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EP0770163B1 - Procede et dispositif de positionnement precis d'accessoires basculants montes sur des chassis de levage a mouvement descendant d'engins de chantier - Google Patents

Procede et dispositif de positionnement precis d'accessoires basculants montes sur des chassis de levage a mouvement descendant d'engins de chantier Download PDF

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Publication number
EP0770163B1
EP0770163B1 EP95926860A EP95926860A EP0770163B1 EP 0770163 B1 EP0770163 B1 EP 0770163B1 EP 95926860 A EP95926860 A EP 95926860A EP 95926860 A EP95926860 A EP 95926860A EP 0770163 B1 EP0770163 B1 EP 0770163B1
Authority
EP
European Patent Office
Prior art keywords
tilting
piston
piston rod
cylinder
pump
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
EP95926860A
Other languages
German (de)
English (en)
Other versions
EP0770163A1 (fr
Inventor
Gustav Leidinger
Walter Kolb
Günter BRÖNNER
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.)
CNH Industrial Baumaschinen GmbH
Original Assignee
O&K Orenstein and Koppel GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE4437300A external-priority patent/DE4437300C2/de
Application filed by O&K Orenstein and Koppel GmbH filed Critical O&K Orenstein and Koppel GmbH
Publication of EP0770163A1 publication Critical patent/EP0770163A1/fr
Application granted granted Critical
Publication of EP0770163B1 publication Critical patent/EP0770163B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • E02F3/43—Control of dipper or bucket position; Control of sequence of drive operations
    • E02F3/431—Control of dipper or bucket position; Control of sequence of drive operations for bucket-arms, front-end loaders, dumpers or the like
    • E02F3/432—Control of dipper or bucket position; Control of sequence of drive operations for bucket-arms, front-end loaders, dumpers or the like for keeping the bucket in a predetermined position or attitude
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • E02F3/43—Control of dipper or bucket position; Control of sequence of drive operations
    • E02F3/431—Control of dipper or bucket position; Control of sequence of drive operations for bucket-arms, front-end loaders, dumpers or the like
    • E02F3/432—Control of dipper or bucket position; Control of sequence of drive operations for bucket-arms, front-end loaders, dumpers or the like for keeping the bucket in a predetermined position or attitude
    • E02F3/433—Control of dipper or bucket position; Control of sequence of drive operations for bucket-arms, front-end loaders, dumpers or the like for keeping the bucket in a predetermined position or attitude horizontal, e.g. self-levelling

Definitions

  • the invention relates to a method for the correct positioning of the on a downward moving mast of a mobile machine, in particular a wheel loader, tiltable work tool, in particular a shovel, according to the generic Share the first two claims.
  • Mobile machines especially wheel loaders, have work equipment, in particular Buckets on the frame of the working machine by means of a lifting and lowering mast are stored.
  • the work equipment especially the shovel
  • the work equipment after the mast has been lowered into a position that is problem-free
  • This position is usually one that runs approximately parallel to the surface to be machined.
  • mobile machines with automatic return for work equipment in particular the shovel, which after activation, preferably by pressing a button, the Work equipment when lowering the mast back into the specified working position, especially digging position.
  • DE-A 41 28 959 is a shovel loader device on any work vehicle known, in which at least one tilt cylinder at one end on the loader frame above the Loading arm and at the other end on a rocker arm that can be swiveled on the loading arm Formation of a parallel kinematics is articulated, which is indirectly connected to the rocker arm Loading shovel remains constant over the entire lifting range of the loading arm holds upward pivot position.
  • the tilt cylinder has one through the cylinder bottom passed through extended piston rod section, the length of which is at least corresponds to that of the piston stroke and that attached to the cylinder with one Bearing eye provided connecting link a corresponding receptacle with side access is assigned to replace the seals of the cylinder base.
