EP1593644B1 - Industrial truck with a piston-cylinder arrangement and an improved cylinder bearing - Google Patents

Industrial truck with a piston-cylinder arrangement and an improved cylinder bearing Download PDF

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Publication number
EP1593644B1
EP1593644B1 EP05009845.8A EP05009845A EP1593644B1 EP 1593644 B1 EP1593644 B1 EP 1593644B1 EP 05009845 A EP05009845 A EP 05009845A EP 1593644 B1 EP1593644 B1 EP 1593644B1
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EP
European Patent Office
Prior art keywords
cylinder
bearing
component
industrial truck
piston
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EP05009845.8A
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German (de)
French (fr)
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EP1593644A2 (en
EP1593644A3 (en
Inventor
Michael Schönauer
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Jungheinrich AG
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Jungheinrich AG
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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B66HOISTING; LIFTING; HAULING
    • B66FHOISTING, 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
    • B66F9/00Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06Devices 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
    • B66F9/075Constructional features or details
    • B66F9/20Means for actuating or controlling masts, platforms, or forks
    • B66F9/22Hydraulic devices or systems
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B66HOISTING; LIFTING; HAULING
    • B66FHOISTING, 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
    • B66F9/00Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06Devices 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
    • B66F9/075Constructional features or details
    • B66F9/08Masts; Guides; Chains

Definitions

  • the present invention relates to an industrial truck with a piston-cylinder arrangement, comprising a cylinder and a retractable and retractable in this piston, as a drive and / or leadership of a first component for movement relative to a second component, in particular as a drive of components a mast, wherein the piston is associated with a component assigned to it: first or second component, for transmitting power and wherein the cylinder is mounted on a cylinder bearing of the other, the cylinder associated component and coupled for transmitting power therewith.
  • piston-cylinder arrangements are used as drives and / or as a guide of an extension and a retraction movement of lifting frame relative to truck frame fixed uprights.
  • the cylinder is usually connected to at least one bearing point as rigid as possible with the component overlying him.
  • misalignment means that piston longitudinal axis and cylinder longitudinal axis are not ideally coaxial, but offset slightly in mutually orthogonal to the cylinder longitudinal axis direction offset direction to each other and / or slightly tilted about an axis of rotation orthogonal to the cylinder axis axis.
  • misalignments affect especially in far out of the cylinder extended piston, since the piston can be performed more accurately through the cylinder, the longer the piston is still in the cylinder piston line.
  • the WO 81/02290 A1 discloses a bearing point on hydraulic cylinders used to laterally adjust the position of forks of a forklift of a forklift so that different distances of the tines are possible.
  • a pivotable in two directions bearing is provided, which is designed with a convex Kalottenabêt on the cylinder and a corresponding concave counterpart on the cylinder bearing.
  • the movable spherical bearing surface extends substantially in the longitudinal direction of the cylinder.
  • the DE 1 556 601 A1 discloses a lift truck with an extendable mast, wherein the lower end of the lift cylinder is supported with a spherical cap-shaped part in a ball socket-shaped part of the mast. In this case, means are provided with which the ball cap elastic in the ball socket is pressed. The power transmission happens in the central area of the ball cap and ball socket.
  • Object of the present invention is therefore to provide an industrial truck of the type mentioned, in which a cylinder of a piston-cylinder assembly overlapping truck component is less heavily loaded.
  • the cylinder closure has a bearing configuration, which protrudes radially outward relative to the cylinder tube along the entire circumference of the cylinder closure, that a support surface also protrudes beyond the cylinder circumference and that the support surface in the retraction of the piston under a is arranged slightly different from the perpendicular to the cylinder axis angle to the bearing design.
  • the cylinder can make a compensating movement in a direction in which shape or / and position deviations from the ideal shape, such as misalignment between piston and Cylinder, to be reduced, which also makes an area the piston opening of the cylinder decreases to this exerted support torque.
  • This support moment is in fact proportional in its amount to the amount of misalignment.
  • the relative amount of shape and / or position inaccuracies is reduced by a compensatory movement, as is made possible by the cylinder bearing according to the invention.
  • the cylinder driven by the force acting on him from the extended piston support torque, move in a direction in which this exerted on him support torque is smaller, so that the truck with the movably mounted cylinder within certain limits, a self-optimizing system represents.
  • a separate control for moving the cylinder in a suitable direction is not required.
  • the piston-cylinder arrangement is preferably a hydraulic drive which is suitable for lifting and / or lowering large loads.
  • the cylinder has a closed longitudinal end and a longitudinal end with a piston opening, wherein the cylinder bearing supports the cylinder in the region of its longitudinal end with piston opening to advantageously avoid excessive cylinder deformation. Since a seal is provided on the piston opening, which seals the piston opening against the ingress of dirt into the cylinder chamber and, if necessary, against the escape of hydraulic fluid, here is a touch contact exists between the piston and cylinder, by which forces are introduced from the piston into the cylinder. These forces can less lead to a deformation of the cylinder, the closer the cylinder bearing of the piston opening.
  • the cylinder bearing is provided such that the piston opening is not located more than 20% of the total length of the cylinder away from the cylinder bearing. More preferably, the distance of the piston opening should not exceed 10% of the total length of the cylinder. Particularly high forces can be absorbed without appreciable deformation of the cylinder, if the piston opening is not located more than 5% of the total length of the cylinder away from the cylinder bearing.
  • a movement of the cylinder and the cylinder bearing relative to one another only denotes a slight local relative movement in the region of the cylinder bearing.
  • the relative movement of the cylinder and cylinder bearing at the location of the cylinder bearing should not preclude, for example, that the cylinder is mounted at a further bearing point on its associated component or on another component.
  • This additional bearing point of the cylinder can be a loose bearing point or even a rigid bearing point, so that in the latter case the local mobility of the cylinder in the range of the cylinder bearing discussed here is adjusted relative to this essentially by a deformation of the cylinder.
  • the cylinder can be provided such that it relative to the cylinder bearing in at least one orthogonal to the cylinder longitudinal axis direction of displacement, preferably in two both to each other and to Cylinder longitudinal axis direction orthogonal displacement directions, is displaceable.
  • the cylinder may be used to reduce tilting Cylinder and piston longitudinal axis relative to each other also be supported on the cylinder bearing so that it is tiltable relative to the cylinder bearing by at least one to the cylinder longitudinal axis orthogonal tilt axis, preferably two mutually orthogonal to each other and to the cylinder axis tilt axes.
  • the latter variant is preferable to the first-mentioned possibility of displaceability of the cylinder relative to the cylinder bearing, because on the one hand with slight movements, which is here a Ausretesverkippung causes a significant reduction of the forces acting on the cylinder bearing due to a previously discussed longitudinal axis offset forces on the cylinder and on the other hand, a bearing with a tiltability of the cylinder relative to the cylinder bearing can be made stiffer than a cylinder bearing with a relative to this displaceable cylinder.
  • a tiltability of the cylinder relative to the cylinder bearing if at least one of the surfaces: bearing surface and cylinder bearing surface, at least in the region of the engagement by at least one orthogonal to the cylinder longitudinal axis orthogonal axis of curvature is convexly curved.
  • the support surface and / or the cylinder bearing surface may be formed here, for example, as a cylinder jacket part surface.
  • both surfaces are convexly curved or that one of the surfaces is flat.
  • tiltability or rotatability about at least two tilt axes orthogonal to each other and to the cylinder longitudinal axis direction can be obtained by the support surface and cylinder surface being convexly curved only about an axis of curvature orthogonal to the cylinder longitudinal axis direction, but the axis of curvature of the support surface and the axis of curvature of the cylinder bearing surface are orthogonal to one another ,
  • such solutions lead to very high surface pressures at the contact point of the bearing surface and cylinder bearing surface, which is less preferred.
  • a particularly good possibility for compensating manufacturing and / or assembly errors can be obtained if at least one of the surfaces: bearing surface and cylinder bearing surface, at least in the region of the engagement engagement convexly curved about two orthogonal to each other and to the cylinder axis direction orthogonal axes of curvature is.
  • the cylinder can be tilted or rotated relative to the cylindrical bearing about any tilt axis orthogonal to the cylinder longitudinal axis direction.
  • the support surface or / and the cylinder bearing surface may be barrel-shaped at least in sections, so that different radii of curvature are assigned to different tilt axes, which is can lead to a preferential tilting axis.
  • This may be desirable if a preferred compensation movement is known, since then still a compensating tilting movement about a tilt axis orthogonal to the preferred tilting axis is possible, but a difficult tilting always allows an increase in the bearing stiffness.
  • a universal possibility of a compensatory tilting movement which can be executed under any conditions around any tilt axis orthogonal to the cylinder longitudinal axis direction, is advantageously obtained when the at least one convexly curved surface is spherical-cap-shaped.
  • the radius of the spherical cap corresponds to the distance of the curved surface from the further clamping, since then the relative movement of the cylinder and cylinder bearings can take place with only a very small deformation of the cylinder.
  • Improved guidance of the relative tilting movement of cylinder and cylinder bearing can be obtained by one of the surfaces: bearing surface and cylinder bearing surface being convexly curved at least in the region of the abutment engagement by at least one axis of curvature orthogonal to the cylinder longitudinal axis direction and the other surface: cylinder bearing surface and bearing surface, at least in the Area of the abutment engagement is concavely curved by at least one orthogonal to the cylinder longitudinal axis direction of curvature axis.
  • the cylinder bearing can be made very robust and thus durable, when the support surface and the cylinder bearing surface are curved so that they lie flat against each other.
  • this embodiment namely between the Bearing surface and cylinder bearing surface acting surface pressure very low. It is the smaller, the larger the contact surface between support surface and cylinder bearing surface.
  • the bearing surface can be provided as desired on the cylinder.
  • the support surface extends along a peripheral portion of the cylinder. A higher load capacity of the support surface while still very efficient use of the available space results when the support surface surrounds the cylinder in the circumferential direction. This also allows a uniform application of force to be supported on the cylinder bearing force in the bearing surface.
  • the cylinder may include a cylinder tube and a cylinder closure with piston opening.
  • the piston can be very easily introduced into the cylinder. Since the cylinder closure is easier and therefore more cost-effective to machine compared to the cylinder tube due to its substantially smaller size, advantageously the bearing surface can be provided as the at least one at least partially curved surface on the cylinder closure. This applies in particular if the cylinder closure is a separate component at least at the time before its connection to the cylinder tube.
  • the piston-cylinder arrangement is generally a hydraulic adjusting device, in which, depending on the desired Auskragin of the piston from the cylinder hydraulic fluid is introduced into the cylinder or discharged therefrom, is from the point of view of a simple installation of the hydraulic lines advantageous if the first component is directly or indirectly fixedly connected to a truck frame and the second component is movably mounted relative to the first component, wherein the cylinder, the first frame-fixed component and the piston is associated with the second movably mounted component.
  • the distance of the connection point for hydraulic fluid on the cylinder does not change relative to the truck frame, which on the one hand allows the use of the shortest possible hydraulic lines and on the other hand, the hydraulic lines does not walkthrough movement.
  • Even sturdy tubes can be used as hydraulic lines.
  • the first component can be a stator and the second component can be a lifting frame.
  • the first component may be a frame of an additional stroke and the second component may be a load carrier, in particular a fork carriage, movably mounted thereon.
  • a mast 10 comprising a mounted on a frame of a truck, not shown stand 12 and a relative to the stator 12 movable lifting frame 14.
  • the lifting frame 14 is in guide rails 16 and 18 of the stator 12 for movement relative to the stator 12 in the direction led the double arrow V.
  • a piston 22 of the piston-cylinder assembly 20 is fixedly connected at its free longitudinal end with a coupling point 24 of the lifting frame 14.
  • the piston 22 can exert both tensile and compressive forces on the lifting frame 14 at the coupling point 24.
  • the piston-cylinder arrangement 20 comprises a cylinder 26 with a cylinder tube 28.
  • the cylinder longitudinal axis L is parallel to the direction of movement V of the relative movement between the lifting frame 14 and stand 12.
  • the cylinder 26 is at its in Fig. 1a lower longitudinal end 26 a held on the stand 12.
  • the holder is made via a known floating bearing 30.
  • a motion damping can be provided to dampen a relative movement between the longitudinal end 26a and the movable bearing 30.
  • the cylinder 26 is mounted slightly movable relative to a cylindrical bearing 34 surrounding it.
  • the cylindrical bearing 34 comprises in the example shown a metal plate with a hole which is penetrated by the cylinder 26.
  • Fig. 1b the storage at the longitudinal end 26b, on which the piston opening 32 is provided, shown in detail.
  • a cylinder lock 36 is inserted and fixedly connected thereto, such as by screwing or by inserting and then welding.
  • a seal assembly 38 is provided which surrounds the piston 22 along its circumference and prevents dirt from entering into the interior 40 of the cylinder 26 or hydraulic fluid exits therefrom.
  • the cylinder closure 36 has a bearing formation 42, which opposite the cylinder tube 28 protrudes radially outward, and along the entire circumference of the cylinder closure 36.
  • the piston 22 and the cylinder 26 surrounding bearing formation 42 has a spherical cap, pointing to the cylinder bearing 34 bearing surface 42a.
  • This bearing surface 42a rests on a part-spherical, concave cylinder bearing surface 34a of the cylindrical bearing 34.
  • the radii of curvature of the spherical cap surface 42a and the partially spherical recess 34a are chosen to be substantially equal, so that the bearing surface 42a bears flat against the cylindrical bearing surface 34a.
  • the cylinder 26 can tilt both about a first axis X orthogonal to the cylinder longitudinal axis L and about a second axis Y orthogonal to the cylinder longitudinal axis L and the first axis X.
  • pan or tilt axes X and Y are in Fig. 1b for reasons of space at the top of the Fig. 1b shown. It will be understood, however, that the true tilting axes X and Y pass through the center of curvature of the bearing surface 42a of the bearing closure 42 of the cylinder closure 36 resting on the part-spherical concave cylinder bearing surface 34a for the same relative movement between the bearing surface 42a and cylinder bearing surface 34a.
  • the addressed components can therefore be dimensioned correspondingly smaller or, if the dimensions are the same, correspondingly have a longer service life.
  • the cylindrical bearing 34 may be formed with a convex curved cylindrical bearing surface and the cylinder 26 with a correspondingly concave bearing surface, but a concave recess on the substantially planar cylinder bearing 34 can be formed easier than a correspondingly convex cylindrical bearing surface.
  • a convexly curved bearing surface can be produced in a simple manner by turning.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Actuator (AREA)

