EP0427001A1 - Chariot élévateur avec un mât de levage disposé mobilement - Google Patents

Chariot élévateur avec un mât de levage disposé mobilement Download PDF

Info

Publication number
EP0427001A1
EP0427001A1 EP90119648A EP90119648A EP0427001A1 EP 0427001 A1 EP0427001 A1 EP 0427001A1 EP 90119648 A EP90119648 A EP 90119648A EP 90119648 A EP90119648 A EP 90119648A EP 0427001 A1 EP0427001 A1 EP 0427001A1
Authority
EP
European Patent Office
Prior art keywords
mast
cylinder
arrangement
piston
damping
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.)
Granted
Application number
EP90119648A
Other languages
German (de)
English (en)
Other versions
EP0427001B1 (fr
Inventor
Rainer Dr.-Ing. Bruns
Friedrich Wilhelm Groll
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.)
Jungheinrich AG
Original Assignee
Jungheinrich AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19893937404 external-priority patent/DE3937404A1/de
Priority claimed from DE9006695U external-priority patent/DE9006695U1/de
Priority claimed from DE19904019075 external-priority patent/DE4019075C2/de
Application filed by Jungheinrich AG filed Critical Jungheinrich AG
Publication of EP0427001A1 publication Critical patent/EP0427001A1/fr
Application granted granted Critical
Publication of EP0427001B1 publication Critical patent/EP0427001B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • B66F9/08—Masts; Guides; Chains
    • B66F9/082—Masts; Guides; Chains inclinable

