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EP1832756B1 - Dual-effect hydraulic actuator handling system for gate moving - Google Patents

Dual-effect hydraulic actuator handling system for gate moving Download PDF

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Publication number
EP1832756B1
EP1832756B1 EP07004321A EP07004321A EP1832756B1 EP 1832756 B1 EP1832756 B1 EP 1832756B1 EP 07004321 A EP07004321 A EP 07004321A EP 07004321 A EP07004321 A EP 07004321A EP 1832756 B1 EP1832756 B1 EP 1832756B1
Authority
EP
European Patent Office
Prior art keywords
oil
actuator
tank
stem
valve
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.)
Active
Application number
EP07004321A
Other languages
German (de)
French (fr)
Other versions
EP1832756A3 (en
EP1832756A2 (en
Inventor
Luigi Pasquali
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.)
FAAC SpA
Original Assignee
FAAC SpA
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 FAAC SpA filed Critical FAAC SpA
Priority to PL07004321T priority Critical patent/PL1832756T3/en
Publication of EP1832756A2 publication Critical patent/EP1832756A2/en
Publication of EP1832756A3 publication Critical patent/EP1832756A3/en
Application granted granted Critical
Publication of EP1832756B1 publication Critical patent/EP1832756B1/en
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/06—Details
    • F15B7/10—Compensation of the liquid content in a system
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • This invention relates to a dual-effect hydraulic actuator handling system for moving gates.
  • the stemless chamber is emptied and the stem-traversed chamber is filled. This causes excessive oil (equal to the volume of the stem) which must be returned into the tank. This is possible only through a not completely closed by-pass valve. In the contrary case, overpressures are observed upon suction which tend to 'suffocate' the pump and slow down the actuator in an anomalous manner.
  • the setting of the by-pass valve must therefore allow for this fact and it is not possible for example to take advantage of the maximum thrust of the operator, which would be useful especially with very heavy gates.
  • the setting of the by-pass valve becomes very delicate and a slight unsetting thereof, always possible especially under onerous outside conditions (for example high thermal changes), compromises the regular operation of the operator, causing jerking and blocking of the movement under load.
  • US-A-4,343,153 discloses a trim and tilt system for outboard drives on small boats, wherein a circuit arrangement according to the preamble of claim 1 is provided.
  • the general purpose of this invention is to avoid the above disadvantages by making available a handling system with dual-effect piston which would allow in a simple, economical and reliable manner compensation of the oil excess. Another purpose is to realize this without interfering with the operation of the by-pass valve.
  • FIG 1 shows diagrammatically a handling system designated as a whole by reference number 10 realized in accordance with this invention and in particular for handling of gates and the like.
  • the system has a dual-effect hydraulic actuator 11, an oil tank 12, a powered pump 13 and hydraulic circuitry 14 for control of the actuator.
  • the hydraulic circuit includes and in good part is symmetrical with two supply branches of the two chambers 11a and 11b of the actuator to control, depending on the pump direction, the opening or closing movement of the actuator (that is, respectively the leftward or rightward movement of the actuator as shown in FIG 1 ).
  • the pump is connected on each side to a respective one-way suction valve 15, 16 which draws from the tank 12 and to a respective by-pass valve 17, 18 which replaces the oil in the tank when the oil pressure exceeds the valve setting pressure.
  • Each side of the pump is also connected through a respective cutoff valve 19, 20 to one of the two actuator chambers.
  • Each cutoff valve 19, 20 is realized with a one-way valve releasable in the opposite direction through a piloting inlet 21, 22 controlled by the inlet pressure to the other cutoff valve.
  • the circuit also calls for a manual release tap 23 which connects the two chambers of the actuator directly to the tank 12 to allow manual handling of the actuator if necessary.
  • the suction valve 15 connecting the chamber 11a of the actuator opposite the stem is a one-way valve releasable by means of a piloting inlet 24 connected to the hydraulic circuit branch supplying the opposite chamber 11b of the actuator containing the stem.
  • this piloting inlet 24 is connected between the pump and the cutoff valve 20.
  • the pump In the opening step (leftward movement of the actuator) the pump is driven to suck the fluid from the left chamber 11a and shift it into the right-hand chamber 11b, in which there is the actuator stem. There will therefore be and excess of oil to be dumped into the tank.
  • pressure higher than atmospheric is generated, pressure which can reach for example 40 bar.
  • this overpressure is brought back to the suction valve 15, which is set to be unblocked by said overpressure so as to allow the excess oil arriving from the chamber 11a of the hydraulic cylinder (along the left-hand branch of the circuit) to flow into the tank through the valve 15.
  • valve 15 behaves instead like a normal one-way suction valve since the pressure in the right-hand branch of the circuit is no longer sufficient to control release of the valve 14 appropriately set. Indeed, the right-hand branch of the circuit is now the one of return and no longer of delivery. In this step, the valve 15 only allows passage of the oil from the tank to the circuit to compensate for the volume of the stem.
  • the piloted suction valve 15 allows a more satisfactory operation of the actuator in allowing return of the excess oil to the tank independently of the adjustment of the by-passes, whose setting thus influences only the adjustment of the force of the actuator.
  • the by-pass valves are set for an opening pressure safely higher than the commanded opening overpressure of the suction valve 15.
  • FIG 2 shows practical realization of the valve 15.
  • 25 and 26 are indicated the two fluid inlet or outlet ducts.
  • the valve includes a one-way cutoff realized by a ball 27 which is pushed by a spring 28 to close the passage between the two ducts 25, 26.
  • the thrust of the spring is such as to allow opening of the passage when there is the normal flow from the tank (duct 25) to the suction pump (duct 26).
  • a small piston 31 which is movable toward the ball in the opening direction against the action of a second opposing spring 29 thanks to the pressure of the fluid arriving from the duct 24.
  • the piston has one end or front pin 30 designed for thrust in opening of the ball 27.
  • a plug 32 closes the seat of the valve while packing the various parts.
  • the spring 29 is set to allow movement of the piston until opening of the ball valve when the pressure in the control duct 24 reaches overpressure due to unbalance of the transferred oil volumes as mentioned above.
  • the piloting system is completely deactivated since in the duct 24 there is not sufficient pressure to move the piston 31 and move the ball 27 in opening.
  • the valve works this way as a normal one-way valve allowing only passage of the oil from the tank to the circuit to compensate for the stem volume.
  • valve described can be easily integrated in a monobloc valve unit containing all the hydraulic circuitry of the handling system so as to have a strong and not cumbersome system. Using molding plastic for the valve of FIG 2 (except possible the small piston) this is a very economical device.
  • the device offers a series of considerable advantages compared with a complexity moderately higher than a normal suction valve. First of all it allows high quickening of the opening step (that is, of return of the stem) which now uses approximately the same time as the closing step.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Jib Cranes (AREA)