Description

Die vorliegende Erfindung betrifft ein Flurförderzeug mit einer Kolben-Zylinder-Anordnung, umfassend einen Zylinder und einen aus diesem ausfahrbaren und in diesen einfahrbaren Kolben, als Antrieb oder/und Führung eines ersten Bauteils zur Bewegung relativ zu einem zweiten Bauteil, insbesondere als Antrieb von Bauteilen eines Hubgerüsts, wobei der Kolben mit einem ihm zugeordneten Bauteil: erstes oder zweites Bauteil, zur Kraftübertragung gekoppelt ist und wobei der Zylinder an einem Zylinderlager des jeweils anderen, dem Zylinder zugeordneten Bauteils gelagert und zur Kraftübertragung mit diesem gekoppelt ist.The present invention relates to an industrial truck with a piston-cylinder arrangement, comprising a cylinder and a retractable and retractable in this piston, as a drive and / or leadership of a first component for movement relative to a second component, in particular as a drive of components a mast, wherein the piston is associated with a component assigned to it: first or second component, for transmitting power and wherein the cylinder is mounted on a cylinder bearing of the other, the cylinder associated component and coupled for transmitting power therewith.

Derartige Flurförderzeuge sind im Stand der Technik allgemein bekannt. So sind beispielsweise Gabelstapler mit teleskopartigen Hubgerüsten bekannt, bei welchen ein Ständer an einem Rahmen des Flurförderzeugs rahmenfest gelagert ist und ein Hubrahmen relativ zum Ständer an diesem verlagerbar gelagert und geführt ist.Such trucks are well known in the art. For example, forklifts with telescopic masts are known in which a stand is mounted on a frame of the truck frame-mounted and a lifting frame is mounted and guided relative to the stator at this displaceable.

Darüber hinaus sind Flurförderzeuge bekannt, bei welchen alternativ oder zusätzlich zu den oben geschilderten Hubgerüsten weitere relativ bewegbare Bauteile vorgesehen sind, wie etwa Zusatzhübe, Last-, insbesondere Gabelträger, Seitenschübe usw. Bei all diesen genannten Vorrichtungen sind an einem Flurförderzeug ein erstes und ein zweites Bauteil relativ zueinander bewegbar angeordnet.In addition, industrial trucks are known in which alternatively or in addition to the above-described masts further relatively movable components are provided, such as additional strokes, load, especially fork carriage, side thrusts, etc. In all these devices mentioned are on a truck, a first and a second Component arranged relative to each other movable.

