valve is arranged parallel to the directional control valve. Hydraulic oil is delivered from the pump via the directional control valve to the piston chamber, so that hydraulic oil flows from the rod space via the check valve to the pump port of the directional control valve because the return flow into the tank is shut off by the directional control valve. The pump must therefore only promote the difference in hydraulic oil.
  • In working machines where such double-acting drive cylinders are used, the piping between the directional control valve and the double-acting drive cylinder is often very long, for example 8 m or more. But a long hydraulic oil line is a hydraulic resistance, which means energy losses and leads to heating of the hydraulic oil.
  • Out EP 0 831 181 B1 and DE 69717 040 T2 a circuit is known in which a circuit with a check valve between the supply lines to the rod space and the piston chamber is present. Thus, hydraulic oil can flow from the rod space to the piston chamber without having to take the detour via the directional control valve. Thus, the problem of energy losses and oil heating is mitigated. The so-called regeneration is therefore effective when extending the rod from the drive cylinder, which may mean, for example, the lifting of a load. When retracting, so for example when lowering the load, no regeneration takes place. The entire amount of hydraulic oil exiting from the piston space of the hydraulic drive cylinder must be discharged to the tank via the directional control valve, while the amount of hydraulic oil to be delivered into the rod space must flow from the pump via the directional control valve. When lowering the load, the pump must therefore perform and the total amount of hydraulic oil must flow through the long lines.
  • Out DE-A1-199 32 948 For example, a controlled float circuit for an actuator is known. In this case, a regeneration of the piston chamber to the rod space of a hydraulic drive cylinder is possible, but requires additional control means, namely a pilot-operated check valve, which is controlled by an electrically controlled valve. The electrically controlled valve in turn is driven by a contact of a switch assembly. In one embodiment, a second pilot-operated check valve is also required, which is controlled by a proportional pressure control part. In the second embodiment variant shown, an additional outlet valve is required, which requires actuation by a second proportional pressure control part.
  • A regeneration of the piston chamber to the rod space is therefore possible here in principle, but requires control interventions and is bound to the presence of pilot-operated check valves and their Ansteuerorgane. Hydraulically controlled valves and their actuators, which also act hydraulically, lead to pressure losses and thus require a certain power requirement.
  • The invention has for its object to simplify the hydraulic circuit and at the same time further reduce the power requirement by hydraulic flow resistance and thus the Ölerwärmung be minimized.
  • The above object is achieved by the features of claim 1. Advantageous developments emerge from the dependent claims.
  • Embodiments of the invention will be explained in more detail with reference to the drawing.
  • Show it:
  • Fig. 1
    a diagram of a circuit for controlling a double-acting hydraulic drive cylinder,
    Fig. 2
    the same scheme in a different operating state,
    Fig. 3
    a diagram with a different position of the drive cylinder,
    Fig. 4
    a scheme for the operating mode extension,
    Fig. 5
    a circuit variant and
    Fig. 6
    a scheme for operating two parallel operating drive cylinder.
  • In the Fig. 1 a double-acting hydraulic drive cylinder 1 is shown, in which a load 4 is movable by a piston 2 and a piston rod 3 connected thereto. Can be controlled, the drive cylinder 1 by a directional control valve 5, which is controllable in a known manner by 6 drives. The directional control valve 5 has a pump connection P, a tank connection T, a first working connection A and a second working connection B in a known manner.
  • A first drive 6.1 brings in a known manner the directional control valve 5 in that position in which the pump port P to the working port B and the tank port T are connected to the working port A. A second drive 6.2 brings the directional control valve 5 in the position in which the pump port P to the working port A and the tank port T to the working port B are connected. If none of the drives 6 is activated, the directional control valve 5 assumes the drawn position, which represents the neutral position of the directional control valve 5.
