EP1632452B1 - Chariot de manutention avec cylindre rigidement attaché au dispositif de déplacement de charge - Google Patents

Chariot de manutention avec cylindre rigidement attaché au dispositif de déplacement de charge Download PDF

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Publication number
EP1632452B1
EP1632452B1 EP05019040A EP05019040A EP1632452B1 EP 1632452 B1 EP1632452 B1 EP 1632452B1 EP 05019040 A EP05019040 A EP 05019040A EP 05019040 A EP05019040 A EP 05019040A EP 1632452 B1 EP1632452 B1 EP 1632452B1
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EP
European Patent Office
Prior art keywords
cylinder
piston
axis
device part
industrial truck
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP05019040A
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German (de)
English (en)
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EP1632452A2 (fr
EP1632452A3 (fr
Inventor
Klaus SCHRÖDER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jungheinrich AG
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Jungheinrich AG
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Publication date
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Publication of EP1632452A2 publication Critical patent/EP1632452A2/fr
Publication of EP1632452A3 publication Critical patent/EP1632452A3/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/08—Masts; Guides; Chains
    • B66F9/10—Masts; Guides; Chains movable in a horizontal direction relative to truck
    • 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 present invention relates to an industrial truck with a load transfer device, according to the preamble of claim 1.
  • FIG. 3 of the US 3,362,503 A shows in conjunction with FIG. 2 how a cylinder of a piston-cylinder system for lifting and lowering a load-receiving means of a truck may be formed as a structural component of a lifting mast.
  • a load transfer device is a mast, an additional stroke, a side thruster and the like.
  • the cylinder of the at least one piston-cylinder system is usually articulated at its longitudinal end opposite the piston outlet end on the device part assigned to it.
  • the cylinder usually penetrates a staggered from the articulation point to the piston outlet end hole die, which is firmly connected to the cylinder associated with the device part.
  • the perforated die holds the cylinder only roughly in position and thus prevents buckling of the piston-cylinder system with the piston extended far.
  • the supporting point of the cylinder on the perforated die is generally not designed to transmit appreciable forces to the cylinder. A relative movement between the punch die and the cylinder along the cylinder longitudinal axis and around it is permitted.
  • the cylinder is rigidly connected to the device part assigned to it, such that torsional moments acting about a torsion axis extending in the cylinder longitudinal direction and / or tensile forces and / or pressure forces substantially acting in the cylinder longitudinal direction and / or about a substantially orthogonal to the cylinder longitudinal direction Bending axis acting bending moments of the device part at least on a longitudinal portion of the cylinder, in particular of the cylinder jacket, are transferable.
  • Such torsional moments can occur in a load transfer device, for example, when the load transfer device has a side thrust device on which a load in the vehicle side direction is taken with respect to a vehicle longitudinal center plane and accelerates or decelerates the truck with such a recorded load.
  • Tensile and / or compressive forces can be caused by acting on the load transfer device bending moment, such as when the load, as usual in forklifts and order pickers, is accommodated such that the load center of gravity is spaced from the adjustable device parts.
  • the load transfer device bending moment such as when the load, as usual in forklifts and order pickers, is accommodated such that the load center of gravity is spaced from the adjustable device parts.
  • the rigid connection of the cylinder with its associated device part of the cylinder is part of the steel frame structure of the load transfer device and contributes to the overall rigidity. Due to the increased overall stiffness, the same load results in less deformation than in the prior art. In addition, the increased overall stiffness of the load transfer device leads to an increase in the stimulable at the load transfer device natural vibration frequencies so that the same applied compared to the prior art applied load in addition to the lower deformation also stimulates a higher-frequency vibration of the load transfer device, which due to The higher frequency attenuates faster by internal and external friction, as is the case in the prior art.
  • piston-cylinder unit is to be provided anyway, and thus the increased overall rigidity of the load transfer device can be realized substantially without mass increase or by omission of the hole matrices even with a concomitant reduction in mass.
  • the cylinder may be connected to its associated device part such that only a load of torsional moment, tensile and / or compressive force or bending moment from the device part to the cylinder is transferable.
  • the cylinder is rigidly connected to the device part such that torsional moment as well as tensile and / or compressive forces as well as bending moments can be introduced into the cylinder by the device part.
  • a rigid connection of the cylinder with the respective device part is then particularly suitable for force and / or torque transmission, when a relative movement between the cylinder and device part in the direction of action of the force and / or the torque is substantially completely prevented.
  • a rigid connection is designed to transmit forces and moments from each of two components to the other, ie bidirectionally.
