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EP1108895B1 - Valve hydraulique pour la commande d'un consommateur indépendant de la charge - Google Patents

Valve hydraulique pour la commande d'un consommateur indépendant de la charge Download PDF

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Publication number
EP1108895B1
EP1108895B1 EP00124779A EP00124779A EP1108895B1 EP 1108895 B1 EP1108895 B1 EP 1108895B1 EP 00124779 A EP00124779 A EP 00124779A EP 00124779 A EP00124779 A EP 00124779A EP 1108895 B1 EP1108895 B1 EP 1108895B1
Authority
EP
European Patent Office
Prior art keywords
control
consumer
spool
chamber
function position
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 - Lifetime
Application number
EP00124779A
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German (de)
English (en)
Other versions
EP1108895A1 (fr
Inventor
Peter BÜTTNER
Tatu Miikkulainen
Jukka Pekkanen
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth 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
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1108895A1 publication Critical patent/EP1108895A1/fr
Application granted granted Critical
Publication of EP1108895B1 publication Critical patent/EP1108895B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B2013/0413—Valve members; Fluid interconnections therefor with four or more positions

Definitions

  • the invention is based on a hydraulic directional control valve, which is load-independent Control of a hydraulic consumer, in particular a hydraulic Consumer of a mobile working machine, in terms of direction and speed serves and that the characteristics from the preamble of the claim 1 has.
  • the wheel motors of a hydraulic traction drive in an open operate hydraulic circuit and the pressure medium paths between the Wheel motors, a hydraulic pump and a tank by means of a directional valve to Taxes.
  • the directional control valve is one with four connections, namely with a the hydraulic pump connected to the inlet port, with a connected to the tank Drain connection and with two consumer connections, of which lines lead to the two sides of the wheel motors, and with three positions. In a Center position of the directional control valve are the two consumer connections with each other and fluidly connected to the tank, the wheel motors are so to speak switched off and can e.g. when towing the machine spin.
  • the wheel motors In the middle position of the directional valve so you have a kind of swimming operation the wheel motors, which is why the corresponding position of a directional valve below Also referred to as swimming function position.
  • the two lateral Positions of the directional control valve is the one connection of the wheel motors with the Hydropumpe.und the other terminal connected to the tank.
  • the directional control valve Depending on which lateral position the directional control valve takes, rotate the wheel motors ie in a first direction or in the opposite, second direction.
  • This fourth Switch position is thus a floating function position. It lies, from the spring-centered Locking function position seen beyond the one directional functional position.
  • US-A-4 355 660 discloses a device provided for throttle control Directional valve, in which in a spring-centered blocking function position, the two consumer connections A and B shut off and the inlet port and the drain port connected to each other.
  • This directional control valve is one Float function between the blocking function position and a directional function position.
  • the well-known hydraulic directional control valve for load-independent control of a hydraulic consumer is designed to be in a special kind of load-independent control, namely a controller with a load-independent Flow distribution of the amount of pressure medium to be used.
  • a controller with a load-independent Flow distribution of the amount of pressure medium to be used.
  • the pressure compensator is in the opening direction of the pressure after the metering orifice and in the closing direction of the highest load pressure and a weak one Compressed spring applied.
  • the applicant is a hydraulic directional control valve for the load-independent control of a hydraulic consumer known in which the pressure compensator of the metering orifice is connected upstream Pressure compensator in the closing direction of the pressure upstream of the metering in Closing direction and the individual load pressure of each consumer and from a spring, which determines the pressure difference across the metering orifice, in Closing direction acted upon.