Vor allem, aber nicht ausschließlich, werden Kolben-Zylinder-Anordnungen als Antriebe oder/und als Führung einer Ausfahr- und einer Einfahrbewegung von Hubrahmen relativ zu flurförderzeugrahmenfesten Ständern eingesetzt. Um eine möglichst stabile, tragfähige Struktur eines Hubgerüsts am Flurförderzeug zu erhalten, ist der Zylinder in der Regel an wenigstens einer Lagerstelle möglichst starr mit dem ihn lagernden Bauteil verbunden.Above all, but not exclusively, piston-cylinder arrangements are used as drives and / or as a guide of an extension and a retraction movement of lifting frame relative to truck frame fixed uprights. In order to obtain a stable, sustainable structure of a mast on the truck, the cylinder is usually connected to at least one bearing point as rigid as possible with the component overlying him.

Durch bei Herstellung und Montage übliche Toleranzen sowie durch Verformung unter Last können Form- und Lagerfehler, wie etwa Fluchtungsfehler, an Kolben und Zylinder bzw. zwischen diesen vorhanden sein. "Fluchtungsfehler" bedeutet dabei, dass Kolbenlängsachse und Zylinderlängsachse nicht ideal koaxial sind, sondern in zur Zylinderlängsachsenrichtung orthogonaler Versatzrichtung geringfügig zueinander versetzt oder/und um eine zur Zylinderlängsachsenrichtung orthogonale Drehachse geringfügig verkippt sind. Derartige Fluchtungsfehler wirken sich vor allem bei weit aus dem Zylinder ausgefahrenem Kolben aus, da der Kolben umso genauer durch den Zylinder geführt werden kann, je länger die noch im Zylinder vorhandene Kolbenstrecke ist. Bei weit aus dem Zylinder ausgefahrenem Kolben ist die Führungslänge der noch im Zylinder verbliebenen Kolbenstrecke gering, was bei einer weit von einer Kolbenöffnung des Zylinders entfernt zu haltenden Last zu großen Abstützmomenten am Zylinder in der Nähe der Kolbenöffnung führt. Diese Abstützmomente müssen als Kräfte vom Zylinderlager aufgenommen und vom Bauteil, an welchem das Zylinderlager vorgesehen ist, abgestützt werden.Due to customary in manufacturing and assembly tolerances and deformation under load form and bearing errors, such as misalignment, on the piston and cylinder or between them may be present. In this case, "misalignment" means that piston longitudinal axis and cylinder longitudinal axis are not ideally coaxial, but offset slightly in mutually orthogonal to the cylinder longitudinal axis direction offset direction to each other and / or slightly tilted about an axis of rotation orthogonal to the cylinder axis axis. Such misalignments affect especially in far out of the cylinder extended piston, since the piston can be performed more accurately through the cylinder, the longer the piston is still in the cylinder piston line. When the piston is extended far out of the cylinder, the guide length of the piston section still remaining in the cylinder is low, which leads to large support torques on the cylinder in the vicinity of the piston opening in the case of a load to be kept far away from a piston opening of the cylinder. These Abstützmomente must be absorbed as forces from the cylinder bearing and the component on which the cylinder bearing is provided, be supported.

Die WO 81/02290 A1 offenbart eine Lagerstelle an Hydraulikzylindern, die eingesetzt wird, die dazu dienen, die Position von Gabelzinken einer Hubgabel eines Gabelstaplers seitlich zu verstellen, so dass verschiedene Abstände der Zinken möglich sind. Zur Befestigung des Zylinders an den Gabelzinken ist eine in zwei Drehrichtungen verschwenkbare Lagerstelle vorgesehen, die mit einem konvexen Kalottenabschnitt an dem Zylinder und einem entsprechenden konkaven Gegenstück am Zylinderlager ausgeführt ist. Die bewegliche Kalottenlagerfläche erstreckt sich im Wesentlichen in Längsrichtung des Zylinders.The WO 81/02290 A1 discloses a bearing point on hydraulic cylinders used to laterally adjust the position of forks of a forklift of a forklift so that different distances of the tines are possible. For fixing the cylinder to the forks a pivotable in two directions bearing is provided, which is designed with a convex Kalottenabschnitt on the cylinder and a corresponding concave counterpart on the cylinder bearing. The movable spherical bearing surface extends substantially in the longitudinal direction of the cylinder.

Die DE 1 556 601 A1 offenbart einen Hublader mit einem ausfahrbaren Hubmast, wobei das untere Ende des Hubzylinders mit einem kugelkappenförmigen Teil in einem kugelpfannenförmigen Teil des Hubmastes abgestützt ist. Dabei sind Mittel vorgesehen, mit denen die Kugelkappe elastisch in die Kugelpfanne gedrückt wird. Die Kraftübertragung geschieht dabei im Zentralbereich von Kugelkappe und Kugelpfanne.The DE 1 556 601 A1 discloses a lift truck with an extendable mast, wherein the lower end of the lift cylinder is supported with a spherical cap-shaped part in a ball socket-shaped part of the mast. In this case, means are provided with which the ball cap elastic in the ball socket is pressed. The power transmission happens in the central area of the ball cap and ball socket.

Aufgabe der vorliegenden Erfindung ist es daher, ein Flurförderzeug der eingangs genannten Art anzugeben, bei welchem ein den Zylinder einer Kolben-Zylinder-Anordnung lagerndes Flurförderzeug-Bauteil weniger stark belastet ist.Object of the present invention is therefore to provide an industrial truck of the type mentioned, in which a cylinder of a piston-cylinder assembly overlapping truck component is less heavily loaded.

Diese Aufgabe wird bei einem gattungsgemäßen Flurförderzeug dadurch gelöst, dass der Zylinderverschluss eine Lagerausbildung aufweist, welche gegenüber dem Zylinderrohr längs des gesamten Umfangs des Zylinderverschlusses nach radial außen vorsteht, dass eine Auflagerfläche ebenfalls über den Zylinderumfang hinausragt und dass die Auflagerfläche in Einfahrrichtung des Kolbens unter einem geringfügig von der Senkrechten zu der Zylinderachse abweichenden Winkel an der Lagerausbildung angeordnet ist.This object is achieved in a generic truck in that the cylinder closure has a bearing configuration, which protrudes radially outward relative to the cylinder tube along the entire circumference of the cylinder closure, that a support surface also protrudes beyond the cylinder circumference and that the support surface in the retraction of the piston under a is arranged slightly different from the perpendicular to the cylinder axis angle to the bearing design.

Ist der Zylinder derart in Anlageeingriff mit dem Zylinderlager, dass er sich relativ zu diesem bewegen kann, kann der Zylinder eine Ausgleichsbewegung in eine Richtung ausführen, in welcher Form- oder/und Lageabweichungen von der Idealform bzw. Ideallage, wie etwa Fluchtungsfehler zwischen Kolben und Zylinder, reduziert werden, wodurch auch ein im Bereich der Kolbenöffnung des Zylinders auf diesen ausgeübtes Abstützmoment abnimmt. Dieses Abstützmoment ist nämlich in seinem Betrag proportional zum Betrag von Fluchtungsfehlern. Der relative Betrag von Form- oder/und Lageungenauigkeiten wird durch eine Ausgleichsbewegung vermindert, wie sie durch die erfindungsgemäße Zylinderlagerung ermöglicht wird.If the cylinder is in abutting engagement with the cylinder bearing so that it can move relative thereto, the cylinder can make a compensating movement in a direction in which shape or / and position deviations from the ideal shape, such as misalignment between piston and Cylinder, to be reduced, which also makes an area the piston opening of the cylinder decreases to this exerted support torque. This support moment is in fact proportional in its amount to the amount of misalignment. The relative amount of shape and / or position inaccuracies is reduced by a compensatory movement, as is made possible by the cylinder bearing according to the invention.

Darüber hinaus wird sich der Zylinder, getrieben durch das auf ihn vom ausgefahrenen Kolben einwirkende Abstützmoment, in einer Richtung bewegen, in welcher dieses auf ihn ausgeübte Abstützmoment kleiner wird, so dass das Flurförderzeug mit dem beweglich gelagerten Zylinder in bestimmten Grenzen ein sich selbst optimierendes System darstellt. Eine eigene Steuerung zur Bewegung des Zylinders in einer geeigneten Richtung ist nicht erforderlich.In addition, the cylinder, driven by the force acting on him from the extended piston support torque, move in a direction in which this exerted on him support torque is smaller, so that the truck with the movably mounted cylinder within certain limits, a self-optimizing system represents. A separate control for moving the cylinder in a suitable direction is not required.

