EP3385215B9 - Entraînement de levage hydraulique d'une machine de travail mobile, en particulier d'un chariot de manutention - Google Patents

Entraînement de levage hydraulique d'une machine de travail mobile, en particulier d'un chariot de manutention Download PDF

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Publication number
EP3385215B9
EP3385215B9 EP18164844.5A EP18164844A EP3385215B9 EP 3385215 B9 EP3385215 B9 EP 3385215B9 EP 18164844 A EP18164844 A EP 18164844A EP 3385215 B9 EP3385215 B9 EP 3385215B9
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EP
European Patent Office
Prior art keywords
load
discharge pressure
pressure
lifting
control
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EP18164844.5A
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German (de)
English (en)
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EP3385215A1 (fr
EP3385215B1 (fr
Inventor
Sebastian Schauer
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STILL GmbH
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STILL GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, 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
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices 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
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems

Definitions

  • the invention relates to a hydraulic lifting drive of a mobile machine, in particular a truck, for lifting and lowering a lifting carriage, wherein the lifting drive has a lifting cylinder and a control valve for controlling the lowering operation of the lifting drive, wherein in a guided from the lifting cylinder to a container sink branch a discharge pressure balance is arranged, which is acted upon by a spring device in the direction of a flow position and by the pressure applied in a signal path of the discharge pressure compensator upstream of the control valve pressure in the direction of a blocking position.
  • Such hydraulic lifting drives are used in mobile machines, such as industrial trucks, for lifting and lowering a lifting carriage, to which a load-handling device is attached, for example a load fork, with a load located thereon.
  • a load-handling device for example a load fork, with a load located thereon.
  • a lowering branch guided by a lifting cylinder to a container is provided, in which a control valve controlling the lowering operation of the lifting carriage is arranged.
  • the maximum lowering speed of the lifting carriage with nominal load is limited by standards to the value of 0.6 m / s.
  • a lowering brake valve outside of a control way valve block in which the control valve for controlling the lowering operation of the lifting drive is arranged.
  • Such a lowering brake valve has a mechanical limitation of the outflow volume flow in order to maintain the maximum lowering speed.
  • such arranged outside of the control-way valve block lowering brake valve leads to an increased number of components of the linear actuator, an increased space requirement and requires additional piping or tubing, which increases the assembly costs and the risk of leakage is increased.
  • At one outside the control way valve block arranged lowering brake valve is also to ensure that the spring preload, which limits the drain volume flow and thus the sink speed, is secured against loosening, thereby increasing the manufacturing cost and process reliability is critical.
  • Senkbremsventile have a high flow resistance.
  • control directional control valve block in which the control valve for controlling the lowering operation of the lifting drive, in the lowering branch a discharge pressure compensator.
  • the discharge pressure balance arranged in the lowering branch regulates the lowering speed of the lifting drive via the outflow volume flow.
  • the installation of the pressure compensator in the control directional control valve block results in no additional space for the pressure compensator and it eliminates an additional piping or tubing, which reduces the installation effort and there is no risk of additional leakage points.
  • the discharge pressure balance usually has a full load independence from the load on the lifting carriage.
  • Such a discharge pressure balance can be arranged in the lowering arm upstream of the control valve and thus upstream of the control valve or arranged downstream of the control valve and thus be connected downstream of the control valve.
  • the usually designed as a slide valve with a spool control valve for controlling the lowering operation of the lifting carriage forms in such a lifting drive in dependence on the operation and deflection of the control valve variable orifice.
  • a discharge pressure compensator arranged upstream of the control valve and thus arranged upstream of the control valve is acted upon by a spring device in the direction of a flow position and by the pressure prevailing in the signal path of the discharge pressure balance upstream of the control valve and thus the load pressure of the lifting drive in the direction of a blocking position.
  • the signal path of the discharge pressure balance is connected to the lowering branch between the discharge pressure balance and the control valve and thus upstream of the measuring diaphragm formed by the control valve.
  • the load pressure of the lifting drive relaxes so far that a predetermined dynamic pressure is applied to the measuring diaphragm formed by the control valve and thus achieves a lowering speed independent of the applied load pressure by the deflection of the control valve and thus the opening cross section of the metering orifice becomes.
  • a downstream of the control valve and thus arranged downstream of the control valve discharge pressure compensator is acted upon by a spring means and the pending between the control valve and the discharge pressure scale pressure in the direction of a flow position and the upstream of the control valve load pressure of the linear actuator in the direction of a blocking position.