  • the invention has for its object to provide a hydraulic directional control valve for Load-independent control of a hydraulic consumer, the characteristics from the preamble of claim 1, so to develop, that with it certain hydraulic consumers in the different operating modes can be controlled without dangerous movements occur.
  • This task is at a hydraulic directional control valve with the features
  • the preamble of claim 1 according to the invention achieved in that according to the characterizing part of patent claim 1 the floating function position the spool between the blocking function position and a Directional function position is.
  • An inventive hydraulic directional control valve is particularly suitable for use within a hydraulic traction drive, for the control of a Bogie axis as well as for the control of hydraulic Rotary actuators suitable for cranes
  • a bogie axle is an axle, the two wheels arranged one behind the other in the longitudinal direction of the vehicle and can be swiveled around itself
  • Bogie axles are used especially in forestry machines. In the forest should the wheels can swing freely, that is, the bogie can swim when driven becomes. When you start working with the crane of the forest machine, On the other hand, all pivot points should be locked so that the machine has a fixed position Stand has. In difficult terrain, e.g. when driving over a pit against it a Bogierad must be raised and held up. As a result, it is convenient when used with a directional control valve, which is used to control a bogie axle is, according to claim 4 a predetermined by a spring arrangement Rest position of the spool the locking function position is The device is then firmly supported and you can work with the crane.
  • the spool is out of the rest position in a floating function position where the consumer connections with connected to the tank and the bogie axis can freely commute. Do you want one Raise the wheel, so the spool is placed in a directional function position
  • the control for the bogie axis is also intrinsically safe. In case of a failure the spool gets into the blocking function position due to the spring centering, in which the bogie axis is locked for movement and the stability of the Vehicle is guaranteed. It only worsens the ride comfort.
  • the floating function position as a rest position after each direction of actuation of the spool towards a blocking function position at.
  • the floating function position between a lock function position and a direction function position when not right next to the latter.
  • one major part of the Slider strokes can be used to control the speed. At a Drive this can be of particular advantage, since you usually forward faster than going backwards and then in for speed control Forward direction a large stroke is available.
  • the spool throttled the two consumer connections with the Drain connection are fluidly connected.
  • the advantage is that a gedrosseite Connection can be designed so that the leakage in the blocking function position only slightly increased.
  • at least one hydraulic traction drive when controlling a bogie axle or rotary actuators on cranes, the volume flows in the floating function position of the Control spool flow, so low that the throttling the swimming of the hydraulic or the hydraulic consumer is not affected.
  • the spool is slidable in a sliding bore to the usual run around each other spaced control chambers, whose fluidic Connections are controlled with each other via the spool.
  • control chambers connected to the consumer terminals are connected and are called in the following consumer combs.
  • the consumer comb are adjacent and connected to the drain port of the directional control valve are. So so a consumer connection with the drain port fluidly to connect, the spool must have a flow area between a Open the consumer chamber and the adjacent drainage chamber.
  • this is done in a particularly preferred manner in that the Spool a running in its longitudinal direction, radially open and axial has on both sides limited connecting groove whose length is greater than the clear distance between the consumer chamber and the drain chamber is.
  • This connection groove can be easily introduced into a slide collar of the spool.
  • the connection between the consumer chamber and drain chamber more or less throttled.
  • the connection is interrupted as soon as one or the other end of the connecting groove from the existing between consumer chamber and drain chamber web the valve housing is covered.