Zwar sind beweglich oder gelenkig gelagerte Zylinder, insbesondere Hydraulikzylinder, im Stand der Technik in zahlreichen Anwendungen bekannt. Gerade bei Flurförderzeugen ging die Fachwelt jedoch bisher davon aus, dass eine möglichst exakte Führung von zueinander beweglichen Bauteilen, insbesondere Bauteilen eines Hubsystems, an einem Flurförderzeug durch eine möglichst starr gelagerte Kolben-Zylinder-Anordnung angetrieben oder/und geführt sein soll. Es ist ein Verdienst des Erfinders der vorliegenden Erfindung, sich über dieses Vorurteil der einschlägigen Fachwelt hinweggesetzt zu haben.Although movable or articulated cylinder, in particular hydraulic cylinders, known in the art in numerous applications. Especially in industrial trucks, however, has hitherto assumed that as exact as possible guidance of mutually movable components, in particular components of a lifting system to be driven on a truck by a rigidly mounted piston-cylinder arrangement and / or should be guided. It is a merit of the inventor of the present invention to have overruled this prejudice of the relevant art.

Bei der Kolben-Zylinder-Anordnung handelt es sich bevorzugt um einen hydraulischen Antrieb, welcher zum Heben oder/und Senken großer Lasten geeignet ist. Bei derartigen Kolben-Zylinder-Anordnungen weist der Zylinder ein geschlossenes Längsende und ein Längsende mit einer Kolbenöffnung auf, wobei das Zylinderlager zur vorteilhaften Vermeidung einer übermäßigen Zylinderverformung den Zylinder im Bereich seines Längsendes mit Kolbenöffnung lagert. Da an der Kolbenöffnung eine Dichtung vorgesehen ist, welche die Kolbenöffnung gegen Eintritt von Schmutz in den Zylinderraum sowie ggf. gegen Austritt von Hydraulikflüssigkeit abdichtet, ist hier ein Berührkontakt zwischen Kolben und Zylinder vorhanden, durch welchen Kräfte vom Kolben in den Zylinder eingeleitet werden. Diese Kräfte können umso weniger zu einer Verformung des Zylinders führen, je näher das Zylinderlager der Kolbenöffnung ist. Vorzugsweise ist das Zylinderlager derart vorgesehen, dass die Kolbenöffnung nicht weiter als 20% der Gesamtlänge des Zylinders vom Zylinderlager entfernt angeordnet ist. Noch vorteilhafter sollte die Entfernung der Kolbenöffnung 10% der Gesamtlänge des Zylinders nicht übersteigen. Besonders hohe Kräfte können ohne nennenswerte Verformung des Zylinders aufgenommen werden, wenn die Kolbenöffnung nicht weiter als 5% der Gesamtlänge des Zylinders vom Zylinderlager entfernt angeordnet ist.The piston-cylinder arrangement is preferably a hydraulic drive which is suitable for lifting and / or lowering large loads. In such piston-cylinder arrangements, the cylinder has a closed longitudinal end and a longitudinal end with a piston opening, wherein the cylinder bearing supports the cylinder in the region of its longitudinal end with piston opening to advantageously avoid excessive cylinder deformation. Since a seal is provided on the piston opening, which seals the piston opening against the ingress of dirt into the cylinder chamber and, if necessary, against the escape of hydraulic fluid, here is a touch contact exists between the piston and cylinder, by which forces are introduced from the piston into the cylinder. These forces can less lead to a deformation of the cylinder, the closer the cylinder bearing of the piston opening. Preferably, the cylinder bearing is provided such that the piston opening is not located more than 20% of the total length of the cylinder away from the cylinder bearing. More preferably, the distance of the piston opening should not exceed 10% of the total length of the cylinder. Particularly high forces can be absorbed without appreciable deformation of the cylinder, if the piston opening is not located more than 5% of the total length of the cylinder away from the cylinder bearing.

Nachzutragen ist, dass eine Bewegung von Zylinder und Zylinderlager relativ zueinander lediglich eine geringfügige lokale Relativbewegung im Bereich des Zylinderlagers bezeichnet. Die Relativbewegbarkeit von Zylinder und Zylinderlager an der Stelle der Zylinderlagerung soll beispielsweise nicht ausschließen, dass der Zylinder an einer weiteren Lagerstelle an dem ihm zugeordneten Bauteil oder an einem sonstigen Bauteil gelagert ist. Diese weitere Lagerstelle des Zylinders kann eine Loslagerstelle oder sogar eine starre Lagerstelle sein, so dass sich im letztgenannten Fall die lokale Bewegbarkeit des Zylinders im Bereich des hier diskutierten Zylinderlagers relativ zu diesem im Wesentlichen durch eine Verformung des Zylinders einstellt.It should be added that a movement of the cylinder and the cylinder bearing relative to one another only denotes a slight local relative movement in the region of the cylinder bearing. The relative movement of the cylinder and cylinder bearing at the location of the cylinder bearing should not preclude, for example, that the cylinder is mounted at a further bearing point on its associated component or on another component. This additional bearing point of the cylinder can be a loose bearing point or even a rigid bearing point, so that in the latter case the local mobility of the cylinder in the range of the cylinder bearing discussed here is adjusted relative to this essentially by a deformation of the cylinder.

Damit der Zylinder einen Versatz von Zylinderlängsachse und hierzu im Wesentlichen paralleler Kolbenlängsachse durch Bewegung relativ zu dem Zylinderlager reduzieren kann, kann der Zylinder derart vorgesehen sein, dass er relativ zum Zylinderlager in wenigstens einer zur Zylinderlängsachsenrichtung orthogonalen Verlagerungsrichtung, vorzugsweise in zwei sowohl zueinander als auch zur Zylinderlängsachsenrichtung orthogonalen Verlagerungsrichtungen, verschiebbar ist.In order that the cylinder can reduce an offset of the cylinder longitudinal axis and this substantially parallel piston longitudinal axis by movement relative to the cylinder bearing, the cylinder can be provided such that it relative to the cylinder bearing in at least one orthogonal to the cylinder longitudinal axis direction of displacement, preferably in two both to each other and to Cylinder longitudinal axis direction orthogonal displacement directions, is displaceable.

Alternativ oder zusätzlich kann der Zylinder zur Verminderung von Verkippungen von Zylinder- und Kolbenlängsachse relativ zueinander auch derart am Zylinderlager gelagert sein, dass er relativ zum Zylinderlager um wenigstens eine zur Zylinderlängsachsenrichtung orthogonale Kippachse, vorzugsweise um zwei sowohl zueinander als auch zur Zylinderlängsachsenrichtung orthogonale Kippachsen, kippbar ist.Alternatively or additionally, the cylinder may be used to reduce tilting Cylinder and piston longitudinal axis relative to each other also be supported on the cylinder bearing so that it is tiltable relative to the cylinder bearing by at least one to the cylinder longitudinal axis orthogonal tilt axis, preferably two mutually orthogonal to each other and to the cylinder axis tilt axes.

Letztere Variante ist gegenüber der erstgenannten Möglichkeit einer Verschiebbarkeit des Zylinders relativ zum Zylinderlager zu bevorzugen, da einerseits bei geringfügigen Bewegungen, um die es hier geht, eine Ausgleichsverkippung einen merklichen Abbau auch der auf das Zylinderlager aufgrund eines zuvor diskutierten Längsachsenversatzes auf den Zylinder einwirkenden Kräfte bewirkt und andererseits ein Lager mit einer Verkippbarkeit des Zylinders relativ zum Zylinderlager steifer ausgebildet werden kann als ein Zylinderlager mit einem relativ zu diesem verschiebbaren Zylinder.The latter variant is preferable to the first-mentioned possibility of displaceability of the cylinder relative to the cylinder bearing, because on the one hand with slight movements, which is here a Ausgleichsverkippung causes a significant reduction of the forces acting on the cylinder bearing due to a previously discussed longitudinal axis offset forces on the cylinder and on the other hand, a bearing with a tiltability of the cylinder relative to the cylinder bearing can be made stiffer than a cylinder bearing with a relative to this displaceable cylinder.

