EP1626029B1 - Lifting structure and hydraulic cylinder for an industrial truck with a compensation arrangement - Google Patents

Lifting structure and hydraulic cylinder for an industrial truck with a compensation arrangement Download PDF

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Publication number
EP1626029B1
EP1626029B1 EP05016448A EP05016448A EP1626029B1 EP 1626029 B1 EP1626029 B1 EP 1626029B1 EP 05016448 A EP05016448 A EP 05016448A EP 05016448 A EP05016448 A EP 05016448A EP 1626029 B1 EP1626029 B1 EP 1626029B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
lifting
compensation
mast
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EP05016448A
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German (de)
French (fr)
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EP1626029A3 (en
EP1626029A2 (en
Inventor
Christian Baerwolff
Gerald Strugg
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STILL GmbH
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STILL GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/08—Masts; Guides; Chains

Definitions

  • the invention relates to a mast for a truck with a liftable load receiving device which can be raised by extending a piston from a cylinder tube of a lifting cylinder, wherein a load lifted with the load receiving device generates a bending moment acting on the mast, and wherein the lifting cylinder relative to the cylinder tube having movable compensation piston, with which an acting on the mast, the bending moment counteracting counter-torque is generated.
  • Such a mast is for example in the DE 101 33 585 A1 and is suitable for use in industrial trucks, such as counterbalanced forklifts, reach trucks, forklift trucks or stackers.
  • the weight of a load picked up by the load-carrying device and lifted by the mast exerts a bending moment on the mast which results in elastic deformation of the mast, the upper end of the mast being bent inwardly relative to the truck.
  • a lifting cylinder of the mast with a compensation piston, which exerts a bending moment counter-rotating counter-torque on the mast.
  • the lifting cylinder is arranged in relation to the truck in front of the mast.
  • the pressure force of the compensation piston is thereby supported at the upper or at the lower end of the mast, while the cylinder tube is fastened to the opposite end of the compensating piston of the mast.
  • the pressure chamber associated with the compensation piston is connected to the pressure chamber of the lift cylinder so that the force generated by the compensation piston is substantially proportional to the weight of a lifted load.
  • the piston of the lifting cylinder and the compensation piston are arranged coaxially one behind the other and extendable in the opposite direction from the cylinder tube.
  • This arrangement has the disadvantage that the length of the piston of the lifting cylinder is reduced by the length of the compensation piston and thus for the mast lower lift height available, as in conventional masts.
  • the present invention is therefore based on the object to provide a generic mast and a lifting cylinder available, in which the available extension length of the piston of the lifting cylinder is increased.
  • the compensation piston is arranged coaxially with the piston of the lifting cylinder and having a passage for the piston.
  • the piston of the lifting cylinder and the compensating piston are thus, like the pistons of a telescopic cylinder, arranged nested and independently displaceable.
  • the compensation piston has a larger diameter and thus a larger effective piston area than the piston of the lifting cylinder.
  • the piston of the lifting cylinder extends through the passage in the compensation piston upwards, wherein the piston has a much greater extension length than the compensation piston.
  • the cylinder tube of the lifting cylinder is mounted in the region of its lower end to a fixed part of the mast.
  • the compensation piston exerts its compressive force on a fixed mast of the mast, whose elastic deformation, which occurs as a result of the weight of a load lifted by the mast, is thereby at least partially compensated.
  • the piston of the lifting cylinder usually an extension mast - connected, which is raised by means of the piston.
  • An expedient embodiment of the invention is when the compensation piston is guided on the outside of the cylinder tube.
  • the compensation piston has a larger diameter than the cylinder tube and is attached to the upper end of the cylinder tube.
  • the compensation piston thus closes the cylinder tube in the manner of an attached cap and is displaceably guided on the outside of the cylinder tube.
  • the guide surface may be formed by the outer surface of the cylinder tube itself or by a separate, attached to the cylinder tube guide member.
  • a sleeve is arranged on the outside of the cylinder tube, on which the compensating piston is guided.
  • the sleeve is attached to the cylinder tube, has a finely machined outer surface and serves as a guide surface and as a sealing surface for the displaceable relative to the sleeve compensation piston.
  • the compensation piston is sealed relative to the cylinder tube, preferably by means of at least one groove and / or at least one scraper. This corresponds to the usual seal for pistons of hydraulic cylinders.
  • the compensation piston has suitable receptacles for the U-ring and for the scraper. The grooved ring and the scraper slide in a movement of the compensation piston on a sealing surface which is formed by the cylinder tube itself or by the arranged on the outside of the cylinder tube sleeve.
  • the piston is sealed off from the compensating piston, preferably by means of at least one groove and / or at least one scraper.
  • the fittings for the grooved ring and the scraper for sealing on the piston are located in the compensation piston, on the inside of the passage of the piston.
  • the compensation piston has a vent opening.
  • the vent opening in the pressure chambers in front of the piston or in front of the compensating piston existing air can be discharged into the environment.
  • the vent is closed.
  • the lifting cylinder on a device for cushioning an extension movement of the piston.