  • The drive cylinder 1 has a piston chamber 11 and a rod space 12. By supplying hydraulic oil into the piston chamber 11 with simultaneous removal of hydraulic oil from the rod space 12, the function "lifting" can be achieved for the load 4 by feeding of hydraulic oil in the rod chamber 12 with simultaneous removal of hydraulic oil from the piston chamber 11, the function "lowering". As mentioned above, the inflowing and outflowing quantities of hydraulic oil are not the same because of the different cross sections of piston chamber 11 and rod space 12.
  • According to the invention, a piston chamber connection A 11 on the piston chamber 11 via a pressure relief valve 21 and an automatic regeneration check valve 22, which requires no control, connected to a rod space connection A 12 on the rod space 12. Through this connection, a flow of the hydraulic oil from the piston chamber port A 11 to the rod space port A 12 is possible, which will be described later.
  • The pressure limiting valve 21 causes the limitation of the pressure in the piston chamber 11. When retracting the piston 2 with the rod 3 in the drive cylinder 1, this pressure relief valve 21 opens when the pressure in the piston chamber 11 is higher than the pressure set at the pressure relief valve 21, so that hydraulic oil the piston chamber 11 can flow to reduce the pressure, so limit. The hydraulic oil flows in different ways depending on the operating conditions. With the pressure limiting valve 21, the drive cylinder 1 is secured against external loads.
  • The regeneration check valve 22 opens automatically when at its the piston chamber port A 11 side facing a higher pressure prevails than at its the rod space connection A 12 side facing. For a regeneration of the piston chamber 11 to the rod space 12 is possible without additional control means must be operated.
  • In the Fig. 1 is - as already mentioned - the neutral position of the directional control valve 5 shown. The two drives 6 are not activated. Thus, the two working ports A, B are connected to the tank port T. The pump connection P is shut off.
  • Between the pressure relief valve 21 and the automatic regeneration check valve 22 branches the connecting line, namely on the one hand via a first biasing valve 24 to the working port A of the directional control valve 5, and on the other hand according to the invention via a load-holding valve 26 to the piston chamber port A 11th The Load holding valve 26 can be controlled by a control pressure p X , which is present at a control pressure connection X.
  • Parallel to the first preload valve 24 and load-holding valve 26, a first automatic bypass check valve 28 is arranged. Thereby, the blocking effect of the first biasing valve 24 and load-holding valve 26 can be bypassed in one direction, so that hydraulic oil from the working port A of the directional control valve 5 to the piston chamber port A 11 can flow when the directional control valve 5 is driven accordingly. A control intervention is not required.
  • Between the working port B of the directional control valve and the rod space connection A 12 , two check valves are connected in anti-parallel, namely a second biasing valve 30 and a second automatic bypass check valve 32. The second biasing valve 30 is thus between the rod chamber 12 and the tank in series with the directional control valve fifth connected.
  • The inventive serial arrangement of load-holding valve 26 and regeneration check valve 22 between the piston chamber port A 11 and the rod space connection A 12 , it is now possible in befindlichem in neutral position directional control valve 5, in which the pump port P is locked and the two working ports A, B are connected to the tank connection T to achieve the retraction of the rod in the drive cylinder, characterized in that the load-holding valve 26 is driven. Under the effect of the load 4, a higher pressure prevails in the piston chamber 11 than in the rod chamber 12. If the load-holding valve 26 is activated with a control pressure p X , this opens and the hydraulic oil can flow into the rod chamber 12 via the regeneration check valve 22 without it requires a further control intervention.