  • a locking function position, which between a Floating function position and a directional function position is obtained one thereby advantageously by an embodiment according to claim 9.
  • an embodiment according to claim 10 is the Wegmaschineswolf between the blocking function position and a directional function position.
  • the directional control valve is preferably electric or electrohydraulic actuated.
  • those of an electrical pilot control device given control signals electrically processed and accordingly modified to be given to the electric actuators.
  • the spool in a lying outside the rest position Locking function or floating function position for a specific Hub hold as long as the electrical pilot signal within a certain Area lies.
  • the two proportionally adjustable directional control valves shown are intended to around together with an upstream of a metering pressure compensator to control a hydraulic load independent of the load pressure.
  • way valve and pressure balance are, as can be seen particularly clearly from Figure 3, to a Directional valve disc combined with a valve housing 10.
  • a spool bore 11 through which a spool 12 is axially movable is.
  • the length of the spool 12 is consistent with the length of the slide bore 11 from the one end face 13 to the other end face 14 of the valve housing 10 match.
  • the slide bore 11 is spaced from five axially Steuerkammem surrounded, which the inflow of pressure medium to and the drain of pressure medium from a hydraulic consumer, e.g. a wheel motor, a a Bogie actuated cylinder or a rotary drive on one Crane, serve and their fluidic connections with each other from the spool 12 are controlled.
  • the middle control chamber 15 of the five Steuerkammem is the inlet chamber. This flows pressure medium via a channel 16 from the pressure compensator 17 forth.
  • On both sides of the inlet chamber is located respectively a consumer chamber 18 and 19, each with a at the end of a Consumer channel lying consumer port 20 and 21 of the valve disc connected is.
  • Each consumer chamber 18 or 19 is followed by a drain chamber 22 and 23, to one of two passing through the valve housing 10 Tank channels 24 is open.
  • the spool 12 increases due to two centering springs 34, which in the End faces 13 and 14 of the valve housing 10 fastened and the slide bore 11 outwardly closing lids 35 are housed, a middle position from which it is steadily adjusted in opposite directions can. At maximum stroke, it beats each on an adjustable stroke limiter 36 on.
  • the spool 12 has a slide neck 37, which in the Centered to the inlet chamber 15 is centered
  • the two control collars 38 and 39 on both sides of the pusher neck 37 are so long that in the middle position of the Spool her one end face at a distance from the inlet chamber 15th and its other end face is located in the drain chamber 22 and 23, respectively.
  • Both piston collars have control grooves 40 and 41, which at one end face or at the other end face are axially open. In the middle position of the spool 12 the control grooves 40 and 41 are located between the control chambers Covered housing webs, so that on the Steuemuten no open fluid There is a connection between individual control chambers. After a short another neck follows on the control collar 39 another slide collar 42, the the spring chamber in which a lid 35 seals against the discharge chamber 23.
  • the distance between the drain chamber 22 and the end face 13 of the valve housing 10 is greater than the distance between the drain chamber 23 and the Stim side 14. Between the drain chamber 22 and the end face 13 are located in the slide bore 11, three axially spaced chambers 43, 44th and 45, wherein the middle of these three chambers referred to as Lastmeldehunt 44 be. To each of the two chambers 43 and 45 is the entrance of a Pressure limiting valve 46 connected. Each of these two pressure relief valves is installed in a bore of the valve housing 10. In the in the Figures 3 and 5 shown center position of the spool 12 extends a slide collar 47 from the end face 13 of the valve housing 10 into the area the housing web between the chamber 45 and the drain chamber 22.
  • valve collar 47 has at its the drain chamber 22 facing outer edge of a notch 50 through which the chamber 45 and the discharge chamber 32 with a small opening cross-section to each other are open when the spool 12 is in its middle position after a certain way of the spool out of its middle position in one direction becomes this fluidic connection between the drainage chamber 22 and the chamber 45 and thus the chamber 44 closed.