  • An extension movement of the piston is decelerated shortly before reaching the extended end position of the piston.
  • the device for end position damping of the extension movement of the piston comprises a throttle valve, which arranged a pressure chamber arranged in front of the piston with a front of the compensation piston Pressure room connects.
  • a throttle valve which arranged a pressure chamber arranged in front of the piston with a front of the compensation piston Pressure room connects.
  • Such a device with a throttle valve in the metallic part of the piston which can also be used in the inventive arrangement is, for example, from WO 98/49451 A1 known.
  • Equally applicable is a device with a throttle valve in a plugged onto the piston plastic ring, as disclosed for example in the not yet published German patent application STILL GmbH with the application mark 102004036424.9.
  • the lifting cylinder has a device for cushioning a retraction movement of the piston.
  • the device for cushioning the retraction movement of the piston comprises a damping piston, which is guided displaceably in the piston.
  • a damping piston which is guided displaceably in the piston.
  • Also part of the invention is a lifting cylinder for use in a mast according to one of the above claims.
  • FIG. 1 shows a mast according to the invention in a schematic representation.
  • a stand mast 30 of the mast is attached to a vehicle-fixed component 31, for example, a vehicle frame.
  • An extension mast 32 is guided on the stationary mast 30 by means of rollers and movable relative to the stationary mast 30 in the vertical direction.
  • On the extension mast 32 in turn is also by means of a load lifting device 33rd guided vertically movable.
  • the force required for lifting the extension mast 32 is generated by means of a lifting cylinder 34, which consists essentially of a cylinder tube 2, a piston 14 and a compensating piston 7.
  • the cylinder tube 2 is connected in its lower region to the stationary mast 30, while the extendable piston 14 is connected to the extension mast 32.
  • the compensation piston 7 is connected to the upper area of the stand mast 30.
  • the weight of this load exerts a bending moment 38 acting on the stand mast 30, causing the upper end of the stand mast 30 to shift to the right in the drawing as a result of the mast deflection.
  • a counter-torque is exerted on the stationary mast 30 by means of the compensation piston 7.
  • the compensation piston 7 arranged in front of the stationary mast 30 exerts an upward pressure force on the upper end of the upright mast 30, while the counterforce acting on the cylinder tube 2 is supported at the lower end of the upright mast 30.
  • FIG. 2 an inventive lifting cylinder 34 is shown.
  • a cylinder bottom 1 has an opening for supplying hydraulic oil. With the cylinder bottom 1 of the hydraulic cylinder is attached to the lower end of the mast.
  • a cylinder tube 2 connects at the upper end of a sleeve 4 is screwed and sealed by means of an O-ring 8.
  • the longitudinally displaceable compensation piston 7, Placed on the sleeve 4 is the longitudinally displaceable compensation piston 7, which is sealed relative to the sleeve 4 by means of a Nutrings 6 and a scraper 5.
  • the compensating piston 7 has a passage for a piston 14 which is displaceable relative to the cylinder tube 2 and relative to the compensating piston 7 in the longitudinal direction of the lifting cylinder.
  • the piston 14 is sealed by means of a Nutrings 12 and by means of a scraper 13, while the piston 14 is guided in the cylinder tube 2 by means of a hydraulic oil permeable piston guide 15.
  • the end position of an extension movement of the piston 14 is defined by means of a plugged stop 9.
  • the extension movement of the compensation piston is limited by the installation situation of the lifting cylinder in the mast. In the front of the piston 14th arranged pressure chamber 20 and in the arranged before the compensating piston 7 pressure chamber 21 is always the same hydraulic pressure, which - apart from dynamic effects - is proportional to the weight of a lifted with the mast load. Consequently, the compensation torque generated with the compensation piston 7 is proportional to the load weight.
  • FIG. 3 shows a lifting cylinder according to the invention with hollow piston 14a and a device for cushioning an extension movement of the piston 14a.
  • the piston 14 a is sealed relative to the cylinder tube 2 by means of a nut ring 18.
  • the hydraulic connection between the pressure chambers 20 and 21 is made with retracted piston 14 a via a channel 22 and a bore 23.
  • the cushioning effect is effective.
  • the hydraulic oil displaced from the pressure chamber 21 during an extension movement of the piston 14a flows via a throttle valve 16, 17 into the pressure chamber 20.
  • the throttle valve 16 defines a throttle opening whose flow resistance leads to an increase in pressure in the pressure chamber 21 and thereby slows the extension movement of the piston 14a.
  • a retraction movement of the piston 14a in the opposite direction is not hindered because the throttle valve 16 allows flow of hydraulic oil into the pressure chamber 21 unhindered.
  • FIG. 4 shows a lifting cylinder according to the invention with a hollow piston 14b and a device for cushioning a retraction of the piston 14b.
  • a damping piston 27 is slidably guided and biased by the force of a spring 20 according to the left in the drawing.
  • a drainage of hydraulic oil from the pressure chamber 20 through the cylinder bottom 1 b is then possible only through a throttle opening 26 in the damping piston 17, whereby the retraction movement of the piston 14b is decelerated.

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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)
  • Forklifts And Lifting Vehicles (AREA)

Abstract

The structure has a load device, driving a piston out (14) from a cylinder barrel (2) of a remote cylinder (34). A load is raised with the load device (33) producing an affecting bending moment. The remote cylinder relative to the cylinder barrel is movable against the bending moment. The piston (7) is coaxially arranged to the remote cylinder executing the piston. The piston is at the exterior of the cylinder barrel.