Definitions

  • the invention relates to a stacking vehicle with a mast, on which a load carrier is vertically movable and which is movably mounted on the vehicle, either displaceably or pivotably, an arrangement which counteracts vibrations being provided in the region of the lower part of the mast.
  • the invention relates in a further embodiment to such a stacking vehicle, in which at least one actuator acts on the mast, with which a displacement or pivoting of the mast can be carried out.
  • Such an actuator can be designed mechanically as a lever arrangement or in the form of a spindle.
  • a control cylinder arrangement which is operated with hydraulic fluid and whose piston engages at the lower end of the mast is particularly preferred.
  • the mast In the case of a displaceable arrangement of the mast, it is mounted, for example, in slide guides or rails. In the case of a pivotable arrangement, the mast is pivotably mounted about the pivot pin above its lower end.
  • the mast can be constructed from several telescopic mast sections and tends to vibrate, particularly in the longitudinal direction of the vehicle. This also applies to the hydraulic control circuit with its flexible lines, which may also result in vibrations when the actuator is designed hydraulically.
  • Such vibrations occur in particular when the vehicle is driving over uneven ground, the vehicle is accelerated (starting or braking), the mast is tilted or shifted.
  • the invention has for its object to improve a stacking vehicle of the type specified in such a way that the resulting vibrations of the mast are largely suppressed or damped and thus an exact positioning of the load carrier is achieved in a very short time, with rapid positioning being achieved in a particularly preferred embodiment should be, at which vibrations per se remain possible, but such vibrations are permitted in a special embodiment in a different way by the storage and are counteracted in an improved manner by the use of the arrangement or such arrangements which counteract the vibrations.
  • the purpose is to absorb vibrations which depend on the weight of the load and the height on the mast, and to suppress or damp them as quickly as possible, so that the load carrier can be positioned without any delay.
  • this object is achieved in that the arrangement counteracting vibrations is provided on the actuator with at least one spring and at least one damper, and in that a spring and a damper are provided in a parallel arrangement in the arrangement.
  • the arrangement counteracting vibrations is functionally provided on the actuator in a series arrangement with the latter.
  • the expression "on the actuator” expresses the relationship to the actuator.
  • the arrangement can be integrated in the actuator.
  • the parts that counteract the vibrations are expediently provided outside the actuator.
  • Shock absorber-like devices can be provided as dampers, which are equipped with the means known in this context, which oppose an adjustment of a deceleration force.
  • dampers are known as shock absorbers in vehicles.
  • both the spring and the damper have an almost linear characteristic.
  • a viscous damper is preferred in which energy is converted into heat by the internal friction of a flowing medium.
  • the functional arrangement in rows or in succession relates to the physical principle and not to a spatial, geometric arrangement.
  • the spring can be designed in different ways. In this way, e.g. Disc springs, coil springs, gas pressure springs are used. In the case of gas pressure springs, the spring force can be applied by means of a flexible, in particular elastic membrane, in addition to the compressibility of the medium and any spring supports. Hydraulic accumulators are included here.
  • a parallel arrangement of the damper and the spring in the arrangement counteracting the vibrations also designates the principle of physical action and not a spatial, geometrical assignment existing in the design.
  • the damper has a constricted passage for a hydraulic pressure medium that can circulate in the damper.
  • the passage can be designed as a constricted bore.
  • the passage is provided as an annular gap.
  • a spring stiffness with an optimal damping setting is expediently chosen in such a way that the damping of the system with the mast is maximum, with an optimal damping constant of the system just being achieved with an optimal damper constant d opt, in which an oscillating movement subsided after two to three oscillations is.
  • the arrangement counteracting the vibrations can be provided as a self-contained assembly without external influences for a fluid, in particular a largely mechanical design, which can also be used particularly advantageously with a mechanical actuator.
  • the invention prefers that an actuating cylinder arrangement is provided as the actuator and that a hydraulic control is connected to this actuating cylinder arrangement. If in this case the arrangement counteracting vibrations can also be used in the manner described, it is preferred in this embodiment, however, that this arrangement is designed with a cylinder in which a piston works against hydraulic pressure medium guided in the cylinder, which works by means of at least one Connection is taken up by the actuator assembly.
  • the rigidity of the actuating cylinder arrangement is expediently as great as possible.
  • the dimensioning of the parts results from the above information, from which the measurement of the at least one spring in connection with the at least one damper can also be derived.
  • the damper consists of a cylinder piston arrangement in which a piston in a cylinder works against pressure medium enclosed in the cylinder, then this is an advantageous feature of the invention.
  • the piston rod is led out on one side towards the mast, the end of the cylinder opposite the piston rod being connected to a control device for adjusting the mast, and the cylinder spaces on both Piston sides are connected via a preload valve, preferably that at least on one side of the actuating cylinder an arrangement which counteracts the vibrations is provided in the form of at least one cylinder, the input of which is designed as a throttle section, in particular a throttle bore, and in which a piston supported on both sides by a spring is movable, the end of the cylinder opposite the throttle section being connected to the surroundings by a filter.
  • this is a mechanical, self-contained assembly with a connection, the pressure being transmitted through the bore to the piston at the same time as it is converted into heat.
  • Both ends of the actuating cylinder arrangement are expediently connected to a cylinder, which is also called damping cylinder in the following.
  • a cylinder which is also called damping cylinder in the following.
  • This also includes the fact that an annular gap is arranged as a throttle section.
  • both ends of the actuating cylinder are connected to a damping cylinder, a throttling section being arranged at one input and a cylinder space downstream of the throttling section having a piston which has a piston rod which is brought out, is provided at the other input.
  • the relevant connection between the actuating cylinder and the damping cylinder is provided between the cylinder spaces each penetrated by a piston rod, and the piston is resiliently supported on both sides in the damping cylinder.
  • a particularly advantageous feature is that the area ratio of the piston area to the diameter of the piston rod with respect to the piston in the actuating cylinder on the one hand and the piston in the damping cylinder is the same.