  • Because now but in the movement of the piston 2 due to the different cross-sections of the piston chamber 11 and rod space 12 more hydraulic oil flows from the piston chamber 11 than the rod chamber 12 is able to accommodate, the difference in quantity over the first biasing valve 24 and / or a second biasing valve 30th and thus flow via the working ports A and B to the tank port T and thus into the tank. The retraction, in this case identical to the lowering of the load 4, thus takes place without that Pump power must be applied-must. The bias valves 24, 30 cause that only the difference amount is discharged. They are therefore essential to the invention.
  • In the Fig. 2 is the same scheme as in the Fig. 1 shown, but now is the directional control valve 5 in another position, in which the pump port P to the working port B and the tank port T are connected to the working port A. This other position is achieved in that the first drive 6.1 is acted upon by the already mentioned control pressure p X. At the same time hydraulic oil flows from the piston chamber 11 because of the here also controlled load-holding valve 26 through this and the regeneration check valve 22 in the rod space 12. Because of Different cross sections of the piston chamber 11 and rod space 12, the difference in quantity over the first biasing valve 24 and thus via the working port A of the directional control valve 5 to the tank port T and thus flow into the tank here.
  • The in the Fig. 2 shown operating mode compared to the operation of Fig. 1 a faster movement. However, this rapid traverse requires little energy for the pump, because here, too, that part of the hydraulic oil flowing from the piston chamber 11 directly via the load-holding valve 26 and the regeneration check valve 22 into the rod chamber 12, does not have to be funded by the pump.
  • In the Fig. 1 and 2 are shown states in which the load 4 acts above the drive cylinder 1, because the drive cylinder 1 is inclined so that the load-side end of the piston rod 3 is higher than the piston-side end of the piston rod 3. In such an arrangement, the extension means the lifting of Load 4 while retracting means lowering the load. There are applications in which the hydraulic drive cylinder 1 always has this position.
  • On the other hand, there are also applications in which the hydraulic drive cylinder 1 is inclined differently. This is in the Fig. 3 shown. Here, the load 4 engages below the drive cylinder 1, because the drive cylinder 1 is inclined so that the load-side end of the piston rod 3 is lower than the piston-side end of the piston rod 3. Consequently, here now retraction means the lifting of the load 4, while the Extending the lowering of the load 4 means.
  • The retraction is not only by driving the load-holding valve 26 according to here Fig. 1 possible because the load 4 does not press on the piston 2, but pulls on this. Accordingly, it is therefore necessary for retraction, which means in this case the lifting of the load 4, the necessary energy to lift the load 4 by the operation of the pump. However, the circuit according to the invention also controls this operating state without problems. Additional control means and their operation is not required.
  • In this case, the control of load-holding valve 26 and directional control valve 5 is the same as in the Fig. 2 , With the control pressure p X both the load-holding valve 26 and the first drive 6.1 of the directional control valve 5 are acted upon. Therefore, the directional control valve 5 is in the position shown, in which the pump port P to the working port B and the tank port T are connected to the working port A. Thus, the pump delivers hydraulic oil from the pump port P via the working port B through the opening second bypass check valve 32 through the rod space connection A 12 in the rod space 12. This is displaced from the piston chamber 11 hydraulic oil, which via the piston chamber port A 11 , through the load-holding valve 26, which opens because of the activation, the automatically opening first pretensioning valve 24 and the connection existing in the directional control valve 5 from the working connection A to the tank connection T to the tank. The pressure in the rod chamber 12 is greater than the pressure in the piston chamber 11 and this has the consequence that the regeneration check valve 22 is closed. In this operating state so no regeneration takes place.