Description

Die Erfindung betrifft ein Hubgerüst für ein Flurförderzeug mit einer anhebbaren Lastaufnahmevorrichtung, die durch Ausfahren eines Kolbens aus einem Zylinderrohr eines Hubzylinders anhebbar ist, wobei eine mit der Lastaufnahmevorrichtung angehobene Last ein auf das Hubgerüst wirkendes Biegemoment erzeugt, und wobei der Hubzylinder einen relativ zu dem Zylinderrohr bewegbaren Kompensationskolben aufweist, mit dem ein auf das Hubgerüst wirkendes, dem Biegemoment entgegen gerichtetes Gegenmoment erzeugbar ist.The invention relates to a mast for a truck with a liftable load receiving device which can be raised by extending a piston from a cylinder tube of a lifting cylinder, wherein a load lifted with the load receiving device generates a bending moment acting on the mast, and wherein the lifting cylinder relative to the cylinder tube having movable compensation piston, with which an acting on the mast, the bending moment counteracting counter-torque is generated.

Ein derartiges Hubgerüst ist beispielsweise in der DE 101 33 585 A1 beschrieben und ist für den Einsatz in Flurförderzeugen, wie beispielsweise Gegengewichtsgabelstaplern, Schubmaststapiem, Schubgabelstaplern oder Hochhubwagen geeignet. Die Gewichtskraft einer mit der Lastaufnahmevorrichtung aufgenommenen und mit dem Hubgerüst angehobenen Last übt ein Biegemoment auf das Hubgerüst aus, das zu einer elastischen Verformung des Hubgerüsts führt, wobei das obere Ende des Hubgerüsts in Bezug auf das Flurförderzeug nach vome gebogen wird. Um dieses Biegemoment, das zu der unerwünschten elastischen Verformung des Hubgerüsts führt, zumindest teilweise zu kompensieren, ist es im gattungsgemäßen Stand der Technik bekannt, einen Hubzylinder des Hubgerüsts mit einem Kompensationskolben zu versehen, der ein dem Biegemoment entgegengerichtetes Gegenmoment auf das Hubgerüst ausübt. Der Hubzylinder ist dabei in Bezug auf das Flurförderzeug vor dem Hubgerüst angeordnet. Die Druckkraft des Kompensationskolbens wird dabei am oberen oder am unteren Ende des Hubgerüsts abgestützt, während das Zylinderrohr an dem dem Kompensationskolben entgegengesetzten Ende des Hubgerüsts befestigt ist. Der dem Kompensationskolben zugeordnete Druckraum ist mit dem Druckraum des Hubzylinders verbunden, sodass die mit dem Kompensationskolben erzeugte Kraft im Wesentlichen proportional zu der Gewichtskraft einer angehobenen Last ist.Such a mast is for example in the DE 101 33 585 A1 and is suitable for use in industrial trucks, such as counterbalanced forklifts, reach trucks, forklift trucks or stackers. The weight of a load picked up by the load-carrying device and lifted by the mast exerts a bending moment on the mast which results in elastic deformation of the mast, the upper end of the mast being bent inwardly relative to the truck. To compensate for this bending moment, which leads to the unwanted elastic deformation of the mast, at least partially, it is known in the generic state of the art to provide a lifting cylinder of the mast with a compensation piston, which exerts a bending moment counter-rotating counter-torque on the mast. The lifting cylinder is arranged in relation to the truck in front of the mast. The pressure force of the compensation piston is thereby supported at the upper or at the lower end of the mast, while the cylinder tube is fastened to the opposite end of the compensating piston of the mast. The pressure chamber associated with the compensation piston is connected to the pressure chamber of the lift cylinder so that the force generated by the compensation piston is substantially proportional to the weight of a lifted load.

Bei der in der DE 101 33 585 A1 vorgeschlagenen Anordnung sind der Kolben des Hubzylinders und der Kompensationskolben koaxial hintereinander angeordnet und in entgegengesetzte Richtung aus dem Zylinderrohr ausfahrbar. Diese Anordnung hat den Nachteil, dass die Länge des Kolbens des Hubzylinders um die Länge des Kompensationskolbens verringert ist und damit für das Hubgerüst eine geringere Hubhöhe zur Verfügung steht, als bei herkömmlichen Hubgerüsten.When in the DE 101 33 585 A1 proposed arrangement, the piston of the lifting cylinder and the compensation piston are arranged coaxially one behind the other and extendable in the opposite direction from the cylinder tube. This arrangement has the disadvantage that the length of the piston of the lifting cylinder is reduced by the length of the compensation piston and thus for the mast lower lift height available, as in conventional masts.