  • the extended piston rod section forms a displacement measuring element for a switchable electro-hydraulic control, through which the cylinder adjustment movement or the tilting movement of the loading shovel on one certain place is stopped, in particular its admission position with the timetable corresponds in general to parallel blade bottom.
  • a switchable electro-hydraulic control through which the cylinder adjustment movement or the tilting movement of the loading shovel on one certain place is stopped, in particular its admission position with the timetable corresponds in general to parallel blade bottom.
  • US-A 3,726,428 is a device for positioning the one moving downwards Mast of a mobile machine, in particular a wheel loader, can be tilted arranged work equipment with at least one by the drive motor the driven machine pump and a spool including a spool to control at least one responsible for moving the work equipment Tilt cylinder.
  • the pump delivers depending on the speed of the drive motor Hydraulic oil in various hydraulic lines on a double acting hydraulic cylinder are switched in the area of a solenoid valve.
  • potentiometric control different circuits can be implemented, e.g. also lowering the mast as well tipping of work equipment in the near-earth area.
  • the addition of tax times result relatively long overrun times of the tilt cylinder, so that the work equipment is not parallel but hits the floor at an angle up or down.
  • the object of the invention is therefore to determine the predeterminable angle of the work equipment, in particular the blade angle, with most of the operating conditions that occur to keep constant when lowering the mast.
  • This goal is achieved on the one hand in that when the piston rod is extended of the tilt cylinder at predeterminable points several measurements of the distance covered the piston rod are carried out, the first measured value triggering a signal to that effect, that the switching logic activates another solenoid valve that moves the tilting piston into one position leads in which a predeterminable reduced oil flow flows to the tilt cylinder, and that at another now slowed down movement of the piston rod a further measured value triggers another signal that the switching logic deactivates both solenoid valves and the oil flow to the tilt cylinder is interrupted.
  • this goal is also achieved in that when extending the piston rod of the tilt cylinder several measurements of the distance covered at predeterminable points Way of the piston rod are carried out, the first measured value triggers a signal that the Switching logic activates another solenoid valve and simultaneously the first solenoid valve is deactivated, causing the tilting piston is guided into a position in which a predefinable reduced oil flow flows to the tilt cylinder, and that when the extension of the piston rod is now slowed down another measured value another signal to that effect triggers that the switching logic now also the rest Solenoid valve deactivated and the oil flow to the tilt cylinder is interrupted.
  • One according to one or the other method according to one or more of claims 1 to 7 working device has work equipment that can be tilted on the mast, especially a shovel, at least one through the drive motor of the driven machine pump and a control slide containing a tilting piston for actuation at least one for moving work equipment responsible tilt cylinder, several from a pilot pump Actuable solenoid valves for displacement the tilting piston as a function of a specified extension path the piston rod of the tilt cylinder, at least one Measuring device in the area of the piston rod to record the current extension of the piston rod and one with the Solenoid valves connected switching logic that the solenoid valves as a function of the measured values of the measuring device controls that the further solenoid valve at a first measured value to reduce the oil flow through the spool is activated and with a second measured value the Oil flow through the control spool is interrupted.
  • the other solenoid valve conducts then oil from the pilot pump into one that can be operatively connected to the tilting piston Adjustment cylinder.
  • the adjusting cylinder has one large area that the force generated when the control pressure is applied is greater, so that the tilting piston is only up to a position predetermined by the stop of the piston can move.
  • This stop is chosen so that the tilting piston is as large as possible Control opening releases that due to the setting on the regulator of the working hydraulic pump Load-sensing differential pressure can still pass an amount of oil that is about the same or around is slightly lower than the amount of oil that can be extracted at idling speed of the diesel engine. As soon as the extension of the piston rod of the tilt cylinder is now slow the control flag leaves the effective range of the proximity switch, it is deactivated, i.e. his signal drops again.
  • both solenoid valves are now (first alternative) or, according to the second alternative, the further solenoid valve switched off again, so that the tilting piston is springs to its central position centered and thus the oil flow to the tilt cylinder is interrupted, causing the piston rod of the tilt cylinder comes to a standstill and thus also the end position of the work equipment is specified.