Es ist darüber hinaus leicht einzusehen, dass eine Verlagerbarkeit, sei es nun Verschiebbarkeit oder Verkippbarkeit in zwei zueinander orthogonale Verlagerungsrichtungen bzw. um zwei zueinander orthogonale Kippachsen eine wesentlich größere Möglichkeit der Fehlerkorrektur bietet als eine Verlagerbarkeit mit lediglich einer zur Zylinderlängsachsenrichtung orthogonalen Verlagerungsrichtung bzw. einer zur Zylinderlängsachsenrichtung orthogonalen Kippachse. Ist jedoch, beispielsweise aufgrund einer stets gleichen Krafteinwirkung, eine maßgeblich benötigte Ausgleichsbewegungsrichtung bekannt, kann eine Verlagerbarkeit in lediglich einer Verlagerungsrichtung bzw. um lediglich eine Kippachse vorteilhaft sein, da dieses Lager steifer als ein Lager mit zweiachsiger Verlagerungsmöglichkeit ausgebildet werden kann.It is also easy to see that a displaceability, whether it is now displaceability or tiltability in two mutually orthogonal displacement directions or two mutually orthogonal tilt axes a much greater possibility of error correction offers as a displaceability with only one to the cylinder longitudinal axis orthogonal direction of displacement or one to Cylinder longitudinal axis direction orthogonal tilt axis. However, if, for example due to always the same force, a significantly required compensation movement direction known, a displacement in only one direction of displacement or only a tilting axis may be advantageous because this camp can be made stiffer than a camp with biaxial displacement possibility.

Mit konstruktiv einfachen und somit kostengünstigen Mitteln kann eine Bewegbarkeit von Zylinder und Zylinderlager relativ zueinander dadurch erhalten werden, dass der Zylinder eine Lagerausbildung mit einer Auflagerfläche aufweist, welche in Anlageeingriff mit einer Zylinderlagerfläche des Zylinderlagers ist.With structurally simple and thus cost-effective means a mobility of cylinder and cylinder bearings relative to each other can be obtained that the cylinder has a bearing design with a bearing surface, which in abutting engagement with a cylinder bearing surface of the cylinder bearing is.

Dabei kann weiter mit einfachen Mitteln eine Kippbarkeit des Zylinders relativ zum Zylinderlager erhalten werden, wenn wenigstens eine der Flächen: Auflagerfläche und Zylinderlagerfläche, zumindest im Bereich des Anlageeingriffs um wenigstens eine zur Zylinderlängsachsenrichtung orthogonale Krümmungsachse konvex gekrümmt ist. Die Auflagerfläche oder/und die Zylinderlagerfläche können hier beispielsweise als Zylindermantelteilfläche ausgebildet sein.It can further be obtained by simple means a tiltability of the cylinder relative to the cylinder bearing, if at least one of the surfaces: bearing surface and cylinder bearing surface, at least in the region of the engagement by at least one orthogonal to the cylinder longitudinal axis orthogonal axis of curvature is convexly curved. The support surface and / or the cylinder bearing surface may be formed here, for example, as a cylinder jacket part surface.

Grundsätzlich ist dabei möglich, dass beide Flächen konvex gekrümmt sind oder dass eine der Flächen eben ist. Weiterhin kann eine Verkippbarkeit bzw. Verdrehbarkeit um wenigstens zwei zueinander und zur Zylinderlängsachsenrichtung orthogonale Kippachsen dadurch erhalten werden, dass Auflagerfläche und Zylinderfläche jeweils nur um eine zur Zylinderlängsachsenrichtung orthogonale Krümmungsachse konvex gekrümmt sind, dass jedoch die Krümmungsachse der Auflagerfläche und die Krümmungsachse der Zylinderlagerfläche orthogonal zueinander liegen. Derartige Lösungen führen jedoch zu sehr hohen Flächenpressungen an der Berührstelle von Auflagerfläche und Zylinderlagerfläche, was weniger bevorzugt ist.Basically, it is possible that both surfaces are convexly curved or that one of the surfaces is flat. Furthermore, tiltability or rotatability about at least two tilt axes orthogonal to each other and to the cylinder longitudinal axis direction can be obtained by the support surface and cylinder surface being convexly curved only about an axis of curvature orthogonal to the cylinder longitudinal axis direction, but the axis of curvature of the support surface and the axis of curvature of the cylinder bearing surface are orthogonal to one another , However, such solutions lead to very high surface pressures at the contact point of the bearing surface and cylinder bearing surface, which is less preferred.

Wie oben bereits ausgesagt wurde, kann eine besonders gute Möglichkeit zum Ausgleich von Fertigungs- oder/und Montagefehlern erhalten werden, wenn wenigstens eine der Flächen: Auflagerfläche und Zylinderlagerfläche, zumindest im Bereich des Anlageeingriffs um zwei sowohl zueinander als auch zur Zylinderlängsachsenrichtung orthogonalen Krümmungsachsen konvex gekrümmt ist. In diesem Falle kann der Zylinder relativ zum Zylinderlager um jede beliebige zur Zylinderlängsachsenrichtung orthogonale Kippachse gekippt bzw. verdreht werden.As already stated above, a particularly good possibility for compensating manufacturing and / or assembly errors can be obtained if at least one of the surfaces: bearing surface and cylinder bearing surface, at least in the region of the engagement engagement convexly curved about two orthogonal to each other and to the cylinder axis direction orthogonal axes of curvature is. In this case, the cylinder can be tilted or rotated relative to the cylindrical bearing about any tilt axis orthogonal to the cylinder longitudinal axis direction.

Beispielsweise kann die Auflagerfläche oder/und die Zylinderlagerfläche zumindest abschnittsweise tonnenförmig ausgeführt sein, so dass unterschiedlichen Kippachsen unterschiedliche Krümmungsradien zugeordnet sind, was zu einer Vorzugskippachse führen kann. Dies kann gewünscht sein, wenn eine Vorzugsausgleichsbewegung bekannt ist, da dann zwar immer noch eine Ausgleichskippbewegung um eine zur bevorzugten Kippachse orthogonale Kippachse möglich ist, jedoch eine erschwerte Kippbarkeit stets eine Erhöhung der Lagersteifigkeit gestattet.For example, the support surface or / and the cylinder bearing surface may be barrel-shaped at least in sections, so that different radii of curvature are assigned to different tilt axes, which is can lead to a preferential tilting axis. This may be desirable if a preferred compensation movement is known, since then still a compensating tilting movement about a tilt axis orthogonal to the preferred tilting axis is possible, but a difficult tilting always allows an increase in the bearing stiffness.

In vielen Fällen werden sich keine Vorzugsausgleichsbewegungen ermitteln lassen, da Fertigungs- oder/und Montagefehler oft nicht systematisch sind, sondern zufällig auftreten. Eine universelle Möglichkeit einer Ausgleichskippbewegung, welche um jede beliebige zur Zylinderlängsachsenrichtung orthogonale Kippachse unter gleichen Bedingungen ausführbar ist, erhält man vorteilhaft dann, wenn die wenigstens eine konvex gekrümmte Fläche kugelkalottenförmig ist.In many cases, no preferential compensation movements will be detectable because manufacturing and / or assembly errors are often not systematic but occur by chance. A universal possibility of a compensatory tilting movement, which can be executed under any conditions around any tilt axis orthogonal to the cylinder longitudinal axis direction, is advantageously obtained when the at least one convexly curved surface is spherical-cap-shaped.

Sollte der Zylinder noch an einer weiteren Lagerstelle eingespannt sein, so ist es vorteilhaft, wenn der Radius der Kugelkalotte dem Abstand der gekrümmten Fläche von der weiteren Einspannung entspricht, da dann die Relativbewegung von Zylinder und Zylinderlager mit nur sehr geringer Verformung des Zylinders erfolgen kann.If the cylinder still be clamped at a further bearing point, it is advantageous if the radius of the spherical cap corresponds to the distance of the curved surface from the further clamping, since then the relative movement of the cylinder and cylinder bearings can take place with only a very small deformation of the cylinder.

Eine verbesserte Führung der Relativkippbewegung von Zylinder und Zylinderlager kann dadurch erhalten werden, dass eine der Flächen: Auflagerfläche und Zylinderlagerfläche, zumindest im Bereich des Anlageeingriffs um wenigstens eine zur Zylinderlängsachsenrichtung orthogonale Krümmungsachse konvex gekrümmt ist und die jeweils andere Fläche: Zylinderlagertläche und Auflagerfläche, zumindest im Bereich des Anlageeingriffs um wenigstens eine zur Zylinderlängsachsenrichtung orthogonale Krümmungsachse konkav gekrümmt ist.Improved guidance of the relative tilting movement of cylinder and cylinder bearing can be obtained by one of the surfaces: bearing surface and cylinder bearing surface being convexly curved at least in the region of the abutment engagement by at least one axis of curvature orthogonal to the cylinder longitudinal axis direction and the other surface: cylinder bearing surface and bearing surface, at least in the Area of the abutment engagement is concavely curved by at least one orthogonal to the cylinder longitudinal axis direction of curvature axis.