Der vorliegenden Erfindung liegt daher die Aufgabe zu Grunde, ein gattungsgemäßes Hubgerüst und einen Hubzylinder zur Verfügung zu stellen, bei dem die zur Verfügung stehende Ausfahrlänge des Kolbens des Hubzylinders vergrößert ist.The present invention is therefore based on the object to provide a generic mast and a lifting cylinder available, in which the available extension length of the piston of the lifting cylinder is increased.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, dass der Kompensationskolben koaxial zu dem Kolben des Hubzylinders angeordnet ist und eine Durchführung für den Kolben aufweist. Der Kolben des Hubzylinders und der Kompensationskolben sind damit, ähnlich wie die Kolben eines Teleskopzylinders, ineinander verschachtelt angeordnet und unabhängig voneinander verschiebbar. Der Kompensationskolben weist einen größeren Durchmesser und damit eine größere wirksame Kolbenfläche auf als der Kolben des Hubzylinders. Der Kolben des Hubzylinders erstreckt sich durch die Durchführung im Kompensationskolben nach oben, wobei der Kolben eine wesentlich größere Ausfahrlänge aufweist als der Kompensationskolben. Das Zylinderrohr des Hubzylinders ist im Bereich seines unteren Endes an einem feststehenden Teil des Hubgerüsts gelagert. Der Kompensationskolben übt seine Druckkraft auf einen feststehenden Mast des Hubgerüsts auf, dessen elastische Verformung, die in Folge der Gewichtskraft einer mit dem Hubgerüst angehobenen Last auftritt, dadurch zumindest teilweise kompensiert wird. Der Kolben des Hubzylinders ist hingegen mit einem ausfahrbaren Teil des Hubgerüsts - in der Regel einem Ausfahrmast - verbunden, das mittels des Kolbens anhebbar ist.This object is achieved in that the compensation piston is arranged coaxially with the piston of the lifting cylinder and having a passage for the piston. The piston of the lifting cylinder and the compensating piston are thus, like the pistons of a telescopic cylinder, arranged nested and independently displaceable. The compensation piston has a larger diameter and thus a larger effective piston area than the piston of the lifting cylinder. The piston of the lifting cylinder extends through the passage in the compensation piston upwards, wherein the piston has a much greater extension length than the compensation piston. The cylinder tube of the lifting cylinder is mounted in the region of its lower end to a fixed part of the mast. The compensation piston exerts its compressive force on a fixed mast of the mast, whose elastic deformation, which occurs as a result of the weight of a load lifted by the mast, is thereby at least partially compensated. The piston of the lifting cylinder, however, with an extendable part of the mast - usually an extension mast - connected, which is raised by means of the piston.

Eine zweckmäßige Ausgestaltung der Erfindung liegt vor, wenn der Kompensationskolben an der Außenseite des Zylinderrohrs geführt ist. Der Kompensationskolben hat dabei einen größeren Durchmesser als das Zylinderrohr und ist auf das obere Ende des Zylinderrohrs aufgesteckt. Der Kompensationskolben verschließt damit das Zylinderrohr in der Art einer aufgesteckten Kappe und ist an der Außenseite des Zylinderrohrs verschiebbar geführt. Die Führungsfläche kann dabei von der Außenfläche des Zylinderrohrs selbst oder von einem separaten, an dem Zylinderrohr befestigten Führungsbauteil gebildet sein.An expedient embodiment of the invention is when the compensation piston is guided on the outside of the cylinder tube. The compensation piston has a larger diameter than the cylinder tube and is attached to the upper end of the cylinder tube. The compensation piston thus closes the cylinder tube in the manner of an attached cap and is displaceably guided on the outside of the cylinder tube. The guide surface may be formed by the outer surface of the cylinder tube itself or by a separate, attached to the cylinder tube guide member.

Besonders vorteilhaft ist es, wenn an der Außenseite des Zylinderrohrs eine Hülse angeordnet ist, an der der Kompensationskolben geführt ist. Die Hülse ist an dem Zylinderrohr befestigt, weist eine feinbearbeitete Außenfläche auf und dient als Führungsfläche und als Dichtfläche für den relativ zur Hülse verschiebbaren Kompensationskolben.It is particularly advantageous if a sleeve is arranged on the outside of the cylinder tube, on which the compensating piston is guided. The sleeve is attached to the cylinder tube, has a finely machined outer surface and serves as a guide surface and as a sealing surface for the displaceable relative to the sleeve compensation piston.

Der Kompensationskolben ist gegenüber dem Zylinderrohr abgedichtet, vorzugsweise mittels mindestens eines Nutrings und/oder mindestens eines Abstreifers. Dies entspricht der üblichen Abdichtung für Kolben von Hydraulikzylindern. Der Kompensationskolben weist dabei geeignete Aufnahmen für den Nutring und für den Abstreifer auf. Der Nutring und der Abstreifer gleiten bei einer Bewegung des Kompensationskolbens auf einer Dichtfläche ab, die von dem Zylinderrohr selbst oder von der an der Außenseite des Zylinderrohrs angeordneten Hülse gebildet ist.The compensation piston is sealed relative to the cylinder tube, preferably by means of at least one groove and / or at least one scraper. This corresponds to the usual seal for pistons of hydraulic cylinders. The compensation piston has suitable receptacles for the U-ring and for the scraper. The grooved ring and the scraper slide in a movement of the compensation piston on a sealing surface which is formed by the cylinder tube itself or by the arranged on the outside of the cylinder tube sleeve.

Weiter ist der Kolben gegenüber dem Kompensationskolben abgedichtet, vorzugsweise mittels mindestens eines Nutrings und/oder mindestens eines Abstreifers. Die Aufnahmen für den Nutring und den Abstreifer zur Abdichtung am Kolben befinden sich im Kompensationskolben, an der Innenseite der Durchführung des Kolbens. Bei einer Relativbewegung zuwischen Kolben und Kompensationskolben gleiten der Nutring und der Abstreifer an der Außenfläche des Kolbens ab.Furthermore, the piston is sealed off from the compensating piston, preferably by means of at least one groove and / or at least one scraper. The fittings for the grooved ring and the scraper for sealing on the piston are located in the compensation piston, on the inside of the passage of the piston. During a relative movement between the piston and compensation piston slide the U-ring and the wiper on the outer surface of the piston from.