  • the length of the control flag is preferably to be determined so that at the highest speed of the Drive motor and thus the greatest possible flow of the working hydraulic pump the piston rod of the tilt cylinder during the time from the triggering of the proximity switch when the control flag approaches, either until the adjustment cylinder stops or until the position specified by this stop is reached Tilting piston passes, the piston rod of the tilting cylinder only travels such a distance, which is the same or a little less than the specified length of the control flag.
  • Figure 1 shows a schematic representation of a circuit diagram, which in this example for a Wheel loaders not shown can be used.
  • the lifting frame 1 of the wheel loader is shown schematically, which at an articulation point 2 of the Wheel loader frame is articulated and raised.
  • a shovel 3 work equipment which is via a lever mechanism 4,5 can be actuated by means of a tilt cylinder 6.
  • the tilt cylinder 6 includes a piston rod 7 and is itself articulated in the region of a pivot point 8 on no further shown frame of the wheel loader attached.
  • At the end of the piston rod 7 is one Support rod 9 attached, which acts as part of a measuring device at its free end Tax flag 10 carries.
  • the tilt cylinder 6 is here by a working hydraulic pump that can be regulated in terms of its delivery pressure and volume by means of a regulator 15 16, which is driven by a diesel engine 17, operable in such a way that the volume flow of the variable displacement pump 16, as described later, in this example via the Line 18 is guided to the piston side 19 of the tilt cylinder 6.
  • solenoid valves 20, 21 are provided which can be actuated by a pilot pump 22.
  • the solenoid valve 20 acts here via the line 23 with the tilting piston 24 of this part only shown control spool 25 together, which is centered between two springs 26,27.
  • the Solenoid valve 21 interacts via line 28 with an adjusting cylinder 29, the Piston rod 30 is operatively connected to the tilting piston 24.
  • the Switching logic 13 constructed as a relay activates the solenoid valve 20 so that the tilting piston 24 of the control slide 25, via which the bucket tipping mechanism 5 is actuated, with that on the pressure relief valve 31 of the pilot pump 22 set pressure is applied.
  • the tilting piston In this example, 24 moves to the left into its end position, so that the working hydraulic pump 16 promotes its oil in the space 19 of the tilt cylinder 6 which triggers the tilting movement.
  • the size of this oil flow depends on the current speed of the drive motor 17 (because in the case of wheel loaders, the control opening 33 is dimensioned such that the at or close to the Maximum speed of the drive motor pumped oil flow this can also happen).
  • this stop is chosen so that the tilting piston 24 has a control opening, however large 33 releases that due to the setting on the controller 15 of the working hydraulic pump 16 Load-sensing differential pressure can still pass through such an amount of oil that the same or is a little lower than the conveyable at idle speed of the drive motor 17 Amount of oil.
  • the rear edge of the control lug 10 the effective range of the proximity switch 11 again, it is deactivated, i.e. his signal drops again.
  • the length of the control flag 10 is to be determined so that at the highest speed of the drive motor 17 and thus the largest possible flow of the working hydraulic pump 16 die Piston rod 7 during the time from the triggering of the proximity switch 11 when approaching the control vane 10 until it reaches the stop of the piston of the adjusting cylinder 29 passes, the piston rod 7 only travels in such a way that the same or by one is slightly less than the length of the control flag 10.
  • Figure 2 shows a schematic representation of an alternative circuit diagram to Figure 1, in this Example of a backhoe loader not shown can be used. There essentially the same components are used, some of which are only different are actuated, the same reference numerals as in Figure 1 are used.
  • the lifting frame 1 of the backhoe loader is shown schematically, which at a pivot point 2 the loader frame is articulated so that it can be raised and lowered.
  • the mast 1 At the lower end of the mast 1 is in this case articulated as a shovel 3 work equipment, which via a lever mechanism 4,5 can be actuated by means of a tilt cylinder 6.