  • a another notch 51 has the same function in an adjustment of the spool 12 in the opposite direction. Only after a certain stroke the fluidic connection between the chamber 44 via the chamber 45 to Drain chamber 22 interrupted. Will the spool 12 from its center position moved out to the specific stroke, the load reporting chamber 44 is ever according to the direction of movement of the spool from the chamber 43 or from the Chamber 45 separated.
  • the pressure compensator 17 has a control piston 65 which is in a slide bore 11 parallel and from the end face 14 in the valve housing 10th introduced blind bore 66 is inserted in the blind bore 66 are axially spaced apart from each other an inlet chamber 67, from a perpendicular to the Sectional plane according to Figures 3 and 5 extending inlet bore 68 cut is formed, and a drain chamber 69, which via the channel 16 with the inlet chamber 15 of the slide bore 11 is connected.
  • the control piston 65 can with a control edge 70, which is provided with Feinêtnuten, an opening cross-section between the two chambers 67 and 69 to influence.
  • the pressure equivalent is in the range between 10 and 20 bar.
  • a spring chamber in one of the two covers 35 acted upon by a control pressure.
  • two electromagnetically actuated pilot valves 72 and 73 which in the a lid 35 are used and as proportionally adjustable pressure reducing valves are formed.
  • a maximum control pressure of e.g. 30 bar is limited to the two pilot valves 72 and 73 control oil via a channel 74 in Valve housing 10 fed while control oil flow through a channel 75 can.
  • the two embodiments shown of directional valves according to the invention on both sides of the spring-centered middle position Have working positions in which the one consumer outlet via the pressure compensator and the metering diaphragm pressure medium from a pressure medium source can flow while from the other consumer connection pressure medium in the Tankchannel 24 and from there via a drain connection of the directional control valve to a Tank flows.
  • the spool 12 is in the tax customer 38 and 39 with additional connecting grooves 80, 81 or 82 provided in Longitudinal direction of the spool 12 extend, limited at both axial ends are and only a small depth in the radial direction of the spool 12 have.
  • the connecting grooves 80 and 81 of the embodiment of Figures 3 and 4 and the connecting grooves 82 of the embodiment of Figure 5 are in the longitudinal direction of Spool 12 longer than the clear distance between a consumer chamber and the adjacent drain chamber.
  • control grooves 80 and 81 are arranged on the control dogs 38 and 39, a control groove 80 on one piston collar and a control groove 80 on the other Piston collar and a Steuemut 81 on a piston collar with a Steuemut 81st on the other piston collar are in alignment with each other.
  • FIGS. 3 and 4 Also in the embodiment of Figure 5 is aligned a connecting groove 82 on the slide collar 38 with a connecting groove 82 on the slide collar 39. Otherwise, the Position of the connecting grooves 82 with respect to the consumer and drain chambers in the middle position of the spool 12 differently than in the execution of the FIGS. 3 and 4.
  • the position of the connecting grooves 82 on the control dogs 38 and 39 is such that in the centered center position of the spool 12, the connecting groove 82 of the control collar 38 both to the consumer chamber 18 and the Drain chamber 22 and the connecting groove 82 on the control collar 39 both to the consumer chamber 19 and the discharge chamber 23 is open.
  • FIG 1 The circuit diagram of Figure 1 is according to the embodiment of FIG 5 designed. It is once again clear that in the middle position of the spool 12 the consumer chambers 18 and 19 and the chambers 43, 44 and 45 are connected to the Wegkammem 22 and 23, and that the inlet chamber 15 is shut off.
  • the connection between a consumer chamber to the neighboring Drain chamber is a throttled connection, which in Figure 1 by the chokes formed by the connecting grooves 82 is indicated.
  • a directional control valve with the diagram of Figure 1 is preferably for controlling a hydraulic traction drive
  • a directional control valve with the diagram of Figure 2 preferably for controlling a bogie axle or a rotary drive for a crane or a rotator used at the free end of a crane.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Sliding Valves (AREA)