Abstract

A system for handling gates and the like including a dual-effect hydraulic actuator (11) with a stem traversing one (11b) of its chambers and a supply circuit (14) controlled with oil which alternately moves the oil between the actuator chambers (11a, 11b) for an 'opening' or 'closing' movement. The circuit includes a pump (13) for transfer of the oil between the chambers through piloted locking one-way valves (19, 20), an oil tank (12) and two one-way suction valves (15, 16) each connected between the tank (12) and one of the two sides of the pump (13) for allowing suction from the tank of the lacking oil. The suction valve (15) connected from the side of the pump opposite the actuator chamber (11a) not traversed by the stem is a one-way valve controlled in such a manner as to open thanks to an overpressure on the hydraulic circuit branch which is for supply of the actuator chamber (11b) traversed by the stem. In this manner the oil in excess during movement of the actuator which is caused by transfer of the oil from the stemless chamber (11a) to the chamber (11b) with stem is dumped into the tank (12).

Description

  • This invention relates to a dual-effect hydraulic actuator handling system for moving gates.
  • In hydraulic handling devices for gates a defect produced by the use of double-effect hydraulic actuators is noted. They have a difference of volume occupied by the fluid in the two hydraulic cylinder chambers because of the volume part occupied by the piston stem.
  • During the 'opening' handling, the stemless chamber is emptied and the stem-traversed chamber is filled. This causes excessive oil (equal to the volume of the stem) which must be returned into the tank. This is possible only through a not completely closed by-pass valve. In the contrary case, overpressures are observed upon suction which tend to 'suffocate' the pump and slow down the actuator in an anomalous manner. The setting of the by-pass valve must therefore allow for this fact and it is not possible for example to take advantage of the maximum thrust of the operator, which would be useful especially with very heavy gates. In addition, the setting of the by-pass valve becomes very delicate and a slight unsetting thereof, always possible especially under onerous outside conditions (for example high thermal changes), compromises the regular operation of the operator, causing jerking and blocking of the movement under load.
  • US-A-4,343,153 discloses a trim and tilt system for outboard drives on small boats, wherein a circuit arrangement according to the preamble of claim 1 is provided.
  • The general purpose of this invention is to avoid the above disadvantages by making available a handling system with dual-effect piston which would allow in a simple, economical and reliable manner compensation of the oil excess. Another purpose is to realize this without interfering with the operation of the by-pass valve.
  • In view of this purpose it was sought to provide in accordance with the present invention a system for handling gates and the like as claimed in claim 1.
  • To clarify the explanation of the innovative principles of the present invention and its advantages compared with the prior art there is described below with the aid of the annexed drawings a possible embodiment thereof by way of non-limiting example applying said principles. In the drawings:
    • FIG 1 shows a hydraulic diagram of the handling system in accordance with this invention, and
    • FIG 2 shows a view of a piloted valve unit which realizes part of the system of FIG 1.
  • With reference to the figures, FIG 1 shows diagrammatically a handling system designated as a whole by reference number 10 realized in accordance with this invention and in particular for handling of gates and the like. The system has a dual-effect hydraulic actuator 11, an oil tank 12, a powered pump 13 and hydraulic circuitry 14 for control of the actuator.
  • The hydraulic circuit includes and in good part is symmetrical with two supply branches of the two chambers 11a and 11b of the actuator to control, depending on the pump direction, the opening or closing movement of the actuator (that is, respectively the leftward or rightward movement of the actuator as shown in FIG 1). The pump is connected on each side to a respective one- way suction valve 15, 16 which draws from the tank 12 and to a respective by- pass valve 17, 18 which replaces the oil in the tank when the oil pressure exceeds the valve setting pressure. Each side of the pump is also connected through a respective cutoff valve 19, 20 to one of the two actuator chambers. Each cutoff valve 19, 20 is realized with a one-way valve releasable in the opposite direction through a piloting inlet 21, 22 controlled by the inlet pressure to the other cutoff valve.
  • Advantageously the circuit also calls for a manual release tap 23 which connects the two chambers of the actuator directly to the tank 12 to allow manual handling of the actuator if necessary.