  • the maximum outflow volume flow flowing out in the sink branch is limited to the maximum load case of the linear actuator.
  • the maximum load case is the load case with nominal load on the lifting slide with maximum (lowest) viscosity of the pressure medium. The lift tends to oscillate during sink operation and the first overshoot should be below the cut-off point for triggering a down line branch line breaker provided on the lift cylinder.
  • the resulting flow rate flow at part load on the lifting or zero load on the lifting (empty lifting carriage without load) is determined by this and leads in a discharge pressure balance with additional bypass line and bypass diaphragm to a lower or maximum same lowering speed at partial load or no load as at rated load.
  • An operator of the truck noticed the variable sink behavior in the various load cases.
  • the handling line of the truck varies depending on the load and the load on the lifting carriage.
  • the drainage volume flow in the sink branch is heavily dependent on the viscosity of the pressure medium and decreases drastically with decreasing pressure medium temperature and thus increasing viscosity.
  • the handling of the truck thus continues to vary depending on the temperature and thus viscosity of the pressure medium.
  • the present invention has for its object to provide a linear actuator of the type mentioned, which avoids the disadvantages mentioned above.
  • the discharge pressure compensator is provided with a control range of the discharge pressure compensating control device with which the control range of the discharge pressure compensator in response to the load located on the lifting and / or in dependence on the viscosity of the pressure means of the lifting drive is variable ,
  • the handling capacity of the truck can be increased.
  • the control device is designed according to an advantageous embodiment of the invention such that starting from zero load up to a limit load on the lifting the discharge pressure balance has a large control range and starting from the limit load to the rated load on the lifting the discharge pressure compensator has a reduced control range.
  • zero load or partial load this can be achieved with the drain pressure scale maximizing the sink speed.
  • limit load this achieves the result that the discharge pressure compensator allows a standard-filling outflow volume flow to flow out to the container in order to comply with the maximum sink rate of 0.6 m / s prescribed by standards and not to exceed it.
  • the control device is designed according to an advantageous embodiment of the invention such that at high viscosity of the pressure medium, the discharge pressure compensator has a large control range and at low viscosity of the pressure medium, the discharge pressure compensator has a reduced control range. This makes it possible to increase the lowering speed at cold temperatures of the pressure medium and thus high viscosity of the pressure medium in order to accelerate the lowering process of the lifting carriage.
  • the control device comprises a discharge pressure in the direction of the locking position acting spring device whose spring bias is variable in dependence on the load on the lifting and / or in dependence on the viscosity of the pressure medium.
  • the spring device advantageously has a low spring preload, starting from zero load up to a limit load on the lifting carriage, and from the limit load to the rated load on the lifting carriage an increased spring preload.
  • the spring device advantageously has a low spring preload at high viscosity of the pressure medium and increased spring preload at low viscosity of the pressure medium. This achieves a simple way that the discharge pressure balance has a large control range at high viscosity of the pressure medium and at low viscosity of the pressure medium has a reduced control range.
  • a switching valve which has a blocking position and a Has flow position.
  • the switching valve is for this purpose advantageously controlled such that, starting from zero load up to a limit load on the lifting the switching valve is acted upon in the blocking position and from the limit load to the rated load on the lifting the switching valve is acted upon in the flow position.
  • the switching valve is for this purpose advantageously controlled such that at high viscosity of the pressure medium, the switching valve is acted upon in the blocking position and at low viscosity of the pressure medium, the switching valve is acted upon in the flow position.
  • control pressure is formed by the upcoming in the lifting cylinder load pressure.
  • the switching valve is electrically operable according to an advantageous embodiment of the invention and is connected to the operation with an electronic control device, wherein the electronic control device for detecting the load located on the lifting with a load pressure in the lifting cylinder detecting pressure sensor and / or for detecting the viscosity of Pressure medium is in communication with a temperature sensor of the pressure detecting temperature sensor.
  • the switching valve can be controlled in a simple manner as a function of the load on the lifting carriage and / or the viscosity of the pressure medium.
  • the control device changes the control range of the discharge pressure compensator as a function of the center of gravity of the load located on the lifting carriage and / or as a function of an allowable overturning torque of the industrial truck.
  • the limit load as a function of the distance of the load center of gravity of the load from a tilting axis of the truck be adapted or be maximized in load cases with low tipping moment the sink speed.