Claims (16)

  1. Un distributeur hydraulique pour la commande d'un récepteur hydraulique, indépendamment de la charge et en termes de sens et de vitesse, doté d'un raccord (68) d'alimentation, doté d'un raccord (24) d'évacuation et doté de deux raccords (20, 21) de récepteur, doté d'un tiroir (12) de distributeur, qui peut coulisser dans la direction axiale à l'intérieur d'un alésage (11) de distributeur dans un corps (10) de valve et qui permet de commander les connexions par voie fluide entre les raccords (20, 21, 24, 68), cependant que, dans une position de fonction de fermeture du tiroir (12) de distributeur, le raccord (68) d'alimentation est fermé et la connexion entre les raccords (20, 21) de récepteur et d'une part le raccord (68) d'alimentation, d'autre part le raccord (24) d'évacuation, est fermée et cependant que, dans une position de fonction flottante du tiroir (12) de distributeur, le raccord (68) d'alimentation est fermé et les deux raccords (20, 21) de récepteur sont reliés par voie fluide au raccord (24) d'évacuation et, dans deux positions de fonction de sens du tiroir (12) de distributeur, l'un des raccords (20, 21) de récepteur est relié, par voie fluide, au raccord (68) d'alimentation et l'autre raccord (21, 20) de récepteur est relié, par voie fluide, au raccord (24) d'évacuation,
    caractérisé en ce que
    la position de fonction flottante du tiroir (12) de distributeur est située entre la position de fonction de fermeture et une position de fonction de sens.
  2. Un distributeur hydraulique selon la revendication n° 1, caractérisé en ce que le tiroir (12) de distributeur est centré dans une position de repos par un dispositif (34) de ressorts et que la position de repos est la position de fonction flottante.
  3. Un distributeur hydraulique selon la revendication n° 2, caractérisé en ce que le tiroir (12) de distributeur peut être amené à coulisser hors de la position de fonction flottante, de part et d'autre, dans des sens opposés, pour atteindre une position de fonction de fermeture.
  4. Un distributeur hydraulique selon la revendication n° 1, caractérisé en ce que le tiroir (12) de distributeur est centré dans une position de repos à l'aide d'un dispositif (34) de ressorts et que la position de repos est la position de fonction de fermeture.
  5. Un distributeur hydraulique selon la revendication n° 4, caractérisé en ce que le tiroir (12) de distributeur peut être amené à coulisser hors de la position de fonction de fermeture, dans des sens opposés, de part et d'autre, pour atteindre une position de fonction flottante.
  6. Un distributeur hydraulique selon une revendication précédente, caractérisé en ce que dans une position de fonction flottante du tiroir (12) de distributeur, les deux raccords (20, 21) de récepteur sont reliés, par voie fluide et de façon étranglée, au raccord (24) d'évacuation.
  7. Un distributeur hydraulique selon une revendication précédente, caractérisé en ce que le tiroir (12) de distributeur présente un épaulement (38, 39) de commande, qui, dans la position de fonction flottante et dans la position de fonction de fermeture et au moins sur une partie de sa longueur, est disposé entre une chambre (18, 19) de récepteur, reliée à un raccord (20, 21) de récepteur, et une chambre (22, 23) d'évacuation, voisine de la précédente et reliée au raccord (24) d'évacuation, de l'alésage (11) de distributeur, et que l'épaulement (38, 39) de commande présente un évidement (80, 81 ; 82), qui dans la position de fonction de fermeture n'est ouvert que sur l'une des deux chambres (18, 22, 19, 23) et dans la position de fonction flottante est ouvert sur les deux chambres (18, 22, 19, 23).
  8. Un distributeur hydraulique selon la revendication n° 7, caractérisé en ce que l'évidement est une rainure (80, 81, 82) de raccordement, qui est orientée dans la direction longitudinale du tiroir de commande, qui est ouverte dans la direction radiale et qui est délimitée de part et d'autre dans la direction axiale, dont la longueur est supérieure à l'espacement entre la chambre (18, 19) de récepteur et la chambre (22, 23) d'évacuation.
  9. Un distributeur hydraulique selon la revendication n° 8, caractérisé en ce que l'épaulement (38) de commande est pourvu de fentes (41) de progressivité à partir de sa face orientée vers la chambre (22, 23) d'évacuation et qu'un segment de course, qui correspond à la position de fonction de fermeture, est parcouru lors d'un déplacement du tiroir (12) de commande à partir du point, où la rainure (82) de raccordement vers la chambre (22, 23) d'évacuation est fermée, jusqu'au point, où les fentes (41) de progressivité sont ouvertes sur la chambre (18, 19) de récepteur.