  • Such bidirectional transferability of torsional moments, tensile and / or compressive forces or bending moments between the cylinder and the device part will also be the rule in the present invention. It is crucial, however, that such forces and moments are transferable from the device part to the cylinder, since it is primarily a question of, from the outside, i. usually from the recorded load to absorb forces acting on the load transfer device on the load transfer device.
  • the cylinder jacket lying between the longitudinal ends of the cylinder is suitable for absorbing torsional moments, tensile and / or compressive forces or bending moments, since it represents a body which is homogeneous over a considerable portion of the cylinder length, which consequently results in a substantially homogeneous material loading, which is the result stressed material less strained.
  • the longitudinal section of the cylinder on which due to the rigid connection with its associated device part forces and moments are transferable from the device part, can thus be integrated as additional Torsionsoder / and bending spring and / or as tension and / or pressure rod in the framework construction of the load transfer device ,
  • this can be directly connected to its associated device part.
  • a cylinder outer surface is directly connected to a surface of the device part by form or material connection.
  • at least a portion of the cylinder outer wall is directly welded to the device part in direct connection.
  • the cylinder can also indirectly with the device part be connected, ie by a holder or a connecting part which is rigidly connected both to the device part and to the cylinder.
  • the device part can be positively or materially connected to the device part, in particular by welding. Welding represents the simplest possible connection, which allows both the transmission of torsional moments, bending moments and tensile and compressive forces from the device part to the cylinder.
  • the above-mentioned form-fit can be achieved for example by an interspersed by a cylinder portion opening of a cylinder holder, the cylinder outer contour and the O réellesinnenkontur are bounded in cross-section by a polygon, a toothing or the like and abut each other.
  • Tensile and compressive forces can be positively transferred by means of a holder penetrated by the cylinder on a protruding in the radial direction of the cylinder outer surface projection, preferably a circumferential projection, between the device part and cylinder.
  • the transfer of a load from the load transfer device to the cylinder can be ensured that the cylinder at least two in the cylinder longitudinally spaced connection points provided with the associated device part for transmitting torsional forces and / or tensile and / or compressive forces and / or bending moments rigidly connected to the cylinder.
  • the at least one piston-cylinder system is provided such that the longitudinal axis of the piston-cylinder system parallel to a Guide shaft is arranged, which of guide elements of the Load displacement device is defined, which guide the device parts in their relative movement along the displacement axis.
  • the tensile and / or compressive force to be absorbed by the cylinder due to the load-induced bending moment at the load transfer device is the lower, the greater the offset of the longitudinal axis of the piston-cylinder system from the guide axis of a guide arrangement formed by guide elements.
  • the guide axis of a guide arrangement can be defined by the contact points of a plurality of guide elements of a device part to the other device part, such as by each support point of a guide element on its track a line parallel to the displacement axis is drawn, the puncture points of these lines by a to the normal axis of displacement, form vertices of a polygon circumscribing an area, and the resulting guide axis is a parallel to the axis of displacement through the centroid of the area framed by the polygon.
  • a load transfer device may well have a plurality of guide axes, for example in the case of a mast, which is usually performed at each side end in the conveyor belt transverse direction for movement along the displacement axis.
  • a stable configuration at a low cost of the device part associated with the cylinder can be achieved by using a profile carrier running along the displacement axis on the relevant device part.
  • the manipulation or displacement of the load unaffected by the piston-cylinder system with minimal influence on the field of view of the truck can take place when the cylinder is arranged with its cylindrical longitudinal axis parallel to the profile carrier on the device part, wherein the cylinder longitudinal axis with respect to the profile carrier is offset to the side facing away from a load-carrying means of the truck side.
  • the cylinder is exposed to a certain deformation due to the forces and moments acting on it from the device part ago.
  • the invention prevents the cylinder deformation inhibits a liquid piston movement of the piston relative to the cylinder by a piston guide means is provided as the only guide a piston movement of the piston relative to the cylinder substantially in the cylinder longitudinal direction at the exit region of the piston from the cylinder on the cylinder head.
  • the piston guide means may be provided on an inner peripheral surface of the cylinder head facing the cylinder center longitudinal axis and abut against an outer peripheral surface of the piston facing away from the cylinder center longitudinal axis.
  • the piston guide means then forms an intermediate layer between the cylinder inner surface and the piston outer surface and can be easily replaced.
  • a cylinder in which the piston according to the invention is guided out of the cylinder for movement in the cylinder longitudinal direction only in the region of the piston outlet represents an advantageous embodiment due to the omitted piston guide on the piston longitudinal end permanently immersed in the cylinder and the associated simplifications.