  • the damping cylinder is subdivided by means of a wall provided with through-openings and, on the one hand, the wall of the resiliently supported pistons with the piston rod brought out and, on the other hand, the wall an inner body provided with smaller outer dimensions than the inner diameter of the damping cylinder, on the outer circumference thereof Passage gap is formed between the connection provided at this end of the damping cylinder and the wall.
  • the piston in the damping cylinder is supported on both sides by a spring. Both the throttle section of the damping cylinder and the springs for the two-sided loading and zeroing of the piston in the damping cylinder are expediently arranged within the damping cylinder, although an arrangement outside is also not excluded.
  • Such a design is robust and, due to the interchangeability of the body, it can also be adapted to different conditions.
  • a connection of each end of the actuating cylinder is connected to a hydraulic accumulator known per se, the membrane of which in each case forms the spring and in the connection of which a constricted passage, in particular a bore, is arranged as a throttle section.
  • the mast is advantageously pivotally mounted in side supports and is movably guided in the longitudinal direction of the vehicle, and that the mast can be pivoted at the lower end is articulated and furthermore the arrangement which counteracts the vibrations is provided in the lower region of the lifting frame.
  • the guide of the mast which is movable in the longitudinal direction of the vehicle, now not in its base, but in the swivel mounting means that additional damping evasive movements are possible in the event of a vibration about the swivel axis.
  • This is particularly advantageous because the damping arrangement, which counteracts the vibrations, acts directly at the height at which the pivot bearing can deflect in the longitudinal direction of the vehicle.
  • the arrangement which counteracts the vibrations, of which one is arranged on each side has a particularly favorable effect.
  • the lower end of the mast is adjustable and an actuator is mounted on the linkage.
  • the pivot point is maintained in the area of the pivot bearing by the arrangements counteracting the vibrations, so that the mast inclination is set, but no translatory movement is carried out.
  • the actuating device engages at the lower end of the mast, there is already the possibility of not only pivoting in the bearing on the side supports, but also a longitudinal movement, on the one hand if the abutment of the arrangements that counteract the vibrations is moved as well or the side supports are movably mounted and connected to the actuator, or on the other hand, if measures are taken to change the effective longitudinal extent of such an arrangement in accordance with a translational movement.
  • an actuator is provided by means of which the side supports for displacing the mast with mobility can also be pivoted through the actuator in the longitudinal direction of the vehicle and / or side struts of the mast, the arrangements counteracting the vibrations, are optionally displaceable with the side carriers.
  • This actuator is the objective version of the so-called adjusting device. It can be changed arbitrarily.
  • the movable guide in the longitudinal direction of the vehicle is addressed above, there is an advantageous embodiment in connection with side supports arranged fixed to the vehicle for the lifting frame or in connection with storage of the lifting frame in that the side supports are assigned U-profiles which are open on one side and in which Swivel and guide pins of the mast are movably and pivotably guided in the longitudinal direction.
  • vibrations counteracting arrangements attack each arm of the mast at the level of the storage.
  • This embodiment creates a holder of the mast that is displaceable in the longitudinal axis of the vehicle, this displaceable holder permitting both a forward and a retracting movement, but above all also a pivoting and under both conditions, an absorption of stress loads.
  • pivot pins protrude outwards and that the side supports are arranged on the outside.
  • the U-profiles are concavely curved downwards.
  • the pivot point radius is taken into account when determining the mast at the lower end, be it by a pivotable mounting itself or by a linkage on an actuator.
  • the embodiment described above significantly improves the subject. It is namely achieved that the mast is displaceable at a distance from its lower end, with pivoting being permitted at the same time. Depending on the arrangement of the damping arrangement, this displaceability has the advantage that the pivoting movement of the mast is dimensioned, or else the displacement as a whole.
  • an advantageous feature also lies in the fact that the pivotable mounting at the lower end of the mast can be adjusted to adjust the inclination, the pivotable mounting being resiliently held by the arrangement counteracting the vibrations.
  • an advantageous embodiment lies in a special embodiment in that the vibration-counteracting arrangement has a damping cylinder in which a spring-loaded piston is guided, the piston rod of which is guided out by the fact that this damping cylinder is pivotably articulated on a vehicle-fixed bearing by the end of the piston rod which is brought out on the other and that the cylinder is divided into two cylinder spaces by the piston.
  • the invention provides a particularly robust, but also easy-to-adjust embodiment in that the pivotally mounted mast is longitudinally movable in the region of the pivot bearing and is then in particular pivotally held at a second location, the arrangement counteracting the vibrations in the region of the bearing the special version is provided.
  • This arrangement can be arranged on both sides of both struts of an extendable mast, it being possible for corresponding cylinder spaces to be connected to one another when using a hydraulic or pneumatic pressure medium. Swiveling and shifting can take place simultaneously under the operational influences and can be damped particularly effectively in a metered manner, because the permitted evasive movement of the pivot bearing permits the unrestricted influence of the arrangement counteracting the vibrations.
  • the mast is connected to the vehicle by means of fixed pivot bearings and the arrangement counteracting vibrations is arranged at a distance from the pivot bearing.
  • This fixed arrangement of the lifting frame with the damping arrangement achieves a particularly favorable configuration of the stacking vehicle in such a way that vibrations which may occur are suppressed and / or reduced from the outset.
  • the arrangement can be designed in a special way.
  • connection by means of a fixed pivot bearing is of particular importance because, under the influence of vibrations, it is possible to adapt the mounting of the mast to its tendency to move, but without the mast itself being displaced.
  • the fixed pivot bearing is arranged above the arrangement counteracting vibrations.
  • the mast can articulate in its storage, but is dampened by the arrangement. This is particularly advantageous if the arrangement is provided at the lower end of the mast, which is mounted above this arrangement, for example at the upper end of a so-called standing mast part.
  • vibration deflections even if they are damped, can be somewhat larger from the outset than in the special configuration described above.
  • An advantageous embodiment is designed with a mast part, in particular a standing mast part, which is articulated to the vehicle at its upper end and the lower end of which is articulated to the arrangement which counteracts the vibrations.
  • the arrangement which counteracts the vibrations is expediently connected at its end remote from the mast to an abutment which is on the vehicle is arranged. This improves adaptability.
  • a spring it can be designed in different ways.
  • Disc springs, coil springs, gas pressure springs are used.