Zweckmäßigerweise weist der Kompensationskolben eine Entlüftungsöffnung auf. Mittels der Entlüftungsöffnung kann eine in den Druckräumen vor dem Kolben oder vor dem Kompensationskolben vorhandene Luft in die Umgebung abgelassen werden. Während des normalen Betriebs des Hubzylinders ist die Entlüftungsöffnung geschlossen.Conveniently, the compensation piston has a vent opening. By means of the vent opening in the pressure chambers in front of the piston or in front of the compensating piston existing air can be discharged into the environment. During normal operation of the lift cylinder, the vent is closed.

Gemäß einer Weiterbildung der Erfindung weist der Hubzylinder eine Vorrichtung zur Endlagendämpfung einer Ausfahrbewegung des Kolbens auf. Eine Ausfahrbewegung des Kolbens wird dabei kurz vor Erreichen der ausgefahrenen Endstellung des Kolbens abgebremst.According to one embodiment of the invention, the lifting cylinder on a device for cushioning an extension movement of the piston. An extension movement of the piston is decelerated shortly before reaching the extended end position of the piston.

Mit besonderem Vorteil umfasst die Vorrichtung zur Endlagendämpfung der Ausfahrbewegung des Kolbens ein Drosselventils, das einen vor dem Kolben angeordneten Druckraum mit einem vor dem Kompensationskolben angeordneten Druckraum verbindet. Eine derartige Vorrichtung mit einem Drosselventil im metallischen Teil des Kolbens, die auch in der erfindungsgemäßen Anordnung einsetzbar ist, ist beispielsweise aus der WO 98/49451 A1 bekannt. Ebenso einsetzbar ist eine Vorrichtung mit einem Drosselventil in einem auf den Kolben aufgesteckten Kunststoffring, wie sie beispielsweise in der noch nicht veröffentlichten deutschen Patentanmeldung der STILL GmbH mit dem Anmeldeaktenzeichen 102004036424.9 offenbart ist.With particular advantage, the device for end position damping of the extension movement of the piston comprises a throttle valve, which arranged a pressure chamber arranged in front of the piston with a front of the compensation piston Pressure room connects. Such a device with a throttle valve in the metallic part of the piston, which can also be used in the inventive arrangement is, for example, from WO 98/49451 A1 known. Equally applicable is a device with a throttle valve in a plugged onto the piston plastic ring, as disclosed for example in the not yet published German patent application STILL GmbH with the application mark 102004036424.9.

Ebenso zweckmäßig ist eine Weiterbildung der Erfindung, bei der der Hubzylinder eine Vorrichtung zur Endlagendämpfung einer Einfahrbewegung des Kolbens aufweist.Equally useful is a development of the invention, in which the lifting cylinder has a device for cushioning a retraction movement of the piston.

Gemäß einer möglichen Ausgestaltungsform umfasst die Vorrichtung zur Endlagendämpfung der Einfahrbewegung des Kolbens einen Dämpfungskolben, der in dem Kolben verschiebbar geführt ist. Eine derartige Vorrichtung, die in einfacher Weise auf den Gegenstand der vorliegenden Erfindung übertragbar ist, ist ebenfalls in der WO 98/49451 A1 offenbart.According to a possible embodiment, the device for cushioning the retraction movement of the piston comprises a damping piston, which is guided displaceably in the piston. Such a device, which is easily transferable to the subject matter of the present invention, is also disclosed in U.S.P. WO 98/49451 A1 disclosed.

Ebenfalls Bestandteil der Erfindung ist ein Hubzylinder zur Verwendung in einem Hubgerüst nach einem der oben erläuterten Ansprüche.Also part of the invention is a lifting cylinder for use in a mast according to one of the above claims.

Weitere Vorteile und Einzelheiten der Erfindung werden anhand der in den schematischen Figuren dargestellten Ausführungsbeispiele näher erläutert. Dabei zeigt

Figur 1
ein erfindungsgemäßes Hubgerüst in schematischer Darstellung,
Figur 2
einen erfindungsgemäßen Hubzylinder,
Figur 3
einen erfindungsgemäßen Hubzylinder mit Endlagendämpfung der Ausfahrbewegung des Kolbens,
Figur 4
einen erfindungsgemäßen Hubzylinder mit Endlagendämpfung der Einfahrbewegung des Kolbens.
Further advantages and details of the invention will be explained in more detail with reference to the embodiments illustrated in the schematic figures. It shows
FIG. 1
an inventive mast in a schematic representation,
FIG. 2
a lifting cylinder according to the invention,
FIG. 3
a lifting cylinder according to the invention with cushioning of the extension movement of the piston,
FIG. 4
a lifting cylinder according to the invention with cushioning the retraction of the piston.