Bei der oben genannten Weiterbildung der vorliegenden Erfindung kann die Zylinderlagerung sehr robust und damit langlebig gestaltet werden, wenn die Auflagerfläche und die Zylinderlagerfläche derart gekrümmt sind, dass sie flächig aneinander anliegen. Bei dieser Ausgestaltung ist nämlich die zwischen Auflagerfläche und Zylinderlagerfläche wirkende Flächenpressung sehr gering. Sie ist umso geringer, je größer die Berührfläche zwischen Auflagerfläche und Zylinderlagerfläche ist.In the above-mentioned embodiment of the present invention, the cylinder bearing can be made very robust and thus durable, when the support surface and the cylinder bearing surface are curved so that they lie flat against each other. In this embodiment, namely between the Bearing surface and cylinder bearing surface acting surface pressure very low. It is the smaller, the larger the contact surface between support surface and cylinder bearing surface.

Grundsätzlich kann die Auflagerfläche beliebig am Zylinder vorgesehen sein. Bei einer Weiterbildung der vorliegenden Erfindung, welche sehr wenig Bauraum beansprucht, erstreckt sich die Auflagerfläche längs eines Umfangsabschnitts des Zylinders. Eine höhere Tragfähigkeit der Auflagerfläche bei immer noch sehr effizienter Ausnutzung des vorhandenen Bauraums ergibt sich, wenn die Auflagerfläche den Zylinder in Umfangsrichtung umgibt. Dies gestattet außerdem eine gleichmäßige Krafteinleitung einer am Zylinderlager abzustützenden Kraft in die Auflagerfläche.In principle, the bearing surface can be provided as desired on the cylinder. In a development of the present invention, which requires very little space, the support surface extends along a peripheral portion of the cylinder. A higher load capacity of the support surface while still very efficient use of the available space results when the support surface surrounds the cylinder in the circumferential direction. This also allows a uniform application of force to be supported on the cylinder bearing force in the bearing surface.

Zur Erleichterung der Montage der Kolben-Zylinder-Anordnung kann der Zylinder ein Zylinderrohr und einen Zylinderverschluss mit Kolbenöffnung umfassen. In diesem Falle kann der Kolben sehr leicht in den Zylinder eingebracht werden. Da der Zylinderverschluss aufgrund seiner wesentlich geringeren Größe gegenüber dem Zylinderrohr einfacher und damit kostengünstiger zu bearbeiten ist, kann vorteilhafterweise die Auflagerfläche als die wenigstens eine zumindest abschnittsweise gekrümmte Fläche am Zylinderverschluss vorgesehen sein. Dies gilt insbesondere dann, wenn der Zylinderverschluss zumindest zum Zeitpunkt vor seiner Verbindung mit dem Zylinderrohr ein gesondertes Bauteil ist.To facilitate assembly of the piston-cylinder assembly, the cylinder may include a cylinder tube and a cylinder closure with piston opening. In this case, the piston can be very easily introduced into the cylinder. Since the cylinder closure is easier and therefore more cost-effective to machine compared to the cylinder tube due to its substantially smaller size, advantageously the bearing surface can be provided as the at least one at least partially curved surface on the cylinder closure. This applies in particular if the cylinder closure is a separate component at least at the time before its connection to the cylinder tube.

Da es sich bei der Kolben-Zylinder-Anordnung in der Regel um eine hydraulische Stelleinrichtung handelt, bei welcher je nach gewünschter Auskraglänge des Kolbens aus dem Zylinder Hydraulikflüssigkeit in den Zylinder eingeführt oder aus diesem abgeführt wird, ist unter dem Gesichtspunkt einer einfachen Installation der Hydraulikleitungen vorteilhaft, wenn das erste Bauteil mittelbar oder unmittelbar fest mit einem Flurförderzeugrahmen verbunden ist und das zweite Bauteil relativ zum ersten Bauteil beweglich gelagert ist, wobei dem Zylinder das erste rahmenfeste Bauteil und dem Kolben das zweite beweglich gelagerte Bauteil zugeordnet ist. Ist nämlich der Zylinder mit dem rahmenfesten Bauteil verbunden, ändert sich der Abstand der Anschlussstelle für Hydraulikflüssigkeit am Zylinder relativ zum Flurförderzeugrahmen nicht, was einerseits die Verwendung möglichst kurzer Hydraulikleitungen ermöglicht und andererseits die Hydraulikleitungen nicht durch Bewegung walkt. Es können sogar stabile Rohre als Hydraulikleitungen verwendet werden.Since the piston-cylinder arrangement is generally a hydraulic adjusting device, in which, depending on the desired Auskraglänge of the piston from the cylinder hydraulic fluid is introduced into the cylinder or discharged therefrom, is from the point of view of a simple installation of the hydraulic lines advantageous if the first component is directly or indirectly fixedly connected to a truck frame and the second component is movably mounted relative to the first component, wherein the cylinder, the first frame-fixed component and the piston is associated with the second movably mounted component. Is namely the cylinder connected to the frame-fixed component, the distance of the connection point for hydraulic fluid on the cylinder does not change relative to the truck frame, which on the one hand allows the use of the shortest possible hydraulic lines and on the other hand, the hydraulic lines does not walkthrough movement. Even sturdy tubes can be used as hydraulic lines.

Wie eingangs bereits beispielhaft angeführt wurde, kann das erste Bauteil ein Ständer und das zweite Bauteil ein Hubrahmen sein. Alternativ oder zusätzlich kann weiterhin das erste Bauteil ein Gestell eines Zusatzhubs und das zweite Bauteil ein daran beweglich gelagerter Lastträger, insbesondere Gabelträger, sein.As already mentioned by way of example, the first component can be a stator and the second component can be a lifting frame. Alternatively or additionally, furthermore, the first component may be a frame of an additional stroke and the second component may be a load carrier, in particular a fork carriage, movably mounted thereon.

Die vorliegende Erfindung wird im Folgenden anhand der beiliegenden Zeichnungen näher erläutert.

Fig. 1a
zeigt beispielhaft einen Ständer und einen relativ zu diesem beweglichen Hubrahmen eines Flurförderzeugs, wie etwa eines Staplers,
Fig. 1 b
zeigt die Zylinderlagerung von Fig. 1a im Detail im Längsschnitt.
The present invention will be explained in more detail below with reference to the accompanying drawings.
Fig. 1a
shows by way of example a stand and a relative to this movable lifting frame of an industrial truck, such as a truck,
Fig. 1 b
shows the cylinder bearing of Fig. 1a in detail in longitudinal section.

In Fig. 1a ist ein Hubgerüst 10 dargestellt, umfassend einen an einem Rahmen eines nicht dargestellten Flurförderzeugs befestigten Ständer 12 und einen an diesem relativ zum Ständer 12 beweglichen Hubrahmen 14. Der Hubrahmen 14 ist in Führungsschienen 16 und 18 des Ständers 12 zur Bewegung relativ zum Ständer 12 in Richtung des Doppelpfeils V geführt.In Fig. 1a a mast 10 is shown, comprising a mounted on a frame of a truck, not shown stand 12 and a relative to the stator 12 movable lifting frame 14. The lifting frame 14 is in guide rails 16 and 18 of the stator 12 for movement relative to the stator 12 in the direction led the double arrow V.

Als Bewegungsantrieb dienen zwei im Wesentlichen gleich aufgebaute und gleich gelagerte hydraulische Kolben-Zylinder-Anordnungen, von welchen aus Gründen der Übersichtlichkeit lediglich die rechte Kolben-Zylinder-Anordnung 20 dargestellt ist. Die im Folgenden gegebene Beschreibung der rechten Kolben-Zylinder-Anordnung 20 trifft ebenso auf die nicht dargestellte linke Kolben-Zylinder-Anordnung zu.As movement drive serve two substantially identically constructed and equally stored hydraulic piston-cylinder assemblies, of which for reasons of clarity, only the right piston-cylinder assembly 20 is shown. The description given below of the right piston-cylinder arrangement 20 also applies to the not shown left piston-cylinder arrangement too.