  • In the Fig. 4 the operating mode extension is shown. By controlling the second drive 6.2, the directional control valve 5 assumes the position shown in the directional valve 5, the pump port P is connected to the working port A and the working port B to the tank port T. The pumped by the pump hydraulic oil reads from the pump port P to the working port A and the automatically opening first bypass check valve 28 in the piston chamber 11. At the same time displaced from the rod chamber 12 hydraulic oil, which flows via the self-opening second biasing valve 30 and existing in the directional control valve 5 connection from the working port B to the tank port T in the tank. The load-holding valve 26 is not activated and the regeneration check valve 22 is closed.
  • The extension is independent of the spatial position of the hydraulic drive cylinder 1. If the drive cylinder 1 in the position shown, the extension means lifting the load 4. Is the drive cylinder 1 in the in the Fig. 3 shown position, the extension means lowering the load. Of course, the power to be applied by the pump is different in both cases.
  • The purpose of the invention associated pressure relief valve 21 has the purpose to protect the drive cylinder 1 during retraction from excessive load. If the pressure in the piston chamber 11 is greater than the pressure set on the pressure limiting valve 21, the pressure limiting valve 21 opens and hydraulic oil flows via the regeneration check valve 22 to the rod chamber 12 and / or via the biasing valve 24 and the directional control valve 5 to the tank. Which way it takes depends on the respective operating conditions.
  • Advantageously, the pressure relief valve 21, the regeneration check valve 22, the first biasing valve 24, the load holding valve 26, the first bypass check valve 28, the second biasing valve 30 and the second bypass check valve 32 in a single valve block 40 and assembled directly to the drive cylinder 1 ,
  • In the Fig. 5 an advantageous embodiment of the invention is shown. In principle, the circuit is the same as the one after Fig. 1 However, here the parallel connection of the second biasing valve 30 and the second bypass check valve 32 is omitted. Thus, there is a direct connection between the working port B and the rod space 12. The required for the operation of the circuit bias of the rod chamber 12 is achieved by a in the tank line between the Tank terminal T and the tank arranged further biasing valve 45. So this takes over the function of the second biasing valve 30 after the Fig. 1 to 4 , The described operating behavior does not change as a result. Also, the biasing valve 45 is connected between the rod space 12 and the tank in series with the directional control valve 5.
  • In the Fig. 6 two parallel working Artriebszylinder 1 are shown. Both attack on the same load 4 '. This is applied when the load 4 'is very heavy. Each drive cylinder 1 is of a similar, that of Fig. 1 corresponding circuit activated. The same reference numbers here mean the same parts as in the Fig. 1 , The Both drive cylinder 1 are driven in parallel by a single directional control valve 5, so that they are completely similar to the working ports A and B of the directional control valve 5 connected. The two load-holding valve 26 are also driven in parallel by the control pressure p X.
  • For such a parallel operation of two drive cylinders 1, however, a compensation line 49 is additionally required, with which the piston chambers 11 of both drive cylinders 1 are connected. In this case, each of the drive cylinders 1 is assigned a compensation line nozzle 50 and a compensation line check valve 51, which are arranged parallel to one another in the compensation line 49. This ensures that the pressures in the two piston chambers 11 are equal. If the pressure in one of the piston chambers 11 is greater, then hydraulic oil can flow from this piston chamber 11 into the piston chamber 11 of the other drive cylinder 1, with the hydraulic oil first passing through the closest compensation nozzle 50 and then the compensation power check valve 51 assigned to the other drive cylinder 1 ,
  • The previously mentioned valve block 40 may also include the directional control valve 5, as well as the possibly existing additional biasing valve 45th
  • By the invention it is achieved that a regeneration from the piston chamber 11 to the rod space 12 can take place. Thus, when retracted no compressed hydraulic oil through the often long line between the drive cylinder 1 and directional control valve 5 is promoted. Energy is saved for operating the pump and the dynamic behavior of the drive cylinder 1 is improved.