  • the spring force can be applied by means of a flexible, in particular elastic membrane, in addition to the compressibility of the medium and any spring supports. Hydraulic accumulators are included here.
  • the throttle section is arranged as a damping throttle in the damping piston.
  • the damper expediently has a constricted passage for a hydraulic pressure medium that can circulate in the damper.
  • the passage is provided as an annular gap.
  • a spring stiffness with an optimal damping setting is expediently chosen such that the damping of the system with the mast is maximum, with an optimal damping constant just sufficient damping of the system is achieved in which an oscillation movement subsided after two to three oscillations is.
  • an optimal damper setting is striven for, in which there is a maximum damping of the overall system for the critical operating point or operating state that occurs with regard to vibrations that arise at maximum load and maximum lifting height. This contains information for the design of the arrangement, which can be dimensioned or calculated from this aspect by mutually adapting the parts.
  • the arrangement counteracting the vibrations can be provided as a self-contained assembly without external influences for a fluid, in particular a largely mechanical design, which can also be used particularly advantageously with a mechanical actuator.
  • a connecting line provided with a throttle is expediently provided between the two cylinder spaces of the damping cylinder on both sides of the damping piston, and a passage or check valve can be optionally set therein Ring line arranged.
  • the cylinder spaces are connected on both piston sides via a preload valve.
  • hydraulic accumulators connected via a throttle section are arranged on each cylinder space of the damping cylinder and a passage or shut-off valve is arranged in the feed line to a hydraulic accumulator. It is understood that in this connection, throttles can also be arranged in the feed lines.
  • Figure 1 is used for explanation. It shows on the left a schematically represented stacking vehicle 1, on which a pivotable mast 2 is mounted on pivots 3, which are arranged in side supports 4 of the stacking vehicle.
  • the mast 2 is shown in the extended state.
  • it has three mast sections to be extended and a fork-shaped load carrier 5, which is shown at the upper end of the extended mast and on which a load 6 is arranged.
  • an actuator 7 engages, through which the mast 2 can be inclined in the direction of the double arrow 8.
  • the mast itself can be represented in the replacement image as a massless elastic bar 10 which has a point mass 11 at the upper end to represent the load 6.
  • This arrangement is capable of vibrating in connection with the actuating cylinder (not shown on the right in FIG. 1) and also with the parts of the lifting drive, and an arrangement 12 is assigned to it, which counteracts the vibrations.
  • FIG. 2 shows the pivotable mast 2 with the load carrier 5, with pivot 3, an actuator 7 and the arrangement 12, which is pivotally mounted on both sides between the actuator 7 and the lower end of the mast.
  • the actuator 7 is also arranged on an abutment 13 in the vehicle so as to be pivotable about a joint 14. It can be extended or extended in the direction of the double arrow 15.
  • FIG. 3 A corresponding arrangement is shown for the mast 2 in FIG. 3.
  • This mast can be moved back and forth in the direction of the double arrow 18 on a horizontal guide, for example on rollers 16, 17 and / or in corresponding rails.
  • the actuator 7 is used for this purpose.
  • the rollers 16, 17 only show the symmetrically movable support.
  • the arrangement 12 for damping vibrations occurring consists of a physical parallel arrangement with a spring 19 and a damper 20, which thus come into effect at the same time.
  • the arrangement 12 can be a self-contained unit, wherein springs can be selected and adjusted in accordance with the aspects specified above and dampers are also present in the manner specified above.
  • FIG. 4 shows a basic illustration with mutual clamping.
  • the elastic bar with the point mass 11 (FIG. 1) shown on the one hand acts on a mass-free intermediate piece 21.
  • the arrangement 12, which counteracts vibrations, is provided on the other hand. It consists of the spring 19 and the damper 20. Both parts are supported on an abutment 23 which, for example according to FIGS. 2 and 3, is the linkage 24 between the actuator 7 and the arrangement 12. It goes without saying that the arrangement 12 is also connected to the mast 2 on the other hand via a joint 25.
  • the actuator previously designated 7 is expediently designed as an actuating cylinder which can be actuated hydraulically.
  • the actuator previously designated 7 is expediently designed as an actuating cylinder which can be actuated hydraulically.
  • actuating cylinder which can be actuated hydraulically.
  • FIG. 5 a basic overall arrangement of the hydraulic system is first shown with reference to FIG. 5, but the special embodiment is also dealt with in more detail in FIG. 7.
  • the piston 27 divides the cylinder 26 into two cylinder spaces 29, 30. These cylinder spaces are connected near their ends by lines 31, 32 which are connected to a control unit 33 as a directional control valve. Between this directional valve 33, which can adjust a shut-off or an inflow in different directions in the usual way, and the actuating cylinder 26, biasing valves 34 are arranged, which ensure the maintenance of a minimum pressure when they are arranged in the return. In the case of feeding, check valves 89, 90 connected in the preload valves open. The preload pressure is set so that a damping cylinder 35 of the arrangement for damping the vibrations can be effective.
  • a piston 36 is guided in the damping cylinder 35, on which a piston rod 37 is arranged, the parts 26, 27; 28 are reproduced in the proportion.
  • the cylinder space 38 of the damping cylinder is connected to the cylinder space 29 of the actuating cylinder 26, these two cylinder spaces being penetrated by the piston rods 28, 37.
  • the line 31 includes the cylinder space 38 and continues to the preload valve 34 and from there to the directional control valve 33.
  • a spring 71 is arranged inside the damping cylinder and on both sides of the piston, as is more clearly described with reference to FIG.
  • the directional control valve has two with a tank 39 in connection standing connections 40, 41. In the former there is a motor-driven pump 42. The latter is the return line into the tank.
  • Both lines 31, 32 are connected to the tank parallel to the directional control valve 33 by means of derivatives 43, 44. Special pressure relief valves 45, 46 can also be expediently arranged in these derivatives.
  • the actuating cylinder 26 can be driven in any direction by the directional control valve 33.
  • the damping cylinder 35 is connected to the lines 31, 32.
  • the cylinder space 47 on the side of the piston 36 which faces away from the piston rod 37 is connected by a connecting line 48 to the line 32 via a throttle section 49. This throttle section represents the damper or the constricted passage, which is mentioned above.
  • an electrical solenoid valve 50 is also arranged in line 48, which is set via an electrical control unit 51 for passage - as shown - or for blocking. The latter is the case when the damping cylinder 35 is to be locked, so that the entire assembly is fixed. Such an adjustment is preferred if the stacking vehicle makes longer journeys, in particular with the lifting frame retracted.
  • the directional control valve 33 When the actuating cylinder 26 or its piston is extended for a specific setting of the mast, the directional control valve 33 is brought into the blocking position. Then the damping cylinder 35 and the throttle section 49 are connected via lines 31, 32 and the connecting line 48 to the actuating cylinder 26, so that the damping becomes effective.