Ein Kolben 22 der Kolben-Zylinder-Anordnung 20 ist an seinem freien Längsende fest mit einem Kopplungspunkt 24 des Hubrahmens 14 verbunden. Der Kolben 22 kann am Kopplungspunkt 24 sowohl Zug- als auch Druckkräfte auf den Hubrahmen 14 ausüben.A piston 22 of the piston-cylinder assembly 20 is fixedly connected at its free longitudinal end with a coupling point 24 of the lifting frame 14. The piston 22 can exert both tensile and compressive forces on the lifting frame 14 at the coupling point 24.

Weiterhin umfasst die Kolben-Zylinder-Anordnung 20 einen Zylinder 26 mit einem Zylinderrohr 28. Die Zylinderlängsachse L ist parallel zur Bewegungsrichtung V der Relativbewegung zwischen Hubrahmen 14 und Ständer 12. In dem dargestellten Ausführungsbeispiel ist der Zylinder 26 an seinem in Fig. 1a unteren Längsende 26a am Ständer 12 gehalten. Die Halterung erfolgt über ein an sich bekanntes Loslager 30. Dort kann eine Bewegungsdämpfung vorgesehen sein, um eine Relativbewegung zwischen dem Längsende 26a und dem Loslager 30 zu dämpfen. An seinem entgegengesetzten Längsende 26b, welches eine Kolbenöffnung 32 aufweist, ist der Zylinder 26 relativ zu einem ihn umgebenden Zylinderlager 34 geringfügig beweglich gelagert. Das Zylinderlager 34 umfasst im gezeigten Beispiel eine Metallplatte mit einem Loch, welches vom Zylinder 26 durchsetzt ist.Furthermore, the piston-cylinder arrangement 20 comprises a cylinder 26 with a cylinder tube 28. The cylinder longitudinal axis L is parallel to the direction of movement V of the relative movement between the lifting frame 14 and stand 12. In the illustrated embodiment, the cylinder 26 is at its in Fig. 1a lower longitudinal end 26 a held on the stand 12. The holder is made via a known floating bearing 30. There, a motion damping can be provided to dampen a relative movement between the longitudinal end 26a and the movable bearing 30. At its opposite longitudinal end 26b, which has a piston opening 32, the cylinder 26 is mounted slightly movable relative to a cylindrical bearing 34 surrounding it. The cylindrical bearing 34 comprises in the example shown a metal plate with a hole which is penetrated by the cylinder 26.

In Fig. 1b ist die Lagerung am Längsende 26b, an welchem die Kolbenöffnung 32 vorgesehen ist, im Detail dargestellt.In Fig. 1b the storage at the longitudinal end 26b, on which the piston opening 32 is provided, shown in detail.

In das Zylinderrohr 28 ist ein Zylinderverschluss 36 eingesetzt und mit diesem fest verbunden, etwa durch Einschrauben oder durch Einstecken und anschließendes Verschweißen.In the cylinder tube 28, a cylinder lock 36 is inserted and fixedly connected thereto, such as by screwing or by inserting and then welding.

In dem Zylinderverschluss 36 ist eine Dichtungsanordnung 38 vorgesehen, welche den Kolben 22 längs seines Umfangs umgibt und verhindert, dass Schmutz in den Innenraum 40 des Zylinders 26 eindringt oder Hydraulikflüssigkeit aus diesem austritt.In the cylinder closure 36, a seal assembly 38 is provided which surrounds the piston 22 along its circumference and prevents dirt from entering into the interior 40 of the cylinder 26 or hydraulic fluid exits therefrom.

Der Zylinderverschluss 36 weist eine Lagerausbildung 42 auf, welche gegenüber dem Zylinderrohr 28 nach radial außen vorsteht, und zwar längs des gesamten Umfangs des Zylinderverschlusses 36. Die den Kolben 22 und den Zylinder 26 umgebende Lagerausbildung 42 weist eine kugelkalottenförmige, zum Zylinderlager 34 hinweisende Auflagerfläche 42a auf. Diese Auflagerfläche 42a liegt auf einer teilsphärischen, konkaven Zylinderlagerfläche 34a des Zylinderlagers 34 auf. Dabei sind die Krümmungsradien der Kugelkalottenfläche 42a und der teilsphärischen Ausnehmung 34a im Wesentlichen gleich gewählt, so dass die Auflagerfläche 42a flächig an der Zylinderlagerfläche 34a anliegt. Somit kann der Zylinder 26 im Bereich der Berührstelle von Auflagerfläche 42a und Zylinderlagerfläche 34a sowohl um eine erste zur Zylinderlängsachse L orthogonale Achse X als auch um eine zur Zylinderlängsachse L und zur ersten Achse X orthogonale zweite Achse Y kippen.The cylinder closure 36 has a bearing formation 42, which opposite the cylinder tube 28 protrudes radially outward, and along the entire circumference of the cylinder closure 36. The piston 22 and the cylinder 26 surrounding bearing formation 42 has a spherical cap, pointing to the cylinder bearing 34 bearing surface 42a. This bearing surface 42a rests on a part-spherical, concave cylinder bearing surface 34a of the cylindrical bearing 34. In this case, the radii of curvature of the spherical cap surface 42a and the partially spherical recess 34a are chosen to be substantially equal, so that the bearing surface 42a bears flat against the cylindrical bearing surface 34a. Thus, in the region of the contact point of the bearing surface 42a and cylinder bearing surface 34a, the cylinder 26 can tilt both about a first axis X orthogonal to the cylinder longitudinal axis L and about a second axis Y orthogonal to the cylinder longitudinal axis L and the first axis X.

Die Schwenk- oder Kippachsen X und Y sind in Fig. 1b aus Platzgründen am oberen Ende der Fig. 1b dargestellt. Es wird jedoch verstanden werden, dass die wahren Kippachsen X und Y bei gleicher Relativbewegung zwischen Auflagerfläche 42a und Zylinderlagerfläche 34a durch den Krümmungskreismittelpunkt der auf der teilsphärischen konkaven Zylinderlagerfläche 34a aufliegenden Auflagerfläche 42a der Lagerausbildung 42 des Zylinderverschlusses 36 hindurchgehen.The pan or tilt axes X and Y are in Fig. 1b for reasons of space at the top of the Fig. 1b shown. It will be understood, however, that the true tilting axes X and Y pass through the center of curvature of the bearing surface 42a of the bearing closure 42 of the cylinder closure 36 resting on the part-spherical concave cylinder bearing surface 34a for the same relative movement between the bearing surface 42a and cylinder bearing surface 34a.

Mit der beschriebenen Lagerung des Zylinders nahe der Kugelöffnung 32 ist eine geringfügige Verdrehung des Längsendes 26b relativ zum Zylinderlager 34 möglich, wodurch Fertigungs- oder/und Montageungenauigkeiten der Kolben-Zylinder-Anordnung 10 zumindest ein Stück weit ausgeglichen und somit verringert werden können. In der Folge kann somit ein vom Kolben 22 auf den Zylinder 26 aufgrund derartiger Ungenauigkeiten ausgeübtes Drehmoment, welches vor allem bei weit aus dem Zylinder 26 ausgefahrenem Kolben 22 groß zu werden droht, verringert werden, was zu einer geringeren Belastung sowohl des Zylinders 26 als auch des Kolbens 22 als auch des Zylinderlagers 34 und damit des Ständers 12 führt.With the described storage of the cylinder near the ball opening 32, a slight rotation of the longitudinal end 26b relative to the cylinder bearing 34 is possible, whereby manufacturing and / or assembly inaccuracies of the piston-cylinder assembly 10 can be at least partially compensated and thus reduced. As a result, therefore, a torque exerted by the piston 22 on the cylinder 26 due to such inaccuracies, which threatens to become large, especially when the piston 22 is extended far out of the cylinder 26, can be reduced, resulting in less stress on both the cylinder 26 and of the piston 22 and the cylindrical bearing 34 and thus of the stator 12 leads.

Zum einen können somit die angesprochenen Bauteile entsprechend schwächer dimensioniert werden oder haben bei gleicher Dimensionierung entsprechend eine längere Standzeit.On the one hand, the addressed components can therefore be dimensioned correspondingly smaller or, if the dimensions are the same, correspondingly have a longer service life.