  • In accordance with the principles of this invention the suction valve 15 connecting the chamber 11a of the actuator opposite the stem is a one-way valve releasable by means of a piloting inlet 24 connected to the hydraulic circuit branch supplying the opposite chamber 11b of the actuator containing the stem. In particular this piloting inlet 24 is connected between the pump and the cutoff valve 20.
  • Operation of the circuit is as follows.
  • In the opening step (leftward movement of the actuator) the pump is driven to suck the fluid from the left chamber 11a and shift it into the right-hand chamber 11b, in which there is the actuator stem. There will therefore be and excess of oil to be dumped into the tank. Along the delivery duct toward the chamber 11b, pressure higher than atmospheric is generated, pressure which can reach for example 40 bar. Through the piloting duct 24 this overpressure is brought back to the suction valve 15, which is set to be unblocked by said overpressure so as to allow the excess oil arriving from the chamber 11a of the hydraulic cylinder (along the left-hand branch of the circuit) to flow into the tank through the valve 15.
  • In the closing step (rightward movement of the actuator) the valve 15 behaves instead like a normal one-way suction valve since the pressure in the right-hand branch of the circuit is no longer sufficient to control release of the valve 14 appropriately set. Indeed, the right-hand branch of the circuit is now the one of return and no longer of delivery. In this step, the valve 15 only allows passage of the oil from the tank to the circuit to compensate for the volume of the stem.
  • It is thus clear how the piloted suction valve 15 allows a more satisfactory operation of the actuator in allowing return of the excess oil to the tank independently of the adjustment of the by-passes, whose setting thus influences only the adjustment of the force of the actuator. In particular, the by-pass valves are set for an opening pressure safely higher than the commanded opening overpressure of the suction valve 15.
  • FIG 2 shows practical realization of the valve 15. In the figure with 25 and 26 are indicated the two fluid inlet or outlet ducts. The valve includes a one-way cutoff realized by a ball 27 which is pushed by a spring 28 to close the passage between the two ducts 25, 26. The thrust of the spring is such as to allow opening of the passage when there is the normal flow from the tank (duct 25) to the suction pump (duct 26).
  • On the same axis as the ball cutoff there is a small piston 31 which is movable toward the ball in the opening direction against the action of a second opposing spring 29 thanks to the pressure of the fluid arriving from the duct 24. The piston has one end or front pin 30 designed for thrust in opening of the ball 27. A plug 32 closes the seat of the valve while packing the various parts.
  • The spring 29 is set to allow movement of the piston until opening of the ball valve when the pressure in the control duct 24 reaches overpressure due to unbalance of the transferred oil volumes as mentioned above.
  • This way, when the handling system is set for opening, the overpressure carried into the valve from the duct 24 moves the piston 31 while compressing the spring 29 so that the front pin 30 moves the ball and the excess oil arriving from the hydraulic cylinder can traverse the valve and dump into the tank.
  • On the other hand, when the handling system is set for closing, the piloting system is completely deactivated since in the duct 24 there is not sufficient pressure to move the piston 31 and move the ball 27 in opening. The valve works this way as a normal one-way valve allowing only passage of the oil from the tank to the circuit to compensate for the stem volume.
  • The valve described can be easily integrated in a monobloc valve unit containing all the hydraulic circuitry of the handling system so as to have a strong and not cumbersome system. Using molding plastic for the valve of FIG 2 (except possible the small piston) this is a very economical device.
  • It is now clear that the preset purposes have been achieved. The device offers a series of considerable advantages compared with a complexity moderately higher than a normal suction valve. First of all it allows high quickening of the opening step (that is, of return of the stem) which now uses approximately the same time as the closing step.
  • In addition, it enables working with completely closed bypasses while making use of the maximum thrust of the operator to the entire advantage of movement of very heavy gates. The more linear operation of the operator in the opening step is also ensured. The simplicity of operation makes it a strong, reliable device.
  • Naturally the above description of an embodiment applying the innovative principles of the present invention is given by way of non-limiting example of said principles within the scope of the exclusive right claimed here.