  • an upstream of the control valve and upstream of the discharge pressure compensator from the sinking branch to the container guided bypass line is provided, in which a bypass aperture is arranged, wherein the bypass aperture is integrated into the discharge pressure compensator.
  • bypass line is shut off with the bypass diaphragm, so that a drain volume flow from the lifting cylinder to the container can only flow through the controlled by the discharge pressure scale sinking branch and compared to the large control range, a reduced maximum lowering speed is achieved.
  • the lifting drive 1 comprises a lifting cylinder 2 and a lowering branch 4 guided as a lowering line from the lifting cylinder 2 to a container 3.
  • the lifting cylinder 2 serves to raise and lower a lifting carriage 5, on which a load-receiving means 6, for example a load fork, is arranged.
  • a load m In the illustrated embodiment is located on the load receiving means 6, a load m.
  • the lifting cylinder 2 is connected to the lifting carriage 5 by means of a traction means 7, for example a lifting chain, in connection with the first end of the Lifting 5 and is attached to the second end of the lifting cylinder 2 and is guided over a arranged at the end of the extendable piston rod 2a of the lifting cylinder 2 guide roller 8.
  • a traction means 7 for example a lifting chain
  • a control valve 10 for controlling the lowering operation of the linear actuator 1 and a discharge pressure compensator 11 is arranged in the lowering branch 4.
  • the control valve 10 and the discharge pressure compensator 11 are arranged in a control way valve block 12.
  • the lowering branch 4 comprises a section 4 a guided by the lifting cylinder 2 to the control-way valve block 12, which may be designed as a hose line, and a section 4 b guided from the control-way valve block 12 to the container 3.
  • the lifting drive 1 further comprises an electronic control device 15, the input side with a load pressure in the lifting cylinder 2 detected pressure sensor 16 and / or with a temperature of the pressure medium detecting temperature sensor 17 is in communication.
  • the pressure sensor 16 detected in the illustrated embodiment, the pressure in the section 4a of the sinking arm 4 and thus the load pressure of the lifting cylinder 2.
  • the temperature sensor 17 detected in the illustrated embodiment, the temperature of the pressure medium in the container 3.
  • the electronic control device 15 With the pressure sensor 16, the electronic control device 15 on detect the load located on the lifting carriage 5 and determine the corresponding load case (zero load, partial load, nominal load). With the temperature sensor 17, the electronic control device 15 can determine the temperature of the pressure medium and thus the viscosity of the pressure medium.
  • the control valve 10 for controlling the lowering operation of the linear actuator 1 is - as in the FIG. 2 is shown in more detail - formed as a throttling in intermediate positions control valve with a blocking position 10a and formed as a lowered position flow position 10b and forms according to the operation and deflection of the control valve 10, a variable orifice 10c in the sinking branch. 4
  • the discharge pressure compensator 11 is arranged in the illustrated embodiment upstream of the control valve 10 in the lowering branch 4 and thus arranged between the lifting cylinder 2 and the control valve 10.
  • the discharge pressure compensator 11 is - as in the FIG. 2 is shown in more detail - designed as a throttling in intermediate positions control valve which is acted upon by a spring device 20 in the direction of a flow position 11a and of the pending in a signal path 21 of the discharge pressure compensator 11 pressure upstream of the control valve 10 in the direction of a blocking position 11b.
  • the signal path 21 is formed by a control pressure line which is connected to the sinking branch 4 between the control valve 10 and the discharge pressure compensator 11 and thus upstream of the metering orifice 10c and is guided to a control pressure chamber 22 of the discharge pressure compensator 11 acting in the direction of the blocking position 11b.
  • bypass line 30 is provided, which is branched off upstream of the control valve 10 and upstream of the discharge pressure compensator 11 from the sinking branch 4 to the container 3 and in which a bypass aperture 31 is arranged.
  • the bypass line 30 is connected to the sinking branch 4 between the lifting cylinder 2 and the discharge pressure compensator 11.
  • the bypass diaphragm 31 is integrated in the discharge pressure compensator 11, which is connected to the bypass line 30 for this purpose.
  • the discharge pressure compensator 11 is thus designed as a four-port valve and has a first flow path, which controls the sinking branch 4, and a second flow path, which controls the bypass line 30.
  • the cross section of the bypass diaphragm 31 is completely released.