Claims (5)

  1. Circuit for controlling a double-action hydraulic drive cylinder (1), which can be controlled by a directional control valve (5) equipped with working connections A, B,
    wherein hydraulic oil can be fed to a piston chamber (11) while simultaneously hydraulic oil discharges from a rod chamber (12) and hydraulic oil can be fed to the rod chamber (12) while simultaneously hydraulic oil discharges from the piston chamber (11),
    wherein the circuit comprises the directional control valve (5), a pressure limiting valve (21), a controllable load maintaining valve (26), a regeneration control valve (22), a first and second pre-tensioning valve (24 and 30) as well as a first automatic by-pass check valve (28),
    wherein the piston chamber (11) of the drive cylinder (1) can be connected to the rod chamber (12) of the drive cylinder (1) via a parallel connection of the pressure limiting valve (21) and of the controllable load maintaining valve (26) and the regeneration control valve (22), which is arranged at the rod chamber side in series thereto and locks in direction to the piston chamber,
    wherein at the connecting point between pressure limiting valve (21), load maintaining valve (26) and regeneration control valve (22) the first pre-tensioning valve (24) is connected, which locks in direction to the connecting point and the second connector of which is connected with the first working connection A of the directional control valve (5),
    wherein anti-parallel to the first pre-tensioning valve (24) and to the load maintaining valve (26) the first automatic by-pass check valve (28) is arranged which locks in direction to the first working connection A,
    wherein the second pre-tensioning valve (30) which locks in direction to the rod chamber can be connected to the rod chamber (12) of the drive cylinder (1) which on the other side can be connected to the second working connection B of the directional control valve (5), and
    wherein the directional control valve (5) features a neutral position in which the pump connection P is locked and the two working connections A, B are connected to the tank connection T.
  2. Circuit for controlling a double-action hydraulic drive cylinder (1), which can be controlled by a directional control valve (5) equipped with working connections A, B,
    wherein hydraulic oil can be fed to a piston chamber (11) while simultaneously hydraulic oil discharges from a rod chamber (12) and hydraulic oil can be fed to the rod chamber (12) while simultaneously hydraulic oil discharges from the piston chamber (11),
    wherein the circuit comprises the directional control valve (5), a pressure limiting valve (21), a controllable load maintaining valve (26), a regeneration control valve (22), a first and second pre-tensioning valve (24 and 30) as well as a first automatic by-pass check valve (28),
    wherein the piston chamber (11) of the drive cylinder (1) can be connected to the rod chamber (12) of the drive cylinder (1) via a parallel connection of the pressure limiting valve (21) and of the controllable load maintaining valve (26) and the regeneration control valve (22), which is arranged at the rod chamber side in series thereto and locks in direction to the piston chamber,
    wherein at the connecting point between pressure limiting valve (21), load maintaining valve (26) and regeneration control valve (22) the first pre-tensioning valve (24) is connected, which locks in direction to the connecting point and the second connector of which is connected with the first working connection A of the directional control valve (5),
    wherein anti-parallel to the first pre-tensioning valve (24) and to the load maintaining valve (26) the first automatic by-pass check valve (28) is arranged which locks in direction to the first working connection A,
    wherein the rod chamber (12) of the drive cylinder (1) can be connected to the second working connection B of the directional control valve (5) and
    wherein the second pre-tensioning valve (45) is arranged at the tank connection of the directional control valve (5) and
    wherein the directional control valve (5) features a neutral position in which the pump connection P is locked and the two working connections A, B are connected to the tank connection T.
  3. Circuit according to claim 1, characterized in that a second by-pass check valve (32) is connected anti-parallel to the second pre-tensioning valve (30).
  4. Circuit according to claim 3, characterized in that the pressure limiting valve (21), the regeneration control valve (22), the first pre-tensioning valve (24), the load maintaining valve (26), the first by-pass check valve (28), the second pre-tensioning valve (30) and the second by-pass check valve (32) are incorporated within one single valve block (40) and in that this valve block (40) can directly be attached to the drive cylinder (1).
  5. Circuit according to claim 4, characterized in that parallel to the one drive cylinder (1) and its control elements (21, 22, 24, 26, 28, 30, 32) a further drive cylinder (1) with the same control elements (21, 22, 24, 26, 28, 30, 32) is connected, wherein both drive cylinders (1) can be corporately controlled by means of only one directional control valve (5),
    and in that the piston chambers (11) of both drive cylinders (1) are connected by means of a balancing line (49) belonging to the circuit, wherein to each of the drive cylinders (1) a balancing line orifice (50) and a balancing line check valve (51) are assigned which are arranged parallel to each other in the balancing line (49).
EP20060701053 2005-08-19 2006-01-27 Circuit for controlling a double-action hydraulic drive cylinder Expired - Fee Related EP1915538B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CH13662005 2005-08-19
PCT/CH2006/000057 WO2007019712A1 (en) 2005-08-19 2006-01-27 Circuit for controlling a double-action hydraulic drive cylinder