  • the tilt cylinder 6 includes a piston rod 7 and is itself articulated in the region of a pivot point 8 on no further illustrated frame of the backhoe attached.
  • At the end of the piston rod 7 is one Support rod 9 attached, which acts as part of a measuring device at its free end Tax flag 10 carries.
  • the tilt cylinder 6 On the tilt cylinder 6 there is a proximity switch in this example 11 formed component arranged as a twelfth part of a measuring device, the an electrical signal line 12 in operative connection with one, preferably on a relay basis built switching logic 13 is.
  • the switching logic 13 could also be electronic Base.
  • the switching logic 13 is in this case preferably in the driver's cabin (Not shown) provided button 14 can be activated.
  • the tilt cylinder 6 is here by a working hydraulic pump that can be regulated in terms of its delivery pressure and volume by means of a regulator 15 16, which is driven by a diesel engine 17, operable in such a way that the volume flow of the variable displacement pump 16, as described later, in this example via the Line 18 is guided to the piston side 19 of the tilt cylinder 6.
  • solenoid valves 20, 21 are provided which can be actuated by a pilot pump 22.
  • the solenoid valve 20 acts here via the line 23 with the tilting piston 24 of this part only shown control spool 25 together, which is centered between two springs 26,27.
  • the Solenoid valve 21 interacts via line 28 with an adjusting cylinder 29, the Piston rod 30 is operatively connected to the tilting piston 24.
  • the Switching logic 13 constructed as a relay activates the solenoid valve 20 so that the tilting piston 24 of the control slide 25, via which the bucket tipping mechanism 5 is actuated, with that on the pressure relief valve 31 of the pilot pump 22 set pressure is applied.
  • the tilting piston In this example, 24 moves to the left into its end position, so that the working hydraulic pump 16 promotes its oil in the space 19 of the tilt cylinder 6 which triggers the tilting movement.
  • the size of this oil flow depends on the current speed of the drive motor 17.
  • a signal is triggered, which activates the solenoid valve 21 via the switching logic 13 and the electrical line 34 and at the same time deactivates the solenoid valve 20.
  • the solenoid valve 21 now directs oil from the Pilot pump 22 via line 28 into the adjusting cylinder 28.
  • the adjusting cylinder 29 has so large an area that the one generated when the control pressure was applied Force is greater than the restoring force of the spring 26 of the tilt piston 24.
  • the tilt piston 24 moves by the force of the spring 26 so far in the corresponding direction until it reached by the stroke of the adjusting cylinder 29 predetermined position ..
  • this Stop is selected so that the tilting piston 24 opens a control opening 33, no matter how large, that due to the load-sensing differential pressure set on the regulator 15 of the working hydraulic pump 16 can still pass through such an amount of oil that is equal to or around one is slightly lower than the amount of oil that can be pumped at idle speed of the drive motor 17.
  • the extension of the piston rod 7 of the tilting cylinder is now slowed down 6 the rear edge of the control flag 10 the effective range of the proximity switch 11 leaves again, it is deactivated, i.e. his signal drops again.
  • the solenoid valve 21 is now also de-energized via the electrical line 34, so that the tilting piston 24 is centered in its central position by the force of the springs 26, 27 and so that the oil flow to the tilt cylinder 6 is interrupted, whereby the piston rod 7 and so that the tipper 5 come to a standstill.