Figur 1 zeigt ein erfindungsgemäßes Hubgerüst in schematischer Darstellung. Ein Standmast 30 des Hubgerüsts ist an einem fahrzeugfesten Bauteil 31, beispielsweise einem Fahrzeugrahmen befestigt. Ein Ausfahrmast 32 ist an dem Standmast 30 mittels Rollen geführt und relativ zu dem Standmast 30 in vertikaler Richtung bewegbar. An dem Ausfahrmast 32 wiederum ist ebenfalls mittels Rollen ein Lastaufnahmemittel 33 vertikal bewegbar geführt. Die zum Anheben des Ausfahrmasts 32 erforderliche Kraft wird mittels eines Hubzylinders 34 erzeugt, der im Wesentlichen aus einem Zylinderrohr 2, einem Kolben 14 und einem Kompensationskolben 7 besteht. Das Zylinderrohr 2 ist in seinem unteren Bereich mit dem Standmast 30 verbunden, während der ausfahrbare Kolben 14 mit dem Ausfahrmast 32 verbunden ist. Der Kompensationskolben 7 ist mit dem oberen Bereich des Standmasts 30 verbunden. FIG. 1 shows a mast according to the invention in a schematic representation. A stand mast 30 of the mast is attached to a vehicle-fixed component 31, for example, a vehicle frame. An extension mast 32 is guided on the stationary mast 30 by means of rollers and movable relative to the stationary mast 30 in the vertical direction. On the extension mast 32 in turn is also by means of a load lifting device 33rd guided vertically movable. The force required for lifting the extension mast 32 is generated by means of a lifting cylinder 34, which consists essentially of a cylinder tube 2, a piston 14 and a compensating piston 7. The cylinder tube 2 is connected in its lower region to the stationary mast 30, while the extendable piston 14 is connected to the extension mast 32. The compensation piston 7 is connected to the upper area of the stand mast 30.

Wenn sich auf dem Lastaufnahmemittel 33 eine Last befindet, übt die Gewichtskraft dieser Last ein auf den Standmast 30 wirkendes Biegemoment 38 aus, das dazu führt, dass das obere Ende des Standmasts 30 infolge der Mastdurchbiegung nach in der Zeichnung rechts verschoben wird. Um dies zumindest teilweise zu kompensieren, wird mittels des Kompensationskolbens 7 ein Gegenmoment auf den Standmast 30 ausgeübt. Hierbei übt der vor dem Standmast 30 angeordnete Kompensationskolben 7 auf das obere Ende des Standmasts 30 eine nach oben gerichtete Druckkraft aus, während die auf das Zylinderrohr 2 wirkende Gegenkraft am unteren Ende des Standmasts 30 abgestützt wird. Diese Kräfte wirken auf den Standmast als dem Biegemoment entgegen gerichtetes Gegenmoment, da die Einleitungspunkte der Kräfte deutlich vor dem Flächenschwerpunkt des Standmasts 30 liegen.When there is a load on the load-carrying means 33, the weight of this load exerts a bending moment 38 acting on the stand mast 30, causing the upper end of the stand mast 30 to shift to the right in the drawing as a result of the mast deflection. To compensate for this at least partially, a counter-torque is exerted on the stationary mast 30 by means of the compensation piston 7. In this case, the compensation piston 7 arranged in front of the stationary mast 30 exerts an upward pressure force on the upper end of the upright mast 30, while the counterforce acting on the cylinder tube 2 is supported at the lower end of the upright mast 30. These forces act on the stationary mast as the bending moment counteracting counter-moment, since the points of introduction of the forces are well ahead of the centroid of the stand mast 30.

In Figur 2 ist ein erfindungsgemäßer Hubzylinder 34 dargestellt. Ein Zylinderboden 1 weist eine Öffnung zur Zuführung von Hydrauliköl auf. Mit dem Zylinderboden 1 ist der Hydraulikzylinder an dem unteren Ende des Standmasts befestigt. An den Zylinderboden 1 schließt sich ein Zylinderrohr 2 an, an dessen oberem Ende eine Hülse 4 aufgeschraubt und mittels eines O-Rings 8 abgedichtet ist. Auf die Hülse 4 aufgesteckt ist der in Längsrichtung verschiebbare Kompensationskolben 7, der gegenüber der Hülse 4 mittels eines Nutrings 6 und eines Abstreifers 5 abgedichtet ist. Erfindungsgemäß weist der Kompensationskolben 7 eine Durchführung für einen Kolben 14 auf, der relativ zu dem Zylinderrohr 2 und relativ zu dem Kompensationskolben 7 in Längsrichtung des Hubzylinders verschiebbar ist. Gegenüber dem Kompensationskolben 7 ist der Kolben 14 mittels eines Nutrings 12 und mittels eines Abstreifers 13 abgedichtet, während der Kolben 14 in dem Zylinderrohr 2 mittels einer für Hydrauliköl durchlässigen Kolbenführung 15 geführt ist. Die Endstellung einer Ausfahrbewegung des Kolbens 14 ist mittels eines aufgesteckten Anschlags 9 definiert. Die Ausfahrbewegung des Kompensationskolbens ist durch die Einbausituation des Hubzylinders im Hubgerüst begrenzt. In dem vor dem Kolben 14 angeordneten Druckraum 20 und in dem vor dem Kompensationskolben 7 angeordneten Druckraum 21 steht stets der gleiche Hydraulikdruck an, der - abgesehen von dynamischen Effekten - proportional zu dem Gewicht einer mit dem Hubgerüst angehobenen Last ist. Demzufolge ist auch das mit dem Kompensationskolben 7 erzeugte Kompensationsmoment proportional zum Lastgewicht.In FIG. 2 an inventive lifting cylinder 34 is shown. A cylinder bottom 1 has an opening for supplying hydraulic oil. With the cylinder bottom 1 of the hydraulic cylinder is attached to the lower end of the mast. At the cylinder bottom 1, a cylinder tube 2 connects at the upper end of a sleeve 4 is screwed and sealed by means of an O-ring 8. Placed on the sleeve 4 is the longitudinally displaceable compensation piston 7, which is sealed relative to the sleeve 4 by means of a Nutrings 6 and a scraper 5. According to the invention, the compensating piston 7 has a passage for a piston 14 which is displaceable relative to the cylinder tube 2 and relative to the compensating piston 7 in the longitudinal direction of the lifting cylinder. Opposite the compensating piston 7, the piston 14 is sealed by means of a Nutrings 12 and by means of a scraper 13, while the piston 14 is guided in the cylinder tube 2 by means of a hydraulic oil permeable piston guide 15. The end position of an extension movement of the piston 14 is defined by means of a plugged stop 9. The extension movement of the compensation piston is limited by the installation situation of the lifting cylinder in the mast. In the front of the piston 14th arranged pressure chamber 20 and in the arranged before the compensating piston 7 pressure chamber 21 is always the same hydraulic pressure, which - apart from dynamic effects - is proportional to the weight of a lifted with the mast load. Consequently, the compensation torque generated with the compensation piston 7 is proportional to the load weight.