Publications (2)

Publication Number Publication Date
EP1915538A1 EP1915538A1 (en) 2008-04-30
EP1915538B1 true EP1915538B1 (en) 2012-04-04

Family

ID=35198032

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060701053 Expired - Fee Related EP1915538B1 (en) 2005-08-19 2006-01-27 Circuit for controlling a double-action hydraulic drive cylinder

Country Status (7)

Country Link
US (1) US7752842B2 (en)
EP (1) EP1915538B1 (en)
JP (1) JP2009505013A (en)
KR (1) KR20080021779A (en)
CN (1) CN101253335B (en)
AT (1) AT552425T (en)
WO (1) WO2007019712A1 (en)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE531754C2 (en) * 2007-05-11 2009-07-28 Nordhydraulic Ab Hydraulic load control valve device
EP2189666B1 (en) * 2008-11-20 2011-07-27 Bosch Rexroth Oil Control S.p.A. A hydraulic device for controlling an actuator.
DE202009006299U1 (en) * 2009-04-29 2010-09-09 Liebherr-France Sas, Colmar Hydraulic system as well as mobile construction machine
JP2011214598A (en) * 2010-03-31 2011-10-27 Takara Belmont Co Ltd Hydraulic control circuit for double-acting cylinder
EP2466153B1 (en) * 2010-12-17 2013-08-14 HAWE Hydraulik SE Electrohydraulic control device
US9080310B2 (en) 2011-10-21 2015-07-14 Caterpillar Inc. Closed-loop hydraulic system having regeneration configuration
CN102383905B (en) * 2011-11-08 2012-12-26 上海三一重机有限公司 Intelligent control method for after-treatment regeneration of engine for engineering machinery
DE102012001562A1 (en) * 2012-01-27 2013-08-01 Robert Bosch Gmbh Valve arrangement for a mobile work machine
CN105705706B (en) * 2013-10-31 2017-10-10 沃尔沃建造设备有限公司 Flow control valve for the engineering equipment with float function
DE102014216682A1 (en) * 2014-08-21 2016-02-25 Jungheinrich Aktiengesellschaft Retrofitting of a safety valve in a commercial vehicle to meet safety requirements regarding the lowering operation of a lifting device and a corresponding commercial vehicle
CN105298951B (en) * 2015-12-02 2018-10-23 湖南星邦重工有限公司 A kind of aerial work platform and its changing-breadth system
US9800795B2 (en) 2015-12-21 2017-10-24 Intel Corporation Auto range control for active illumination depth camera
US9759340B2 (en) * 2015-12-21 2017-09-12 Fisher Controls International Llc Methods and appratus for independently controlling seating forces in rotary valves
ITUA20162376A1 (en) 2016-04-07 2017-10-07 Atlantic Fluid Tech S R L of an actuator control device
JP6673551B2 (en) * 2016-09-21 2020-03-25 Smc株式会社 Fluid pressure cylinder
CN108180177A (en) * 2017-12-26 2018-06-19 邵立坤 It is a kind of for the hydraulic valve of differential circuit and hydraulic differential circuit
CN110259743A (en) * 2019-06-24 2019-09-20 绍兴文理学院 A kind of hydraulic cylinder autonomous control system of rock triaxial creep testing machine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4135013C2 (en) * 1991-10-23 2000-07-27 Linde Ag Hydraulic drive system
US5331882A (en) * 1993-04-05 1994-07-26 Deere & Company Control valve system with float valve
US5415076A (en) * 1994-04-18 1995-05-16 Caterpillar Inc. Hydraulic system having a combined meter-out and regeneration valve assembly
JP3478931B2 (en) * 1996-09-20 2003-12-15 新キャタピラー三菱株式会社 Hydraulic circuit
JP3446023B2 (en) * 1997-03-24 2003-09-16 大淀小松株式会社 Hydraulic equipment
US6092454A (en) * 1998-07-23 2000-07-25 Caterpillar Inc. Controlled float circuit for an actuator
DE10006908A1 (en) * 2000-02-16 2001-08-23 Caterpillar Sarl Genf Geneva Hydraulic cylinder unit for raising and lowering front arm on root harvester has branch pipe leading back to oil tank which is fitted with shut-off valve and pressure-regulating valve

Also Published As

Publication number Publication date
KR20080021779A (en) 2008-03-07
CN101253335B (en) 2010-06-16
US7752842B2 (en) 2010-07-13
JP2009505013A (en) 2009-02-05
CN101253335A (en) 2008-08-27
EP1915538A1 (en) 2008-04-30
US20100083651A1 (en) 2010-04-08
AT552425T (en) 2012-04-15
WO2007019712A1 (en) 2007-02-22