  • the length of the control flag 10 is to be determined so that at the highest speed of the drive motor 17 and thus the largest possible flow of the working hydraulic pump 16 die Piston rod 7 during the time from the triggering of the proximity switch 11 when approaching the control vane 10 until it reaches the stop of the piston of the adjusting cylinder 29 passes, the piston rod 7 only travels in such a way that the same or by one is slightly less than the length of the control flag 10.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Operation Control Of Excavators (AREA)

Claims (16)

  1. Procédé destiné à positionner avec précision l'outil de travail basculant, en particulier le godet (3), monté sur un bras de levage (1) articulé d'un engin de chantier mobile, en particulier une chargeuse sur roues, dans lequel, à la suite de la manoeuvre d'un dispositif automatique de positionnement (14), une logique de commande (13) agissant conjointement avec ce dernier active une vanne magnétique (20), de telle sorte que le piston de basculement (24) d'une soupape pilote (25) est commandé dans une position laissant passer le flux d'huile refoulé par une pompe (16), régulées en particulier, vers le vérin de basculement (6), caractérisé en ce que, pendant que la tige de piston (7) du vérin de basculement (6) continue à se déplacer hors du vérin, le trajet parcouru parla tige de piston (7) est mesuré en plusieurs points prédéfinis, la première valeur de mesure déclenchant un signal par lequel la logique de commande (13) active une deuxième vanne magnétique (21), qui entraíne le piston de basculement (24) dans une position dans laquelle un flux d'huile est réduit de manière prédéfinie et est acheminé vers le vérin de basculement (6), et en ce que, pendant que la tige de piston (7) continue à se déplacer de manière plus lente maintenant hors du vérin, une deuxième valeur de mesure déclenche un autre signal par lequel la logique de commande (13) désactive les deux vannes magnétiques (20,21) et interrompt le flux d'huile vers le vérin de basculement (6).
  2. Procédé destiné à positionner avec précision l'outil de travail basculant, en particulier le godet (3), monté sur un bras de levage (1) articulé d'un engin de chantier mobile, en particulier une chargeuse sur roues, dans lequel, à la suite de la manoeuvre d'un dispositif automatique de positionnement (14), une logique de commande (13) agissant conjointement avec ce dernier active une vanne magnétique (20), de telle sorte que le piston de basculement (24) d'une soupape pilote (25) est commandé dans une position laissant passer le flux d'huile refoulé par une pompe (16), régulée en particulier, vers le vérin de basculement (6), caractérisé en ce que, pendant que la tige de piston (7) est mesuré en plusieurs points prédéfinis, la première valeur de mesure déclenchant un signal par lequel la logique de commande (13) active une deuxième vanne magnétique (21) et désactive simultanément la première vanne magnétique (20), ce qui entraíne le piston de basculement (24) dans une position dans laquelle un flux d'huile est réduit de manière prédéfinie et est acheminé vers le vérin de basculement (6), et en ce que, pendant que la tige de piston (7) continue à se déplacer de manière plus lente maintenant hors du vérin, une deuxième valeur de mesure déclenche un autre signal par lequel la logique de commande (13) désactive maintenant aussi la deuxième vanne magnétique (21) et interrompt le flux d'huile vers le vérin de basculement (6).
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que, à la suite de l'activation de la vanne magnétique (20), le piston de basculement (24) est sollicité par une pression régulée par une soupape de surpression (31) d'une pompe pilote (22).
  4. Procédé selon l'une quelconque des revendications 1 à 3, caractérisé en ce que les mesures du trajet parcouru par la tige de piston sont exécutées sans contact.
  5. Procédé selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le piston de basculement (24), à la suite de son mouvement de retour, libère encore une ouverture de commande (33) suffisamment grande pour encore laisser passer une quantité d'huile qui dépend de la pression différentielle de détection de charge régulée par le régulateur (15) de la pompe hydraulique de travail (16), laquelle quantité d'huile est égale ou légèrement inférieure à la quantité d'huile pouvant être acheminée pendant la vitesse à vide du moteur (17).
  6. Procédé selon l'une quelconque des revendications 1 à 5, caractérisé en ce que les points de mesure sont définis de telle sorte que, en présence de la vitesse de rotation maximale du moteur (17) et, de ce fait, en présence du plus grand flux d'huile possible refoulé par la pompe hydraulique de travail (16), la tige de piston (7) pendant l'intervalle de temps entre le déclenchement du signal pour la vanne magnétique (21) et la position du piston de basculement (24) déterminée par le vérin de réglage (29), ne se déplace que sur une distance qui est égale ou légèrement inférieure à la longueur de la palette de commande (10).