  • a damping cylinder 52, 53 is connected to the lines 31, 32.
  • a row arrangement is provided from a physical point of view without being geometrically present. It also goes without saying that in a simple embodiment only one damping cylinder 52 or 53 on one of the lines 31, 32 is arranged. However, the embodiment shown with two damping cylinders is preferred.
  • a piston 54, 55 is guided in both damping cylinders. This piston is held in each case in a spring 56 which is arranged on both sides of the piston and supports this piston on the cylinder end walls.
  • the connections of the damping cylinders 52, 53 to the lines 31, 32 are designated 57, 58.
  • the electric solenoid valve 50 is arranged in the mouth of the connections 57, 58 in the damping cylinders 52, 53.
  • constricted passages 59, 60 are arranged as throttling sections or constricted bores, the constriction being designed such that it is closely related to the length in accordance with the above aspects.
  • the damper of the arrangement in which the flow energy is partly dissipated in heat It can be seen that this takes place simultaneously with the pressurization of the pistons 54, 55, so that both parts and thus also the spring 56 have a physically parallel effect.
  • the other cylinder space 63, 64 is breathably connected to the surroundings via a filter 65, 66.
  • FIG. 6 also shows the outer sealing of the piston 27 in the cylinder 26 and the piston rod 28 at the passage in the relevant cylinder end wall.
  • the piston 27 moves in accordance with the pressure pulses occurring.
  • the hydraulic fluid is displaced on one side of the piston 27 and sucked in on the other side.
  • the lines 31, 32 are shut off and the pulsating fluid movement in connection with the cylinder chambers 61, 62 occurs, the hydraulic fluid must flow through the constricted passages 59, 60 or throttle sections.
  • Kinetic energy is converted into thermal energy and vibration damping is achieved.
  • the spring 56 also acts in the parallel arrangement.
  • FIG. 7 shows in more detail the damping cylinder 35 arranged in FIG. 5 within the framework of a hydraulic system that applies to all embodiments. This is at one end through the line 31 in the area of the cylinder spaces 29 and 38, which are penetrated by the piston rods 28 and 37, with the Actuating cylinder 26 connected, the line connector being designated 67. The other end of the damping cylinder 35 is connected to the cylinder space 47 of the damping cylinder 35 by the line 32 or the connecting line 48, which contains the electric solenoid valve 50.
  • the damping cylinder 35 is divided into the two cylinder spaces 38 and 47 by a wall 68 with through openings 69, 70.
  • the piston 36 is guided in the cylinder space 38.
  • it is bilateral held in a neutral position by a spring 71 corresponding to the spring 56 in FIG. 6 and deflectable against the spring from the neutral position.
  • the throttle section 49 is arranged outside the cylinder space 47, the annular gap 72 as a throttle or annular passage in the cylinder space 47 is created in that a cylindrical body 73 is arranged over its essential part, the outer diameter of which is smaller than is the inner diameter of the damping cylinder 35.
  • the cylindrical body 73 is supported with end pieces 74, 75 and pins 76, 77 arranged on them in end wall parts, a compression spring 78 being arranged in an axial bearing, which brings about a tolerance uptake.
  • FIG. 7 also shows, in comparison to FIG. 5, a throttle section (annular gap 72) 49 in relation to a damping piston 36 with a piston rod 37.
  • a throttle section annular gap 72
  • FIG. 7 which contains more details, in particular in connection with the spring 71, than FIG. 5, is subject to a special condition such that the dimensions for the arrangement with the actuating cylinder 26 and the parts with the damping cylinder 35 must be coordinated and selected so that the area ratios of the pistons 27 and 36 with respect to the piston rods 28 and 37 are the same with respect to the cylinder spaces. This has already been pointed out above.
  • FIG. 8 shows the actuating cylinder 26 with its piston 27, the piston rod 28 and the lines 31, 32 which connect this actuating cylinder.
  • hydraulic accumulators 79, 80 are connected to lines 31, 32 with pressure valves 34 by branch lines 81, 82. Constricted passages 83, 84 are connected as throttling sections in these branch lines.
  • a membrane 85, 86 is contained, which is enclosed and insofar as compressible gas volume 87, 88 is supported.
  • FIG. 9 largely corresponds to FIG. 1.
  • the frame 2 is mounted on pins 3, which are pivot and guide pins in this case.
  • lateral guides 91 are arranged one on each side, in which the pivot and guide pins are arranged to be movable in the longitudinal direction of the stacking vehicle.
  • the guides 91 have a limited range of motion for the pivot and guide pins 3. This limited range of motion also has a length with respect to the diameter of the pivot and guide pins 3, at least in the multiple millimeter range.
  • the mast 2 is shown in the extended state according to FIG. 1.
  • the parts 5, 6, 7 correspond to those in Fig. 1, which also applies to the double arrow 8.
  • the arrangement 12 in FIGS. 9 and 10 is arranged at a distance from the lower end of the mast 2.
  • the damping arrangement 12 is provided on the mast at the height of the pivot pins 3. It can be seen that, according to FIG. 10, the arrangement 12 is pivotally mounted on an abutment 93 on the vehicle via a joint 92.
  • the actuator 7 is also arranged on an abutment 94 in the vehicle so as to be pivotable about a joint 95. It is extendable or extendable in the direction of the double arrow 7 '.
  • the actuator 7 can have a cylinder piston device with an extendable piston rod, the end of which is articulated to the mast 2.
  • Fig. 10 shows the pivotable mast 2 with the load carrier 5, with pivot and guide pin 3, the guide 91, an actuator 7 and the arrangement 12, which counteracts vibrations and which can also be referred to as an attenuator and will be described in more detail below .
  • It can be designed as an arbitrary damping element per se, ie as a special type of spring, a spring damped in a special way, a gas pressure spring or in the preferred embodiment.
  • FIG. 11 shows, using the same reference numerals, a more concrete embodiment, which is, however, also schematized. However, it shows that the mast 2 is mounted and guided in side supports 96, 97, which are fixedly arranged on a vehicle or vehicle chassis. The latter is shown by line 98 to illustrate the fixed position.
  • the lower side struts 99, 100 of the mast are guided.
  • the mast sections can be box sections that are designed from bottom to top so that the lower mast sections can accommodate the upper ones.
  • known reciprocal guides made of double-T profiles in connection with guide rollers are also possible.
  • Cylinder-piston arrangements are used for extending, optionally also with cable or chain hoists, a schematic arrangement being shown in FIG. 11 by the crossed double arrow 103.
  • This lifting arrangement acts according to a schematic representation on the cross struts 101 and 101 ', of which the latter is arranged between the lower side struts.
  • the side supports 96, 97 have guides 91 at their upper ends. These are each designed as inwardly open U-profiles with the legs 104, 105. Between these legs, the pivot and guide pins 3 engage the two arms of the mast.
  • pivot and guide pins 3 are directed outwards, which is particularly preferred if the side supports 96, 97 surround the mast 2 on both sides.
  • the guides 91 could also be arranged within the mast and then the pivot and guide pins 3 are directed inward from the side struts 99, 100.