Similar Documents

Publication Publication Date Title
ES2429842T3 (en) Hydraulic system for implements
US6854268B2 (en) Hydraulic control system with energy recovery
US7104181B2 (en) Hydraulic control circuit for a hydraulic lifting cylinder
US4833971A (en) Self-regulated hydraulic control system
JP5574375B2 (en) Energy regeneration control circuit and work machine
DE102004056418B4 (en) Hydraulic arrangement
JP4410512B2 (en) Hydraulic drive
JP5216085B2 (en) Method for supplying pressure medium to at least one hydraulic consumer and hydraulic control device
JP5758624B2 (en) Negative control hydraulic system
CN101253335B (en) Oil circuit for controlling a double-action hydraulic drive cylinder
US7614336B2 (en) Hydraulic system having augmented pressure compensation
US6715403B2 (en) Independent and regenerative mode fluid control system
JP4856131B2 (en) Hydraulic system of work machine
EP0468944B1 (en) An arrangement for controlling hydraulic motors
JP4520041B2 (en) Hydraulic circuit
KR100706594B1 (en) Hydraulic control
EP1252449B1 (en) Method and device for controlling a lift cylinder, especially of working machines
KR100228810B1 (en) Hydraulic apparatus for building machinery
US9376787B2 (en) Hydraulic valve device
US7484814B2 (en) Hydraulic system with engine anti-stall control
US9080310B2 (en) Closed-loop hydraulic system having regeneration configuration
US7243591B2 (en) Hydraulic valve arrangement
JP2005098455A (en) Hydraulic controller of industrial machinery
US20030150210A1 (en) Fluid pressure circuit
JP2008014468A (en) Hydraulic control system in working machine

Legal Events

Date Code Title Description
17P Request for examination filed

Effective date: 20071213

AK Designated contracting states:

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

17Q First examination report

Effective date: 20090212

DAX Request for extension of the european patent (to any country) deleted
REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

AK Designated contracting states:

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: CH

Ref legal event code: NV

Representative=s name: E. BLUM & CO. AG PATENT- UND MARKENANWAELTE VSP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 552425

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120415

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502006011238

Country of ref document: DE

Effective date: 20120531

REG Reference to a national code

Ref country code: NL

Ref legal event code: T3

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20120404

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: FI

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: 20120404

Ref country code: LT

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: 20120404

Ref country code: SI

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: 20120404

Ref country code: CY

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: 20120404

Ref country code: IS

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: 20120804

Ref country code: PL

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: 20120404

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: PT

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: 20120806

Ref country code: LV

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: 20120404

Ref country code: GR

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: 20120705

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: RO

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: 20120404

Ref country code: CZ

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: 20120404

Ref country code: SK

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: 20120404

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: 20120404

Ref country code: EE

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: 20120404

PGFP Postgrant: annual fees paid to national office

Ref country code: CH

Payment date: 20121212

Year of fee payment: 8

26N No opposition filed

Effective date: 20130107

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: ES

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: 20120715

PGFP Postgrant: annual fees paid to national office

Ref country code: GB

Payment date: 20130122

Year of fee payment: 8

Ref country code: SE

Payment date: 20130122

Year of fee payment: 8

Ref country code: DE

Payment date: 20130122

Year of fee payment: 8

Ref country code: FR

Payment date: 20130213

Year of fee payment: 8

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502006011238

Country of ref document: DE

Effective date: 20130107

PGFP Postgrant: annual fees paid to national office

Ref country code: NL

Payment date: 20130122

Year of fee payment: 8

BERE Be: lapsed

Owner name: BUCHER HYDRAULICS A.G.

Effective date: 20130131

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: BG

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: 20120704

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: MC

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

Effective date: 20130131

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: BE

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

Effective date: 20130131

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: IE

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

Effective date: 20130127

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 552425

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130127

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: AT

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

Effective date: 20130127

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502006011238

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: V1

Effective date: 20140801

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

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

Effective date: 20140127

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502006011238

Country of ref document: DE

Effective date: 20140801

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: CH

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

Effective date: 20140131

Ref country code: NL

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

Effective date: 20140801

Ref country code: LI

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

Effective date: 20140131

Ref country code: DE

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

Effective date: 20140801

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140930

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: FR

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

Effective date: 20140131

Ref country code: SE

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

Effective date: 20140128

Ref country code: GB

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

Effective date: 20140127

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: TR

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: 20120404

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: HU

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

Effective date: 20060127

Ref country code: LU

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

Effective date: 20130127

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: IT

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

Effective date: 20140127