  7. Procédé selon l'une quelconque des revendications 1 à 5, caractérisé en ce que les points de mesure sont définis de telle sorte que, en présence de la vitesse de rotation maximale du moteur (17) et, de ce fait, en présence du plus grand flux d'huile possible refoulé par la pompe hydraulique de travail (16), la tige de piston (7) pendant l'intervalle de temps entre le déclenchement du signal pour les vannes magnétiques (20 et 21) et la position du piston de basculement (24) déterminée par le vérin de réglage (29), ne se déplace que sur une distance qui est égale ou légèrement inférieure à la longueur de la palette de commande (10).
  8. Dispositif destiné à la mise en oeuvre du procédé selon l'une quelconque des revendications 1 à 7, comprenant un dispositif de travail basculant, en particulier un godet basculant (3), monté contre le bars de levage, au moins une pompe (16) qui peut être actionnée par le moteur (17) de l'engin de chantier et une vanne pilote (25) contenant un piston de basculement (24) et destinée à commander au moins un vérin de basculement (6) assurant le déplacement du dispositif de travail (3), plusieurs vannes magnétiques qui peuvent être sollicitées par une pompe pilote (22) et qui sont destinées à déplacer le piston de basculement (24) en fonction d'un déplacement prédéfini de la tige de piston (7) hors du vérin de basculement (6), au moins un dispositif de mesure (10,11) installé dans la zone de la tige de piston (7) et destiné à enregistrer le déplacement actuel de la tige de piston (7) hors du vérin, ainsi qu'une logique de commande (13) reliée aux vannes magnétiques (20,21) qui commande les vannes magnétiques (20,21) en fonction des valeurs mesurées par le dispositif de mesure (10,11), de telle sorte qu'en présence d'une première valeur de mesure la deuxième vanne magnétique (21) est activée par la vanne pilote (25) pour réduire le flux d'huile et en présence d'une deuxième valeur de mesure la vanne pilote (25) interrompt le flux d'huile.
  9. Dispositif selon la revendication 8, caractérisé en ce que la logique de commande (13) est conçue selon le principe du relais.
  10. Dispositif selon les revendications 8 et 9, caractérisé en ce que la pompe (16) est conçue sous forme de pompe hydraulique de travail de l'engin de chantier et sous forme de pompe de réglage dont il est possible de réguler le volume du fluide à acheminer.
  11. Dispositif selon l'une quelconque des revendications 8 à 10, caractérisé en ce que le dispositif de mesure est formé par un détecteur de proximité (11) monté dans la zone du vérin de basculement (6), lequel détecteur de proximité est en liaison active, par l'intermédiaire de la ligne de transmission des signaux (12), avec la logique de commande (13).
  12. Dispositif selon l'une quelconque des revendications 8 à 11, caractérisé en ce qu'une palette de commande (10) est montée dans la zone de la tige de piston (7), laquelle peut être guidée pendant le déplacement de la tige de piston (7) hors du vérin au-dessous du détecteur de proximité (11) prévu au niveau du vérin de basculement (6).
  13. Dispositif selon l'une quelconque des revendications 8 à 12, caractérisé en ce que le piston de basculement (24) de la vanne pilote (25), actionné par une vanne en fonction du trajet parcouru par la tige de piston (7), peut être guidé à l'aide d'un vérin de réglage (29) à partir d'une position complètement ouverte vers une position (33) partiellement ouverte prédéfinie.
  14. Dispositif selon l'une quelconque des revendications 8 à 13, caractérisé en ce que le piston du vérin de réglage (29) présente une surface plus grande que celle du piston de basculement (24), de telle sorte que le piston de basculement (24), sous l'effet de la pression différentielle et sous l'effet de la force exercée par le ressort (26), est déplacé jusqu'à ce que le piston du vérin de réglage (29) ait atteint sa butée.