Claims (4)

  1. System for handling gates and the like including a dual-effect hydraulic actuator (11) with a stem traversing one (11b) of its chambers and a circuit (14) for controlled oil supply, which alternately moves the oil between the actuator chambers (11a, 11b) for an 'opening' or 'closing' movement, with the circuit including a pump (13) for transfer of the oil between the chambers through piloted-cutoff one-way valves (19, 20), an oil tank (12) and two one-way suction valves (15, 16) each connected between the tank (12) and one of the two sides of the pump (13) to allow suction of lacking oil from the tank, the suction valve (15) connected on the side of the pump corresponding to the actuator chamber (11a) not traversed by the stem being a controlled one-way valve with control inlet (24) connected in such a way as to be opened by an overpressure in the hydraulic circuit branch which is for supply of the actuator chamber (11b) traversed by the stem so as to allow, through said controlled one-way valve (15), dumping of the oil in excess into the tank (12) during a movement of the actuator which is caused by transfer of the oil from the stemless chamber (11a) to the chamber (11b) containing the stem, characterized in that the controlled one-way valve (15) includes a cut-off formed by a closing ball (27) thrust to close by a spring (28) and a control piston (31) moved by a fluid pressure at the control inlet (24) to run axially, against the action of an opposing spring (29), to push the closing ball (27) toward the cut-off opened position.
  2. System in accordance with claim 1 characterized in that said controlled suction valve (15) has a control inlet (24) connected between the pump (13) and the cutoff valve (20) connected to the chamber (11b) containing the stem.
  3. System in accordance with claim 1 characterized in that between each side of the pump (13) and the tank (12) is connected a respective bypass valve (17, 18) for dumping oil into the tank, which is set for an opening pressure higher than the controlled-opening overpressure of the controlled one-way valve (15).
  4. System in accordance with claim 1 characterized in that between the two chambers (11a, 11b) of the actuator and the tank (12) there is a dumping tap (23) to allow manual handling of the actuator.
EP07004321A 2006-03-10 2007-03-02 Dual-effect hydraulic actuator handling system for gate moving Active EP1832756B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07004321T PL1832756T3 (en) 2006-03-10 2007-03-02 Dual-effect hydraulic actuator handling system for gate moving