  10. Un distributeur hydraulique selon la revendication n° 8, caractérisé en ce que l'épaulement (38, 39) de commande présente une rainure (80) de raccordement, qui est ouverte uniquement sur la chambre (18, 19) de récepteur, lorsque le tiroir (12) de commande est dans sa position de repos, qui d'abord ouvre également sur la chambre (22, 23) d'évacuation, lorsque le tiroir (12) de commande est amené à coulisser hors de sa position neutre, et qui se ferme par rapport à la chambre (18, 19) de récepteur, après une course ultérieure.
  11. Un distributeur hydraulique selon la revendication n° 10, caractérisé en ce que le tiroir (12) de commande présente un deuxième épaulement (39, 38) de tiroir, qui, dans les positions de fonction flottante et de fermeture et au moins sur une partie de sa longueur, est disposé entre une deuxième chambre (19, 18) de récepteur, reliée au deuxième raccord (21, 20) de récepteur, et une deuxième chambre (23, 22) d'évacuation, voisine de la précédente et reliée au raccord (24) d'évacuation, de l'alésage (11) de distributeur, que le deuxième épaulement (39, 38) de commande est pourvu de fentes (41) de progressivité à partir de sa face orientée vers la deuxième chambre (23, 22) d'évacuation et que le deuxième épaulement (39, 38) de commande présente une rainure (81) de raccordement, qui est ouverte uniquement sur la deuxième chambre (23, 22) d'évacuation, lorsque le tiroir (12) de commande est dans sa position de repos, et qui ouvre également sur la deuxième chambre (19, 18) de récepteur, lorsque le tiroir (12) de commande est amené à coulisser hors de sa position neutre, et qui après une course ultérieure se ferme par rapport à la deuxième chambre (23, 22) d'évacuation, environ en un point où les fentes (41) de progressivité du deuxième épaulement (39, 38) de commande ouvrent sur la deuxième chambre (19, 18) de récepteur.
  12. Un distributeur hydraulique selon la revendication n° 11, caractérisé en ce que les fentes (41) de progressivité du deuxième épaulement (39, 38) de commande ouvrent sur la deuxième chambre (23, 22) d'évacuation, peu après que la rainure (81) de raccordement du deuxième épaulement (39, 38) de commande vers la deuxième chambre (23, 22) d'évacuation soit fermée.
  13. Un distributeur hydraulique selon la revendication n° 11 ou n° 12, caractérisé en ce que chacun des épaulements (38, 39) de commande présente une première rainure (80) de raccordement, qui dans la position de repos du tiroir (12) de commande est ouverte sur une chambre (18, 19) de récepteur, et une deuxième rainure (81) de raccordement, qui dans la position de repos est ouverte sur une chambre (22, 23) d'évacuation, et que, dans la direction axiale, une première rainure (80) de raccordement du premier épaulement (38) de commande est alignée sur une première rainure (80) de raccordement du deuxième épaulement (39) de commande et une deuxième rainure (81) de raccordement du premier épaulement (38) de commande est alignée sur une deuxième rainure (81) de raccordement du deuxième épaulement (39) de commande.
  14. Un distributeur hydraulique selon une des revendications n° 8 à n° 13, caractérisé en ce que à chaque rainure (80, 81, 82) de raccordement sur un épaulement (38, 39) de commande correspond une autre rainure (80, 81, 82) de raccordement, disposée de façon exactement diamétralement opposée.
  15. Un distributeur hydraulique selon une revendication précédente, caractérisé en ce que il peut être actionné par voie électrique ou électro-hydraulique.
  16. Une utilisation d'un distributeur hydraulique selon une revendication précédente au sein d'un entraínement hydraulique de déplacement, au sein d'une commande hydraulique pour un axe de bogie ou au sein d'un entraínement hydraulique de mouvement de rotation pour une grue ou pour un rotateur à l'extrémité libre d'une grue.
EP00124779A 1999-12-02 2000-11-14 Valve hydraulique pour la commande d'un consommateur indépendant de la charge Expired - Lifetime EP1108895B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19957952A DE19957952A1 (de) 1999-12-02 1999-12-02 Hydraulisches Wegeventil zur lastunabhängigen Steuerung eines hydraulischen Verbrauchers von insbesondere einer mobilen Arbeitsmaschine
DE19957952 1999-12-02