Alternativ kann auch das Zylinderlager 34 mit einer konvex gekrümmten Zylinderlagerfläche und der Zylinder 26 mit einer entsprechend konkav gekrümmten Auflagerfläche ausgebildet sein, jedoch lässt sich eine konkave Ausnehmung an dem im Wesentlichen ebenen Zylinderlager 34 leichter ausbilden als eine entsprechend konvex gekrümmte Zylinderlagerfläche. Am Zylinder 26 oder besonders vorteilhaft am Zylinderverschluss 36 kann eine konvex gekrümmte Auflagerfläche in einfacher Weise durch Drehbearbeitung hergestellt werden.Alternatively, the cylindrical bearing 34 may be formed with a convex curved cylindrical bearing surface and the cylinder 26 with a correspondingly concave bearing surface, but a concave recess on the substantially planar cylinder bearing 34 can be formed easier than a correspondingly convex cylindrical bearing surface. On the cylinder 26 or particularly advantageous on the cylinder closure 36, a convexly curved bearing surface can be produced in a simple manner by turning.

Claims (14)

  1. Industrial truck having a piston/cylinder arrangement (20), comprising a cylinder (26) and a piston (22), which can be extended out of and withdrawn into said cylinder (26), as a drive and/or as guidance for a first component (12) for the purpose of moving it in relation to a second component (14), in particular as a drive for components (12, 14) of a mast (10), the piston (22) being coupled for force transfer purposes to a component (14) associated with it (first or second component), and the cylinder (26) being mounted on a cylinder bearing (30, 34) of the respective other component (12) associated with the cylinder (26) and being coupled to said component (12) for force transfer purposes, the cylinder (26) being in bearing engagement with the cylinder bearing (34) such that it can be moved in relation to the cylinder bearing (34), the cylinder (26) having a bearing formation (42) having a supporting surface (42a) which is in bearing engagement with a cylinder bearing surface (34a) of the cylinder bearing (34), extends along a circumferential section of the cylinder (26) and surrounds the cylinder (26) in the circumferential direction, characterized in that the supporting surface (42a) is arranged on a surface of the bearing formation (42) which is directed towards a lower longitudinal end (26a) of the cylinder (26).
  2. Industrial truck according to Claim 1, characterized in that the cylinder (26) has a closed longitudinal end (26a) and a longitudinal end (26b) having a piston opening (32), and the cylinder bearing (34) bears the cylinder (26) in the region of its longitudinal end (26b) having the piston opening (32), preferably in a longitudinal end region, which starts from the longitudinal end (26b) having the piston opening (32), of 20% of the total length of the cylinder (26), particularly preferably of 10% of the total length of the cylinder (26), most preferably of 5% of the total length of the cylinder (26).
  3. Industrial truck according to Claim 1 or 2, characterized in that the cylinder (26) can be displaced in relation to the cylinder bearing (34) in at least one displacement direction, which is orthogonal with respect to the cylinder longitudinal axis direction (L), preferably in two displacement directions, which are orthogonal both with respect to one another and with respect to the cylinder longitudinal axis direction (L).
  4. Industrial truck according to one of the preceding claims, characterized in that the cylinder (26) can be tipped in relation to the cylinder bearing (34) about at least one tipping axis (X, Y), which is orthogonal with respect to the cylinder longitudinal axis direction (L), preferably about two tipping axes (X, Y), which are orthogonal both with respect to one another and with respect to the cylinder longitudinal axis direction (L).
  5. Industrial truck according to Claim 4, characterized in that at least one of the surfaces (42a) (supporting surface (42a) and cylinder bearing surface (34a)) is curved convexly, at least in the region of the bearing engagement, about at least one axis of curvature (X, Y), which is orthogonal with respect to the cylinder longitudinal axis direction (L).
  6. Industrial truck according to Claim 5, characterized in that at least one of the surfaces (42a) (supporting surface (42a) and cylinder bearing surface (34a)) is curved convexly, at least in the region of the bearing engagement, about two axes of curvature (X, Y), which are orthogonal both with respect to one another and with respect to the cylinder longitudinal axis direction (L).
  7. Industrial truck according to Claim 6, characterized in that the at least one surface (42a), which is curved convexly at least in sections, is in the form of a spherical dome.
  8. Industrial truck according to one of Claims 5 to 7, characterized in that one of the surfaces (42a) (supporting surface (42a) and cylinder bearing surface (34a)) is curved convexly, at least in the region of the bearing engagement, about at least one axis of curvature (X, Y), which is orthogonal with respect to the cylinder longitudinal axis direction (L), and the respective other surface (34a) (cylinder bearing surface (34a) and supporting surface (42a)) is curved concavely, at least in the region of the bearing engagement, about at least one axis of curvature (X, Y), which is orthogonal with respect to the cylinder longitudinal axis direction (L).
  9. Industrial truck according to Claim 8, characterized in that the supporting surface (42a) and the cylinder bearing surface (34a) are curved such that they bear flat against one another.
  10. Industrial truck according to Claim 2, possibly incorporating at least one of Claims 3, 4 or 5 to 9, characterized in that the cylinder (26) comprises a cylinder tube (28) and a cylinder closure (36) having a piston opening (32), the supporting surface (42a) being provided as the at least one surface, which is curved at least in sections, on the cylinder closure (36).
  11. Industrial truck according to Claim 10, characterized in that the cylinder closure (36) is a separate component at least prior to its connection to the cylinder tube (28).
  12. Industrial truck according to one of the preceding claims, characterized in that the first component (12) is fixedly connected to an industrial truck frame, and the second component (14) is mounted such that it can move in relation to the first component (12), the first component (12), which is fixed to the frame, being associated with the cylinder (26), and the second component (14), which is mounted such that it can move, being associated with the piston (22).
  13. Industrial truck according to Claim 12, characterized in that the first component (12) is an upright (12), and the second component (14) is a lifting frame (14).
  14. Industrial truck according to any of the preceding claims, characterized in that the first component (12) is a rack of an additional lifting device, and the second component (14) is a load carrier, in particular a fork carrier, which is mounted on said rack such that it can move.
EP05009845.8A 2004-05-06 2005-05-04 Industrial truck with a piston-cylinder arrangement and an improved cylinder bearing Active EP1593644B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004022338A DE102004022338A1 (en) 2004-05-06 2004-05-06 Truck with piston-cylinder arrangement and improved cylinder bearing
DE102004022338 2004-05-06

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EP1593644A2 EP1593644A2 (en) 2005-11-09
EP1593644A3 EP1593644A3 (en) 2011-09-07
EP1593644B1 true EP1593644B1 (en) 2013-06-26

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EP05009845.8A Active EP1593644B1 (en) 2004-05-06 2005-05-04 Industrial truck with a piston-cylinder arrangement and an improved cylinder bearing

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US (1) US7340989B2 (en)
EP (1) EP1593644B1 (en)
DE (1) DE102004022338A1 (en)

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Publication number Priority date Publication date Assignee Title
US10562746B2 (en) * 2016-10-28 2020-02-18 Hyster-Yale Group, Inc. Mast support device
CN211110874U (en) * 2017-03-09 2020-07-28 海斯特-耶鲁集团有限公司 Mast for forklift
CN108689350B (en) * 2017-03-30 2021-06-08 雷蒙德股份有限公司 Extendable mast system and method for a materials handling vehicle
CN110817753B (en) * 2019-11-27 2020-12-25 江苏航运职业技术学院 Gantry sliding gap control structure of fork lift truck

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US3394778A (en) * 1966-11-25 1968-07-30 Eaton Yale & Towne Lift truck mast assembly
DE1556601A1 (en) * 1967-08-01 1970-03-05 Linde Ag A lift truck with an extendable mast
US4183836A (en) * 1978-02-06 1980-01-15 E. I. Du Pont De Nemours And Company Aqueous polyurethane dispersions
US4294572A (en) * 1978-04-10 1981-10-13 Pattison Jack E Internal fluid communication system for power cylinders
DE2905084A1 (en) 1979-02-10 1980-08-21 Fluro Gelenklager Gmbh Spherical ball joint prodn. system - involves turning spherical cup contour in half of ring and upsetting other half to enclose ball
DE3070695D1 (en) * 1980-02-07 1985-07-04 Towmotor Corp Hydraulic cylinder with spherical bearing mount
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JP3419265B2 (en) * 1997-08-28 2003-06-23 日産自動車株式会社 Mounting structure of lifting equipment lifting cylinder

Also Published As

Publication number Publication date
DE102004022338A1 (en) 2005-11-24
US20060027094A1 (en) 2006-02-09
EP1593644A2 (en) 2005-11-09
EP1593644A3 (en) 2011-09-07
US7340989B2 (en) 2008-03-11

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