  • the blocking position 11b of the discharge pressure compensator 11 the cross section of the bypass diaphragm 31 is shut off.
  • the discharge pressure compensator 11 is provided with a control region of the discharge pressure compensator 11 controlling control device 40, with which the control range of the discharge pressure compensator 11 in response to the load located on the lifting 5 and / or in dependence on the viscosity of the pressure means of the linear actuator 1 is variable.
  • the control device 40 comprises a spring pressure device 11 acting in the direction of the blocking position 11b spring device 41 whose spring preload is variable in dependence on the load located on the lifting slide 5 and / or in dependence on the viscosity of the pressure medium.
  • a pressure translating piston 42 of the control device 40 which is in operative connection with the spring device 41, which can be acted upon by a control pressure.
  • a switching valve 43 of the control device 40 is provided, which has a blocking position 43a and a flow position 43b. The discharge pressure compensator 11 is thus expanded by the pressure booster piston 43.
  • the pressure booster piston 42 is pilot-controlled by means of the switching valve 43.
  • the switching valve 43 is actuated in the illustrated embodiment by a spring device 44 in the blocking position 43a and by an electrical actuator 45, such as a magnet in the flow position 43b.
  • an electrical actuator 45 such as a magnet in the flow position 43b.
  • the electrical actuating device 45 is connected to the electronic control device 15, so that the electronic control device 15 can control the switching valve 43 between the blocking position 43a and the flow position 43b.
  • the control pressure which acts on the pressure booster piston 42 is formed in the illustrated embodiment of the pending in the lifting cylinder 2 load pressure.
  • the switching valve 43 is connected on the input side to a control line 46, which communicates with the section 4a of the sinking branch 4.
  • the switching valve 43 is in the blocking position 43 a, is the pressure booster piston 42 in the in the FIG. 2 clarified position X 0 . If the electrical actuator 45 is driven, the switching valve 43 is actuated in the flow position 43b, so that the pending in the control line 46 control pressure applied to the pressure booster piston 42 and in the in the FIG. 2 clarified position X 1 actuated.
  • the discharge pressure compensator 11 is designed as a proportional valve which, in the blocking position 11 b and thus in the closed state, does not lead any oil flow via the sink branch 4 and via the bypass line 30. As long as the discharge pressure compensator 11 is opened, a constant volume flow flows via the bypass line 30 into the container 3 in accordance with the diaphragm equation. This quantity of pressure medium via the bypass line 30 is independent of whether the pressure booster piston 42 is in the position X 0 or X 1 , since the cross section of the bypass aperture 31 is constant and is open, as long as the discharge pressure compensator 11 is not in the blocking position 11 b. A second volume flow, which is dependent on the valve deflection and has a variable opening cross-section, flows depending on the adjusted valve position via the sink branch 4 to the control valve 10th
  • the maximum flowing volume flow over the sink branch 4 is dependent on the balance of forces acting on the discharge pressure compensator 11 spring means 20, 41.
  • the outflow volume over the sink branch 4 to the control valve 10 is a maximum in the position state X 0 of the pressure booster piston 42 and is reduced in the position X 1 of the pressure booster piston 42, since the pressure booster piston 42, the spring means 41 further biases and the discharge pressure compensator 11 in the FIG. 2 moves left in the direction of the blocking position 11b and reduces the flow cross-section over the sinking branch 4.
  • the over the sink branch 4 to the control valve 10 effluent maximum flow is thus dependent on the position X 0 or X 1 of the pressure booster piston 42nd
  • the pressure booster piston 42 is in the position X 0 , the discharge pressure compensator 11 is in the flow position 11 a and has a large control range, the sinking arm 4 is opened to the maximum and additionally the bypass line 30 is opened with the bypass aperture 31, so that over Expiry scale 11 a maximum drain volume flow in the sink branch 4 to the control valve 10 and in the bypass line 30 to the container 3 can flow.
  • the pressure booster piston 42 is in the position X 1 , receives the spring means 41 by the displacement of the pressure booster piston 42 from the position X 0 in the position X 1 an additional spring bias, so that the discharge pressure compensator 11 is displaced in the direction of the blocking position 11b.
  • the flow cross-section is reduced via the lowering branch 4, the bypass line 30 with the bypass aperture 31 is further additionally opened.
  • the discharge pressure compensator 11 thus has a reduced control range. In the reduced control range, the maximum flow cross-section of the sinking branch 4 is reduced and via the discharge pressure compensator 11, a reduced outflow volume flow can flow via the sink branch 4 to the control valve 10.