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EP1108895A1 EP1108895A1 (fr) 2001-06-20
EP1108895B1 true EP1108895B1 (fr) 2003-07-23

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EP00124779A Expired - Lifetime EP1108895B1 (fr) 1999-12-02 2000-11-14 Valve hydraulique pour la commande d'un consommateur indépendant de la charge

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EP (1) EP1108895B1 (fr)
AT (1) ATE245771T1 (fr)
DE (2) DE19957952A1 (fr)
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DE102011120302A1 (de) * 2011-12-03 2013-06-06 Robert Bosch Gmbh Hydraulisches Wegeventil für das Hubwerk eines landwirtschaftlichen Fahrzeugs
CN110374949A (zh) * 2018-04-13 2019-10-25 丹佛斯动力系统（浙江）有限公司 阀和具有该阀的液压系统
US11654815B2 (en) 2021-02-01 2023-05-23 Caterpillar Inc. Closed center hoist valve with snubbing

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DE10107532A1 (de) * 2001-02-17 2002-08-29 Mannesmann Rexroth Ag Wegeventil zur lastunabhängigen Steuerung eines hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit
DE10135298A1 (de) * 2001-07-24 2003-02-13 Bosch Rexroth Ag Ventilanordnung
DE102008018546A1 (de) 2008-04-12 2009-10-15 Robert Bosch Gmbh Ventilanordnung, insbesondere für ein mobiles Arbeitsgerät
DE102010053805A1 (de) * 2010-12-08 2012-06-14 Robert Bosch Gmbh Wegeventil zur insebondere lastunabhängigen Steuerung eines hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit
CN102398866B (zh) * 2011-10-26 2013-12-25 徐州重型机械有限公司 一种起重机变幅控制阀及起重机变幅液压系统
DE102013014671A1 (de) 2013-09-03 2015-03-05 Hydac Technology Gmbh Ventilbaukomponenten
DE102014209277A1 (de) * 2014-05-16 2015-11-19 Robert Bosch Gmbh Anti-Pendel-Ventil für einen hydraulischen Drehantrieb
DE102014012117A1 (de) * 2014-08-12 2016-02-18 Hydac Fluidtechnik Gmbh Steuerungsvorrichtung für einen fluidisch betätigbaren Arbeitszylinder mit zumindest einer Heben- und Senkenfunktion
CN105201943B (zh) * 2015-01-23 2017-05-03 徐州重型机械有限公司 换向阀、油缸下落控制阀以及起重机变幅系统
EP3020983B1 (fr) * 2014-11-14 2020-04-22 Danfoss Power Solutions Aps Module d'entrée pour une unité de soupape
WO2019219492A1 (fr) * 2018-05-18 2019-11-21 Hydac Systems & Services Gmbh Soupape

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DE102011120302A1 (de) * 2011-12-03 2013-06-06 Robert Bosch Gmbh Hydraulisches Wegeventil für das Hubwerk eines landwirtschaftlichen Fahrzeugs
CN110374949A (zh) * 2018-04-13 2019-10-25 丹佛斯动力系统（浙江）有限公司 阀和具有该阀的液压系统
CN110374949B (zh) * 2018-04-13 2020-12-04 丹佛斯动力系统（浙江）有限公司 阀和具有该阀的液压系统
US11654815B2 (en) 2021-02-01 2023-05-23 Caterpillar Inc. Closed center hoist valve with snubbing

Also Published As

Publication number Publication date
ATE245771T1 (de) 2003-08-15
DK1108895T3 (da) 2003-11-03
EP1108895A1 (fr) 2001-06-20
DE50002982D1 (de) 2003-08-28
DE19957952A1 (de) 2001-06-07

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