Figur 3 zeigt einen erfindungsgemäßen Hubzylinder mit hohlem Kolben 14a und einer Vorrichtung zur Endlagendämpfung einer Ausfahrbewegung des Kolbens 14a. Im Unterschied zu der Anordnung gemäß Figur 2 ist der Kolben 14a gegenüber dem Zylinderrohr 2 mittels eines Nutrings 18 abgedichtet. Die hydraulische Verbindung zwischen den Druckräumen 20 und 21 ist bei eingefahrenem Kolben 14a über einen Kanal 22 und eine Bohrung 23 hergestellt. Wenn sich der Kolben 14a - wie in Fig. 3 dargestellt - in einer Position befindet, in der die Bohrung 23 durch den Kompensationskolben 7 verdeckt ist, ist die Endlagendämpfung wirksam. In diesem Fall fließt das bei einer Ausfahrbewegung des Kolbens 14a aus dem Druckraum 21 verdrängte Hydrauliköl über ein Drosselventil 16, 17 in den Druckraum 20 ab. Hierbei definiert das Drosselventil 16 eine Drosselöffnung, deren Strömungswiderstand zu einer Druckerhöhung im Druckraum 21 führt und dadurch die Ausfahrbewegung des Kolbens 14a verlangsamt. Eine Einfahrbewegung des Kolbens 14a in entgegengesetzte Richtung wird jedoch nicht behindert, da das Drosselventil 16 ein Zuströmen von Hydrauliköl in den Druckraum 21 ungehindert zulässt. FIG. 3 shows a lifting cylinder according to the invention with hollow piston 14a and a device for cushioning an extension movement of the piston 14a. In contrast to the arrangement according to FIG. 2 the piston 14 a is sealed relative to the cylinder tube 2 by means of a nut ring 18. The hydraulic connection between the pressure chambers 20 and 21 is made with retracted piston 14 a via a channel 22 and a bore 23. When the piston 14a - as in Fig. 3 shown - located in a position in which the bore 23 is covered by the compensation piston 7, the cushioning effect is effective. In this case, the hydraulic oil displaced from the pressure chamber 21 during an extension movement of the piston 14a flows via a throttle valve 16, 17 into the pressure chamber 20. Here, the throttle valve 16 defines a throttle opening whose flow resistance leads to an increase in pressure in the pressure chamber 21 and thereby slows the extension movement of the piston 14a. However, a retraction movement of the piston 14a in the opposite direction is not hindered because the throttle valve 16 allows flow of hydraulic oil into the pressure chamber 21 unhindered.

Figur 4 zeigt einen erfindungsgemäßen Hubzylinder mit hohlem Kolben 14b und einer Vorrichtung zur Endlagendämpfung einer Einfahrbewegung des Kolbens 14b. In einer mit dem Kolben 14b verschraubten Führungshülse 28 ist ein Dämpfungskolben 27 verschiebbar geführt und mit der Kraft einer Feder 20 nach in der Zeichnung links vorgespannt. Bei einer Einfahrbewegung des Kolbens 14b nach in der Zeichnung links tritt der mit der Kraft der Feder 20 bis zum Anschlag 24 nach links verschobene Dämpfungskolben 27 kurz vor Erreichen der Endstellung mit einem Sitz 25 im Zylinderboden 1 b in Kontakt. Ein Abfließen von Hydrauliköl aus dem Druckraum 20 durch den Zylinderboden 1 b ist dann nur noch durch eine Drosselöffnung 26 im Dämpfungskolben 17 möglich, wodurch die Einfahrbewegung des Kolbens 14b abgebremst wird. FIG. 4 shows a lifting cylinder according to the invention with a hollow piston 14b and a device for cushioning a retraction of the piston 14b. In a screwed to the piston 14b guide sleeve 28, a damping piston 27 is slidably guided and biased by the force of a spring 20 according to the left in the drawing. At a retraction movement of the piston 14b left in the drawing occurs with the force of the spring 20 to stop 24 to the left shifted damping piston 27 shortly before reaching the end position with a seat 25 in the cylinder base 1 b in contact. A drainage of hydraulic oil from the pressure chamber 20 through the cylinder bottom 1 b is then possible only through a throttle opening 26 in the damping piston 17, whereby the retraction movement of the piston 14b is decelerated.