  • the guides are provided in the manner described on the side struts 99, 100, while the pivot and guide pins are provided on the side supports 96, 97 of the mast.
  • the actuator 7 engages via a joint 106, which on the other hand is supported on the abutment 94 by means of the joint.
  • the mast 2 is pivotable in the guides 91 and in the longitudinal direction of the vehicle, i.e. practically also in the direction of action of the actuator 7.
  • the displaceability can be limited if the guides 91 are closed at their ends by locking members or walls 107, 108. It goes without saying that such locking members or walls can also be arranged at the ends of the guides which are at the rear with respect to FIG. 11, as is shown, for example, by a locking member or a wall 109 in FIG.
  • the articulation points 110, 111 are shown schematically in FIG. In the practical embodiment it is preferred that the articulation points 110, 111 are mounted essentially coaxially to the pivot and guide pins 3 on the side struts 99, 100 of the lifting frame.
  • FIG. 12 the upper end of the side beam 97 and a section, in particular the side strut 100 of the mast 2 is shown.
  • the U-shaped guide on the side support 97 and the outwardly projecting pivot and guide pin 3 can be seen on the side strut 100.
  • this carries a roller 112 at its outer end, which runs in the guide 91.
  • the roller 112 has a slightly smaller diameter than the inner distance between the legs 104, 105 of the U-shaped guide 91, so that, as shown, the roller 112 runs on the bottom of the leg 104.
  • a sliding shoe can also be arranged on the pivot and guide pin 3, which has parallel top and bottom surfaces or, in the special embodiment, spherical or concave curved surfaces.
  • FIGS. 10 and 11 correspond to FIGS. 10 and 11 with the exception that, instead of the actuator 7, the lower end of the mast 2 is articulated by means of the joint 113 on the vehicle.
  • the guides 91 are concavely curved downward in order to accommodate the arcuate movement of the pivot and guide pins around the joints 114, 115 correspond to.
  • This embodiment according to FIGS. 13 and 14 is particularly advantageous because a defined arrangement of the mast is created in the vehicle, in which vibratory movements of the mast are per se particularly cheap because the lower end is set in an adjustable angle, but at a distance, the arms or side struts of the mast are displaceable under the vibration effect with damping influence.
  • the lower end of the mast can be pivoted in the longitudinal direction by the joints 114, 115 on the vehicle in the longitudinal direction, but is otherwise fixed in such a way that the pivot and guide pins 3 are movable in the guides 91 , is understood that in a modified and also advantageous embodiment, a pivotable and fixed in the vehicle longitudinal direction storage is also included at a distance from the lower end of the mast, by joints, as shown at 114, 115.
  • the training with the guides and the pivot and guide pin 3 is provided at the lower end of the mast 2.
  • the vibration damping at the lower end of the mast results with the possibility of evasion.
  • the arrangement 12 for damping the vibrations that occur consists, for example, according to FIG. 9 of a spring 116 and a damper 117, which come into effect at the same time.
  • This is a self-contained unit.
  • the springs like the damper, are appropriately designed with an approximately linear characteristic.
  • the springs and dampers can be arranged in parallel or in one another, with individual elements being able to be provided several times.
  • the springs can be disc or coil springs, gas pressure springs or the like, with the latter being able to use elastic membranes.
  • Shock absorber-like devices can be provided as dampers, which are equipped with the means known in this context, which oppose an adjustment of a deceleration force.
  • a piston rod 118 is provided, which guides a piston 119 within a cylinder 120. This is arranged on the piston rod so that it cannot be pivoted.
  • the piston 119 is guided with a seal in the cylinder.
  • the piston rod sections guided through the end faces of the cylinder 120 are sealed and, in a special embodiment, sealed in such a way that less canting is possible.
  • the cylinder 120 is mounted on the vehicle.
  • the piston rod 118 is connected to the lifting frame via a joint 121 via an abutment 122.
  • the piston 119 is supported on both sides in the center of the cylinder 120 within a spring 123. 15, the piston is penetrated by a constricted opening 124 which acts as a damping throttle.
  • the design corresponds to the viscosity of a liquid (oil) in cylinder 120 and the forces or loads that occur. Leakage losses, for example due to worn sealing rings, are compensated for via an expansion tank 125 with an oil supply via a check valve 126.
  • a damping throttle 127 is arranged in a ring line 128 between the cylinder spaces on both sides of the piston.
  • a control valve 129 is additionally provided in the ring line as a solenoid valve, which switches the ring line to passage or blocking, the latter taking place when the mast is to be ascertained.
  • throttles 139 there are constricted passages or, in relation to FIGS. 5 and 6, throttles 139 are present.
  • FIG. 18 is also shown to explain another embodiment. It shows on the left a schematically illustrated stacking vehicle 140, on which, according to FIG. 1, a pivotable mast 2 is mounted on pivot 3.
  • FIG. 1 shows on the left a schematically illustrated stacking vehicle 140, on which, according to FIG. 1, a pivotable mast 2 is mounted on pivot 3.
  • FIG. 1 shows on the left a schematically illustrated stacking vehicle 140, on which, according to FIG. 1, a pivotable mast 2 is mounted on pivot 3.
  • FIG. 1 in which the same parts are designated with the same reference numerals.
  • the guide designated 4 is missing there.
  • the pivots 3 are arranged in side supports 141 of the stacking vehicle.
  • the mast 2 is shown in the extended state.
  • it has three mast sections to be extended and a fork-shaped load carrier 5, which is shown at the upper end of the extended mast and on which a load 6 is arranged.
  • On the right in Fig. 18 it is shown that the mast itself can be represented in the replacement image as a massless elastic bar which has a point mass 11 at the upper end to represent the load 6.
  • a massless elastic bar which has a point mass 11 at the upper end to represent the load 6.
  • This arrangement is capable of oscillating in connection with the actuating cylinder shown only formally on the right in FIGS. 1 and 18 and also with the parts of the linear actuator to which an arrangement 12 is assigned which counteracts the vibrations.
  • the mast 2 which is designed, for example, with a standing mast part 142 and two mast sections 143, 144, can be extended via a hydraulic cylinder piston device, not shown, optionally also using deflected cable or chain hoists.
  • the mast 2 is pivotally mounted on the vehicle by the pivot 3 or the joint so-called, the joint being provided with the abutment 145 on the vehicle.
  • the lower end of the standing mast part 142 is connected in an articulated manner to the arrangement 12 which counteracts vibrations and which, on the other hand, is supported in an articulated manner on an abutment 146 on the vehicle.
  • This preferred embodiment leads to particularly favorable vibration damping in the case of extended masts of so-called high stacker trucks.
  • the arrangement 12 for damping vibrations occurring consists of a physical parallel arrangement with a spring 19 and a damper 26, which thus come into effect at the same time.
  • the arrangement 12 can be a self-contained unit, wherein springs can be selected and adjusted in accordance with the aspects specified above and dampers are also present in the manner specified above.