  • the control device 40 is designed such that, starting from zero load to a limit load on the lifting slide 5, the discharge pressure compensator 11 has the large control range and starting from the limit load to the nominal load on the lifting slide 5, the discharge pressure compensator 11 has the reduced control range.
  • the limit load corresponds to a limit load pressure value which is determined by means of the pressure sensor 16 from the electronic control device 15.
  • the control device 40 is additionally or alternatively designed such that at high viscosity of the pressure medium, the discharge pressure compensator 11 has the large control range and at low viscosity of the pressure medium, the discharge pressure compensator 11 has the reduced control range.
  • the spring device 41 of the control device 40 starting from zero load up to the limit load on the lifting carriage 5, has a low spring preload and, starting from the limit load up to the rated load on the lifting carriage 5, an increased preload.
  • the spring device 41 additionally or alternatively has a low spring preload with a high viscosity of the pressure medium and an increased spring preload with a low viscosity of the pressure medium.
  • the switching valve 43 of the control device 40 is in this case controlled by the electronic control device 15, that from zero load to the limit load on the lifting 5, the switching valve 43 is acted upon in the blocking position 43 a and starting from the limit load to the rated load on the lifting 5 the Switching valve 43 is applied in the flow position 43b.
  • the switching valve 43 of the control device 40 is controlled by the electronic control device 15 that at high viscosity of the pressure medium, the switching valve 43 is acted upon in the blocking position 43a and at low viscosity of the pressure medium, the switching valve 43 is acted upon in the flow position 43b.
  • the switching valve 43 is operated at no load or partial load (limit load) on the lifting 5 or at high viscosity of the pressure medium by not energizing the electrical actuator 45 in the blocking position 43a, the pending in the control line 46 load pressure of the lifting cylinder 2 is not to Pressure booster piston 42 forwarded so that the pressure booster piston 42 is in the position X 0 .
  • the spring device 41 receives no additional spring preload and the discharge pressure compensator 11 has the large control range in which the discharge pressure compensator 11 has a maximum flow cross-section and 30 via the sink branch 4 and the bypass line a high, maximum drain volume flow from the lifting cylinder 2 to the container 3 can flow , It is thereby achieved that the lifting carriage 5 is lowered even at no load or partial load on the lifting carriage 5 or at high viscosity of the pressure medium with a maximum lowering speed of 0.6 m / s or a lowering speed greater than 0.6 m / s.
  • the spring device 41 receives an additional spring preload and the discharge pressure compensator 11 is moved in the direction of the blocking position 11b, so that the discharge pressure compensator 11 has a reduced control range in which the discharge pressure compensator 11 a smaller flow cross-section than the maximum flow cross-section has a large control range.
  • a drain volume flow can only flow away from the lifting cylinder 2 to the container 3 via the sink branch 4.
  • the bypass line 30 is shut off.
  • the flow cross-section at reduced control range of the discharge pressure compensator 11 is designed such that only a so large normer Jewishder drain volume flow can flow through the discharge pressure compensator 11, that the limited by standards maximum lowering speed of 0.6 m / s is maintained. This ensures that above the limit load and rated load or at low viscosity of the pressure medium, the maximum lowering speed of 0.6 m / s of the lifting carriage 5 is maintained and not exceeded.
  • the discharge pressure compensator 11 thus has in the position X 0 of the pressure booster piston 42 in the operating state empty load or partial load or high viscosity of the pressure medium on a large control range, so that through the open bypass line 30 via the bypass aperture 31, a maximum drain volume flow from the lifting cylinder 2 to the container 3 can flow out.
  • the bypass line 30 is open, the flow resistance of the discharge pressure compensator 11 decreases, so that at low temperatures of the pressure medium and thus high viscosity of the pressure medium and up to the limit load on the lifting carriage 5, the lifting carriage 5 is lowered at the highest possible lowering speed.
  • the discharge pressure compensator 11 has a reduced control range and operates as usual to the standards-limited maximum lowering speed of 0.6 m / s to comply with the lifting carriage 5.
  • the control device 40 the control range of the discharge pressure compensator 11 in addition to change depending on the load center of the load located on the lifting 5 and / or in dependence on an allowable overturning torque of the truck.