  15. Dispositif selon l'une quelconque des revendications 8 à 13, caractérisé en ce que le piston du vérin de réglage (29) est muni d'une surface dont la dimension est définie de telle sorte que la force produite au moment de la sollicitation avec la pression de commande est supérieure à la force de rappel du ressort (26) du piston de basculement (24), de telle sorte que le piston de basculement (24) ne se déplace que jusque dans une position prédéfinie par la butée du vérin de réglage (29).
  16. Dispositif selon l'une quelconque des revendications 8 à 15, caractérisé en ce que, lorsque les vannes magnétiques (20,21) sont désactivées, le piston de basculement (24) peut être ajusté dans sa position centrale sous l'effet de la force exercée par deux ressorts (26,27).
EP95926860A 1994-07-13 1995-07-12 Procede et dispositif de positionnement precis d'accessoires basculants montes sur des chassis de levage a mouvement descendant d'engins de chantier Expired - Lifetime EP0770163B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4424621 1994-07-13
DE4424621 1994-07-13
DE4437300 1994-10-19
DE4437300A DE4437300C2 (de) 1994-07-13 1994-10-19 Verfahren und Einrichtung zur lagegerechten Positionierung der an einem abwärts sich bewegenden Hubgerüst einer mobilen Arbeitsmaschine kippbar angeordneten Arbeitsausrüstung
PCT/EP1995/002721 WO1996002707A1 (fr) 1994-07-13 1995-07-12 Procede et dispositif de positionnement precis d'accessoires basculants montes sur des chassis de levage a mouvement descendant d'engins de chantier

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EP0770163A1 EP0770163A1 (fr) 1997-05-02
EP0770163B1 true EP0770163B1 (fr) 1999-05-26

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EP (1) EP0770163B1 (fr)
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WO2000058565A1 (fr) * 1999-03-31 2000-10-05 Caterpillar Inc. Systeme de position libre du godet
DE19939796C1 (de) 1999-08-21 2000-11-23 Orenstein & Koppel Ag Verfahren und Arbeitsmaschine zur Herstellung von Bodenflächen
DE102006024731B3 (de) * 2006-05-26 2007-08-16 Cnh Baumaschinen Gmbh Verfahren zur lagegerechten Ausrichtung einer an einem heb- und senkbaren Hubgerüst einer Arbeitsmaschine kippbar angeordeten Arbeitausrüstung sowie Arbeitsmaschine
WO2021192969A1 (fr) 2020-03-26 2021-09-30 日立建機株式会社 Véhicule de travail

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US3484010A (en) * 1967-10-09 1969-12-16 Caterpillar Tractor Co Control system for an ejector bucket
US3726428A (en) * 1971-02-04 1973-04-10 Int Harvester Co Control circuit for front end loader
GB2035464B (en) * 1978-11-28 1982-12-15 Dartec Ltd Actuator protection assemblies
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DE3409705A1 (de) * 1984-03-16 1985-09-19 Robert Bosch Gmbh, 7000 Stuttgart Verfahren zur rueckmeldung von stoerungen auf die bremspedalcharakteristik und hydraulischer bremskraftverstaerker
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DE4128959A1 (de) * 1991-08-30 1993-03-04 Schaeff Karl Gmbh & Co Schaufellader-kippzylinder
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WO1994018399A1 (fr) * 1993-02-09 1994-08-18 Hitachi Construction Machinery Co., Ltd. Dispositif de commande hydraulique pour une machine de chantier
JPH0685449U (ja) * 1993-05-24 1994-12-06 株式会社小松製作所 排土板制御装置
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US5784812A (en) 1998-07-28
ATE180529T1 (de) 1999-06-15
EP0770163A1 (fr) 1997-05-02
WO1996002707A1 (fr) 1996-02-01

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