Landscapes

  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Forklifts And Lifting Vehicles (AREA)
EP90119648A 1989-11-10 1990-10-13 Chariot élévateur avec un mât de levage disposé mobilement Expired - Lifetime EP0427001B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE3937404 1989-11-10
DE19893937404 DE3937404A1 (de) 1989-11-10 1989-11-10 Stapelfahrzeug mit einem beweglich an ihm angeordneten hubgeruest
DE9006695U 1990-06-15
DE9006695U DE9006695U1 (de) 1990-06-15 1990-06-15 Stapelfahrzeug mit einem Hubgerüst, an welchem ein Lastträger höhenbeweglich geführt ist
DE19904019075 DE4019075C2 (de) 1989-11-10 1990-06-15 Stapelfahrzeug mit einem Hubgerüst
DE4019075 1990-06-15

Publications (2)

Publication Number Publication Date
EP0427001A1 true EP0427001A1 (fr) 1991-05-15
EP0427001B1 EP0427001B1 (fr) 1996-02-07

Family

ID=27200430

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90119648A Expired - Lifetime EP0427001B1 (fr) 1989-11-10 1990-10-13 Chariot élévateur avec un mât de levage disposé mobilement

Country Status (2)

Country Link
EP (1) EP0427001B1 (fr)
DE (1) DE59010115D1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2723734A1 (fr) * 1994-08-01 1996-02-23 Murata Machinery Ltd Appareil de levage de chariots.
GB2364992A (en) * 2000-07-24 2002-02-13 Lansing Linde Ltd Lifting structure for an industrial truck
GB2379434A (en) * 2001-09-10 2003-03-12 Lansing Linde Ltd A vibration absorber for a lift truck
EP1975114A1 (fr) * 2007-03-30 2008-10-01 STILL WAGNER GmbH Compensation des oscillations sur un châssis de levage d'un chariot de manutention
CN114810883A (zh) * 2022-04-28 2022-07-29 中国舰船研究设计中心 一种双簧双侧并联支撑的推力轴承减振结构

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3321216A (en) * 1963-12-23 1967-05-23 Caterpillar Tractor Co Method and apparatus for controlling bounce in tractor-trailer combinations
DE1913526B1 (de) * 1969-03-18 1970-09-03 Eaton Yale & Towne Gmbh Hublader mit zwei mittels Federn abgestuetzten vorderen Antriebsraedern
FR2030641A5 (fr) * 1968-02-23 1970-11-13 Gates Rubber Co
US3734326A (en) * 1971-07-15 1973-05-22 Eaton Corp Variable capacity lift truck
US3949892A (en) * 1974-11-29 1976-04-13 Caterpillar Tractor Co. Cushioned mast for lift trucks
DE2948605A1 (de) * 1979-12-03 1981-06-11 Ludwig Dr.-Ing. 7500 Karlsruhe Pietzsch Federsystem
FR2504905A1 (fr) * 1981-04-30 1982-11-05 Fenwick Manutention Ste Indle Chariot de manutention comportant un dispositif de suspension entre son chassis et son ensemble elevateur
DE3201917A1 (de) * 1982-01-22 1983-08-25 Josef 4802 Halle Kozlowski Sicherheitsvorrichtung fuer hubvorrichtungen
DE8908133U1 (de) * 1989-04-19 1989-08-31 Braun, Artur, 3523 Grebenstein Vorrichtung zur Abfederung und Dämpfung einer Fahrzeugkarosserie