  • the maximum lowering speed of the rated load lift 5 is limited by standards to the value of 0.6 m / s to prevent sinking, i. a stop of the lowering movement of the lifting slide 5 such an impulse introduced into the truck, which causes a tilting moment about the front of the truck and would lead to tipping the truck forward.
  • the maximum lowering speed of the lifting carriage 5 is limited by standards to the value of 0.6 m / s in order to prevent the incidence of arranged on the lifting cylinder 2 line rupture protection.
  • the tipping moment introduced into the truck during the lowering stop reduces the residual load capacity and thus the stability of the truck in the short term and, in the event of an abrupt stopping of the lifting carriage 5, can lead to tilting of the truck to the front.
  • the delay of the lifting carriage 5 at the lowering stop and thus the pulse generated is proportional to the force acting on the lifting 5 by the load recorded weight. With reduction of the weight and thus the load on the lifting 5 or the Load pressure in the lifting cylinder 2 reduces the delay in lowering stop.
  • the truck has a lower load or no load on the lifting 5 a much higher stability. In the load case without load on the lifting 5 tilting the truck to the front when lowering stop is not provoked.
  • the lowering speed can be increased to the limited by the standards value of 0.6 m / s or a value beyond (> 0.6 m / s) as long as the line break safety device is not triggered.
  • the load on the lifting 5 has a small distance of the center of gravity of the truck's tilting axis, the load generates a low tilting moment, so that the limit load can be increased up to which the switching valve 43 is actuated in the flow position 43b and thus the discharge pressure balance 11 has the large control range with high sink speed.
  • the lowering speed can be increased by determining the load case of the lifting slide 5 to the value of 0.6 m / s or beyond, as long as an allowable overturning moment during lowering stop is not exceeded and thus the stability of the truck is not endangered.
  • the invention has a number of advantages: With the discharge pressure compensator 11 according to the invention, the lifting slide 5 can be lowered at no load or at partial load and at high viscosity of the pressure medium with the highest possible lowering speed.
  • the lowering speed in particular when the lifting carriage 5 is unloaded, can be maximized.
  • sluggish drain operations can be accelerated due to high viscosity of the pressure medium.
  • an increase in the handling capacity of the truck can be achieved, in particular in a load cycle lifting the lift with rated load and lowering the lifting with unloading, since each lowering operation of the lifting can be performed faster.
  • the invention is not limited to the illustrated embodiment with an upstream of the control valve 10 arranged discharge pressure compensator 11.
  • the discharge pressure compensator 11 can be arranged in the lower branch 4 downstream of the control valve 10.

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Claims (13)

  1. Entraînement de levage hydraulique (1) d'une machine de travail mobile, en particulier d'un chariot de manutention, pour lever et abaisser un chariot de levage (5), l'entraînement de levage (1) présentant un cylindre de levage (2) et une soupape de commande (10) pour commander le mode d'abaissement de l'entraînement de levage (1), une balance de pression d'évacuation (11) étant disposée dans une branche d'abaissement (4) guidée depuis le cylindre de levage (2) vers un contenant (3), laquelle est sollicitée par un dispositif de ressort (20) dans la direction d'une position d'écoulement (11a), et par la pression s'exerçant dans une voie de signal (21) de la balance de pression d'évacuation (11) en amont de la soupape de commande (10), dans la direction d'une position de blocage (11b), caractérisé en ce que la balance de pression d'évacuation (11) est pourvue d'un dispositif de commande (40) commandant la plage de réglage de la balance de pression d'évacuation (11), avec lequel la plage de réglage de la balance de pression d'évacuation (11) peut être modifiée en fonction de la charge appliquée au chariot de levage (5) et/ou en fonction de la viscosité du fluide de pression de l'entraînement de levage (1).
  2. Entraînement de levage hydraulique selon la revendication 1, caractérisé en ce que le dispositif de commande (40) est réalisé de telle sorte qu'à partir de la charge nulle jusqu'à une charge limite appliquée au chariot de levage (5), la balance de pression d'évacuation (11) présente une grande plage de réglage et à partir de la charge limite jusqu'à la charge nominale appliquée au chariot de levage (5), la balance de pression d'évacuation (11) présente une plage de réglage réduite.
  3. Entraînement de levage hydraulique selon la revendication 1 ou 2, caractérisé en ce que le dispositif de commande (40) est réalisé de telle sorte que dans le cas d'une grande viscosité du fluide de pression, la balance de pression d'évacuation (11) présente une grande plage de réglage, et dans le cas d'une faible viscosité du fluide de pression, la balance de pression d'évacuation (11) présente une plage de réglage réduite.