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT000426A ITMI20060426A1 (en) 2006-03-10 2006-03-10 HANDLING SYSTEM WITH HYDRAULIC DOUBLE ACTING ACTUATOR FOR GATE HANDLING

Publications (3)

Publication Number Publication Date
EP1832756A2 EP1832756A2 (en) 2007-09-12
EP1832756A3 EP1832756A3 (en) 2009-12-30
EP1832756B1 true EP1832756B1 (en) 2011-06-01

Family

ID=38093591

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07004321A Active EP1832756B1 (en) 2006-03-10 2007-03-02 Dual-effect hydraulic actuator handling system for gate moving

Country Status (9)

Country Link
US (1) US20070209502A1 (en)
EP (1) EP1832756B1 (en)
CN (1) CN101033671B (en)
AT (1) ATE511608T1 (en)
DK (1) DK1832756T3 (en)
ES (1) ES2367373T3 (en)
IT (1) ITMI20060426A1 (en)
PL (1) PL1832756T3 (en)
PT (1) PT1832756E (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITVI20080233A1 (en) * 2008-10-08 2010-04-09 Bft S P A HYDRAULIC DRIVE SYSTEM FOR HANDLING MOTORIZED AND SIMILAR GATES
DE102011005337A1 (en) * 2011-03-10 2012-09-13 Zf Friedrichshafen Ag Drive arrangement for carrying out working movements in working machines
JP6093535B2 (en) * 2012-10-10 2017-03-08 Ｋｙｂ株式会社 Cylinder drive
DE102014219244A1 (en) * 2014-09-24 2016-03-24 Robert Bosch Gmbh Hydraulic circuit for supplying a consumer with differential character
DE102016215311A1 (en) 2016-08-17 2018-02-22 Voith Patent Gmbh Hydraulic drive

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
US3747351A (en) * 1971-10-22 1973-07-24 Bertea Corp Hydraulic system
US4343153A (en) * 1980-03-21 1982-08-10 Eltra Corporation Anti-supercharge pressure valve
US4410056A (en) * 1981-05-27 1983-10-18 Paccar Inc. Hydraulic cab tilting system having full locking with controlled free-fall
FR2755481B1 (en) * 1996-11-07 1998-12-24 Lohr Ind DEVICE FOR HOLDING IN POSITION AND UNDER LOAD OF A HYDRAULIC CYLINDER
EP0893605B1 (en) * 1997-07-23 2002-10-09 Hoerbiger Hydraulik GmbH Hydraulic drive system
DE10261225B4 (en) * 2002-12-20 2006-11-16 Dorma Gmbh + Co. Kg Electrohydraulic servo door drive for driving a door, a window or the like
SE532772C2 (en) * 2008-08-14 2010-04-06 Haldex Traction Ab Hydraulic actuator controlling one or more slip couplings of a distribution system
KR20110076073A (en) * 2009-12-29 2011-07-06 볼보 컨스트럭션 이큅먼트 에이비 Negative Control Hydraulic System

Also Published As

Publication number Publication date
ES2367373T3 (en) 2011-11-02
US20070209502A1 (en) 2007-09-13
ITMI20060426A1 (en) 2007-09-11
EP1832756A3 (en) 2009-12-30
DK1832756T3 (en) 2011-09-19
EP1832756A2 (en) 2007-09-12
CN101033671A (en) 2007-09-12
PT1832756E (en) 2011-09-01
PL1832756T3 (en) 2011-11-30
CN101033671B (en) 2012-06-27
ATE511608T1 (en) 2011-06-15

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