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3321216A (en) * 1963-12-23 1967-05-23 Caterpillar Tractor Co Method and apparatus for controlling bounce in tractor-trailer combinations
FR2030641A5 (fr) * 1968-02-23 1970-11-13 Gates Rubber Co
DE1913526B1 (de) * 1969-03-18 1970-09-03 Eaton Yale & Towne Gmbh Hublader mit zwei mittels Federn abgestuetzten vorderen Antriebsraedern
US3734326A (en) * 1971-07-15 1973-05-22 Eaton Corp Variable capacity lift truck
US3949892A (en) * 1974-11-29 1976-04-13 Caterpillar Tractor Co. Cushioned mast for lift trucks
DE2948605A1 (de) * 1979-12-03 1981-06-11 Ludwig Dr.-Ing. 7500 Karlsruhe Pietzsch Federsystem
FR2504905A1 (fr) * 1981-04-30 1982-11-05 Fenwick Manutention Ste Indle Chariot de manutention comportant un dispositif de suspension entre son chassis et son ensemble elevateur
DE3201917A1 (de) * 1982-01-22 1983-08-25 Josef 4802 Halle Kozlowski Sicherheitsvorrichtung fuer hubvorrichtungen
DE8908133U1 (de) * 1989-04-19 1989-08-31 Braun, Artur, 3523 Grebenstein Vorrichtung zur Abfederung und Dämpfung einer Fahrzeugkarosserie

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2723734A1 (fr) * 1994-08-01 1996-02-23 Murata Machinery Ltd Appareil de levage de chariots.
GB2364992A (en) * 2000-07-24 2002-02-13 Lansing Linde Ltd Lifting structure for an industrial truck
GB2364992B (en) * 2000-07-24 2004-05-05 Lansing Linde Ltd Lifting structure for an industrial truck
GB2379434A (en) * 2001-09-10 2003-03-12 Lansing Linde Ltd A vibration absorber for a lift truck
GB2379434B (en) * 2001-09-10 2004-09-22 Lansing Linde Ltd Industrial truck with a lifting frame
EP1975114A1 (fr) * 2007-03-30 2008-10-01 STILL WAGNER GmbH Compensation des oscillations sur un châssis de levage d'un chariot de manutention
CN114810883A (zh) * 2022-04-28 2022-07-29 中国舰船研究设计中心 一种双簧双侧并联支撑的推力轴承减振结构
CN114810883B (zh) * 2022-04-28 2024-04-26 中国舰船研究设计中心 一种双簧双侧并联支撑的推力轴承减振结构

Also Published As

Publication number Publication date
EP0427001B1 (fr) 1996-02-07
DE59010115D1 (de) 1996-03-21

Similar Documents

Publication Publication Date Title
EP2148014B1 (fr) Appareil de travail
DE3902743C1 (en) Active wheel or axle support
DE4115311C2 (de) Gefederte Aufhängung einer Lenkachse
DE3806709A1 (de) Federbein fuer fahrzeuge
EP0301051B1 (fr) Suspension d'essieux pour vehicules, notamment pour vehicules lourds a deux ou plusieurs essieux
DE1531146C3 (de) Hydraulischer Antrieb für einen Kranausleger mit teleskopartig verschiebbaren Auslegerstücken
DE19647300C2 (de) Vorrichtung zur höhenveränderlichen Abstützung eines Radträgers oder Achskörpers
DE4019075C2 (de) Stapelfahrzeug mit einem Hubgerüst
WO2017137180A1 (fr) Amortisseur de vibrations pourvu d'une chambre de compensation
EP0427001A1 (fr) Chariot élévateur avec un mât de levage disposé mobilement
DE3642956C2 (fr)
DE3937404C2 (fr)
DE2031098B2 (de) Abstützung des Kastens eines Schienenfahrzeuges auf einem Drehges teil
DE1135310B (de) Dynamischer Schwingungsdaempfer fuer eine Kraftfahrzeugradachse
DE19714745A1 (de) Hydraulische Schwingungsdämpfungsanordnung
DE3145377A1 (de) Gabelanordnung an einem lastaufnahmemittel fuer foerderzeuge
DE10137337A1 (de) Stampfer mit schwingungsarmem Führungbügel
DE1605060A1 (de) Verfahren und Vorrichtung um dem seitlichen Schwanken von Eisenbahnwagen entgegenzuwirken
DE3345002A1 (de) Hydropneumatischer druckzylinder
DE3934896C2 (de) Endanschlagdämpfer zur Dämpfung einer in ein Fahrzeugrad eingeleiteten Stoßenergie
EP3329142B1 (fr) Amortisseur de vibrations télescopique monotube hydraulique
DE1006219B (de) Hydropneumatischer Stossdaempfer, insbesondere fuer Fahrzeuge
DE102009060304A1 (de) Achsspielprüfeinrichtung
DE2209092C3 (de) Ausgleichsschwinge
DE9006695U1 (de) Stapelfahrzeug mit einem Hubgerüst, an welchem ein Lastträger höhenbeweglich geführt ist

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19910419

17Q First examination report despatched

Effective date: 19931222

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19960209

REF Corresponds to:

Ref document number: 59010115

Country of ref document: DE

Date of ref document: 19960321

ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19981203

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

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

Effective date: 20000801

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20081029

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20091023

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20091023

Year of fee payment: 20

Ref country code: FR

Payment date: 20091110

Year of fee payment: 20

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20101012

EUG Se: european patent has lapsed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20101012

Ref country code: IT

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

Effective date: 20091013