  4. Entraînement de levage hydraulique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le dispositif de commande (40) comprend un dispositif de ressort (41) sollicitant la balance de pression d'évacuation (11) dans la direction de la position de blocage (11b), la précontrainte de ressort duquel peut être modifiée en fonction de la charge appliquée au chariot de levage (5) et/ou en fonction de la viscosité du fluide de pression.
  5. Entraînement de levage hydraulique selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le dispositif de ressort (41), à partir de la charge nulle jusqu'à une charge limite appliquée au chariot de levage (5), présente une faible précontrainte de ressort, et à partir de la charge limite jusqu'à la charge nominale appliquée au chariot de levage (5), présente une précontrainte de ressort accrue.
  6. Entraînement de levage hydraulique selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le dispositif de ressort (41), dans le cas d'une viscosité élevée du fluide de pression, présente une faible précontrainte de ressort, et dans le cas d'une faible viscosité du fluide de pression, présente une précontrainte de ressort accrue.
  7. Entraînement de levage hydraulique selon l'une quelconque des revendications 4 à 6, caractérisé en ce que pour faire varier la précontrainte de ressort du dispositif de ressort (41), il est prévu un piston de transfert de pression (42) en liaison fonctionnelle avec le dispositif de ressort (41), qui peut être sollicité par une pression de commande, une soupape de commutation (43) étant prévue pour commander la sollicitation du piston de transfert de pression (42) avec la pression de commande, laquelle présente une position de blocage (43a) et une position d'écoulement (43b).
  8. Entraînement de levage hydraulique selon la revendication 7, caractérisé en ce que la soupape de commutation (43) est commandée de telle sorte qu'à partir de la charge nulle jusqu'à une charge limite appliquée au chariot de levage (5), la soupape de commutation (43) soit sollicitée dans la position de blocage (43a) et qu'à partir de la charge limite jusqu'à la charge nominale appliquée au chariot de levage (5), la soupape de commutation (23) soit sollicitée dans la position d'écoulement (43b).
  9. Entraînement de levage hydraulique selon la revendication 7 ou 8, caractérisé en ce que la soupape de commutation (43) est commandée de telle sorte que pour une viscosité élevée du fluide de pression, la soupape de commutation (43) soit sollicitée dans la position de blocage (43a), et que pour une faible viscosité du fluide de pression, la soupape de commutation (43) soit sollicitée dans la position d'écoulement (43b).
  10. Entraînement de levage hydraulique selon l'une quelconque des revendications 7 à 9, caractérisé en ce que la pression de commande est formée par la pression de charge s'établissant dans le cylindre de levage (2).
  11. Entraînement de levage hydraulique selon l'une quelconque des revendications 7 à 10, caractérisé en ce que la soupape de commutation (43) peut être actionnée électriquement et, pour son actionnement, est en liaison avec un dispositif de commande électronique (15), le dispositif de commande électronique (15), pour détecter la charge (m) appliquée au chariot de levage (5), étant en liaison avec un capteur de pression (16) détectant la pression de charge dans le cylindre de levage (2) et/ou pour la détection de la viscosité du fluide de pression, étant en liaison avec un capteur de température (17) détectant la température du fluide de pression.
  12. Entraînement de levage hydraulique selon l'une quelconque des revendications 1 à 11, caractérisé en ce que le dispositif de commande (40) modifie la plage de réglage de la balance de pression d'évacuation (11) en fonction du centre de gravité de charge de la charge (m) appliquée au chariot de levage (5) et/ou en fonction d'un couple de basculement admissible du chariot de manutention.
  13. Entraînement de levage hydraulique selon l'une quelconque des revendications 1 à 12, caractérisé en ce qu'une conduite de dérivation (30) guidée depuis la branche d'abaissement (4) vers le récipient est prévue en amont de la soupape de commande (10) et en amont de la balance de pression d'évacuation (11), dans laquelle est disposé un diaphragme de dérivation (31), le diaphragme de dérivation (31) étant intégré dans la balance de pression d'évacuation (11).
EP18164844.5A 2017-04-06 2018-03-29 Entraînement de levage hydraulique d'une machine de travail mobile, en particulier d'un chariot de manutention Active EP3385215B9 (fr)

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