Claims (11)

  1. Lifting mast for an industrial truck with a load pickup apparatus (33) capable of being raised, which load pickup apparatus can be raised by a piston (14) being extended out of a cylinder tube (2) of a lifting cylinder (34), a load, which is raised by the load pickup apparatus (33), generating a bending torque acting on the lifting mast, and the lifting cylinder (34) having a compensation piston (7), which is capable of moving relative to the cylinder tube (2) and with which a countertorque, which acts on the lifting mast and is in the opposite direction to the bending torque, can be generated, characterized in that the compensation piston (7) is arranged coaxially with respect to the piston (14) of the lifting cylinder (34) and has a bushing for the piston (14).
  2. Lifting mast according to Claim 1, characterized in that the compensation piston (7) is guided on the outer side of the cylinder tube (2).
  3. Lifting mast according to Claim 1 or 2, characterized in that a sleeve (4) is arranged on the outer side of the cylinder tube (2), and the compensation piston (7) is guided on said sleeve (4).
  4. Lifting mast according to one of Claims 1 to 3, characterized in that the compensation piston (7) is sealed off from the cylinder tube (2), preferably by means of at least one lip seal (6) and/or at least one wiper seal (5).
  5. Lifting mast according to one of Claims 1 to 4, characterized in that the piston (14) is sealed off from the compensation piston (7), preferably by means of at least one lip seal (12) and/or at least one wiper seal (13).
  6. Lifting mast according to one of Claims 1 to 5, characterized in that the compensation piston (7) has a ventilation opening (10).
  7. Lifting mast according to one of Claims 1 to 6, characterized in that the lifting cylinder (39) has an apparatus for the stop-position damping of an extension movement of the piston (14).
  8. Lifting mast according to Claim 7, characterized in that the apparatus for the stop-position damping of the extension movement of the piston (14) comprises a throttle valve (16, 17), which connects a pressure chamber (20), which is arranged in front of the piston (14), to a pressure chamber (21), which is arranged in front of the compensation piston (7).
  9. Lifting mast according to one of Claims 1 to 8, characterized in that the lifting cylinder (34) has an apparatus for the stop-position damping of a withdrawal movement of the piston (14).
  10. Lifting mast according to Claim 9, characterized in that the apparatus for the stop-position damping of the withdrawal movement of the piston (14) comprises a damping piston (17), which is guided displaceably in the piston (14).
  11. Hydraulic cylinder for use as a lifting cylinder in a lifting mast according to one of Claims 1 to 10, the lifting cylinder (24) having a compensation piston (7), which is capable of moving relative to a cylinder tube (2), and the compensation piston (7) being arranged coaxially with respect to a piston (14) of the lifting cylinder (34) and having a bushing for the piston (14).
EP05016448A 2004-08-12 2005-07-28 Lifting structure and hydraulic cylinder for an industrial truck with a compensation arrangement Active EP1626029B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004039211A DE102004039211A1 (en) 2004-08-12 2004-08-12 Mast and hydraulic cylinder with a compensation device

Publications (3)

Publication Number Publication Date
EP1626029A2 EP1626029A2 (en) 2006-02-15
EP1626029A3 EP1626029A3 (en) 2007-01-24
EP1626029B1 true EP1626029B1 (en) 2008-09-24

Family

ID=35335748

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05016448A Active EP1626029B1 (en) 2004-08-12 2005-07-28 Lifting structure and hydraulic cylinder for an industrial truck with a compensation arrangement

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EP (1) EP1626029B1 (en)
AT (1) ATE409165T1 (en)
DE (2) DE102004039211A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202012002445U1 (en) 2012-03-06 2013-06-07 Jungheinrich Aktiengesellschaft Truck with optionally selectable destacking auxiliary mode
CN103967865A (en) * 2014-05-29 2014-08-06 徐州徐工液压件有限公司 Hydraulic cylinder with position locking function

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29707639U1 (en) * 1997-04-28 1997-08-21 Still GmbH, 22113 Hamburg Hydraulic cylinder with shock protection
DE19802119A1 (en) * 1998-01-21 1999-07-22 Still Wagner Gmbh & Co Kg Industrial truck with a lifting device
GB2364992B (en) * 2000-07-24 2004-05-05 Lansing Linde Ltd Lifting structure for an industrial truck
DE102004036424A1 (en) * 2004-07-27 2006-03-23 Still Gmbh Hydraulic cylinder with end position damping

Also Published As

Publication number Publication date
EP1626029A3 (en) 2007-01-24
DE502005005456D1 (en) 2008-11-06
EP1626029A2 (en) 2006-02-15
DE102004039211A1 (en) 2006-02-23
ATE409165T1 (en) 2008-10-15

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