  • the cylinder can be freely designed in large parts of its cylinder jacket. In particular, it need not be cylindrical in shape, but may have any polyhedral outer and inner peripheral surface. Only at the piston outlet end of the cylinder is to ensure the piston guide and a sufficient seal against leakage of hydraulic fluid from the cylinder.
  • At least one structural component of the device part assigned to the cylinder forms a housing wall section of the cylinder.
  • a structural component of the cylinder associated with the device part forms a housing wall portion of the cylinder, forming cylinder and device part quasi a single common structural unit whose structural rigidity is higher than if a cylinder as a separate component via brackets would be only indirectly connected to a structural component of the device part. Furthermore, this integral construction can reduce the number of components necessary for producing a device part, such as a stand, with a cylinder provided thereon and reduce the required assembly time.
  • the torsional stiffness and possibly also the bending and tensile rigidity of the device part can be increased by the components that expand the structural component around a cylinder, so that smaller or lighter structural components without loss of strength and rigidity are used for the same load compared to the prior art can.
  • the structural component of the device part serves to limit a cylinder volume into which the piston can be inserted and out of which it can be pushed out.
  • the cylinder and its associated device part form an integral unit.
  • the cylinder comprises plate elements which are rigidly connected to one another and to the at least one structural component in order to form a cavity for displaceably receiving the piston. Since the cylinder should preferably serve as a hydraulic cylinder and thus be able to withstand high pressures, it is preferred that the plate elements are welded to the at least one structural component. To simplify the structure and to avoid unnecessarily large dead volumes in the cylinder cavity, the plate elements are preferably flat.
  • the device part assigned to the cylinder can have a profile carrier running essentially along the displacement axis.
  • This profile carrier is particularly suitable as the above-mentioned at least one structural component, since it can form a housing wall section of the cylinder over a sufficient length.
  • the device part assigned to the cylinder preferably has two such profile carriers. In such a case, when the profiled supports are arranged parallel to each other, an existing space between the profiled supports can be completed by attaching the aforementioned plate members to the profiled supports to form a pressure-tight cylinder cavity.
  • the plate elements are preferably mounted such that they each span the distance between the two profile carriers, so that four plate elements may be sufficient to provide six side surfaces for a cuboid or basically rhombic cylinder cavity, including the two profile carrier.
  • the cylinder interior facing surfaces of the plate elements and the profile support then form the boundary surfaces of the cylinder interior.
  • FIG. 1 A first embodiment of an industrial truck according to the invention is in Fig. 1 generally designated 10.
  • the truck 10 has a mast 12, a thereto in the direction of the double arrow V movably arranged driver station carrier 14, arranged on the driver's seat carrier 14 side thruster 16 and one at the Side thruster 16 arranged additional stroke 18.
  • the Gabelplatzussi 20 carries the two forks 22 and 24, which serve as a load-handling means of the truck 10.
  • the additional stroke 18 has two profile supports 26 and 28, which are essentially parallel to one another and extend in the direction of the movement direction V, which contribute to the formation of an auxiliary lifting element 19 and to which the fork carriage 20 is guided for movement in the direction of the double arrow V.
  • the profile carriers 26 and 28 are arranged in the direction of the width V substantially orthogonal width direction B of the fork carrier 20 at a distance from each other, wherein between the profile beams 26 and 28, a piston-cylinder system 30 is arranged.
  • the piston-cylinder system 30 has a piston or a piston rod 32, which in Fig. 1 completely retracted into a cylinder 34 of the piston-cylinder system 30.
  • the cylinder 34 of the piston-cylinder system 30 is connected by means of two transverse struts 36 and 38 with the stand 19 belonging to the additional stroke 18 profile carriers 26 and 28.
  • This connection is rigid, wherein both the cylinder outer surface 34a is welded to the transverse struts 36 and 38 and the respective longitudinal ends of the transverse struts 36 and 38 are welded to the profile carriers 26 and 28.
  • Torsion axis T shown coincides with the longitudinal axis L of the cylinder 34, which is ideally also the longitudinal axis of the piston-cylinder system 30.
  • a bending moment is introduced into the upright 19 by the load taken and by the distance between its center of gravity and the guideways on the profile girders 26 and 28, which is about a width direction B extending bending axis W acts on the stand 19. Due to the rigid connection of the cylinder 34 with the stator 19 also such a bending moment is transmitted to the cylinder 34, so that the cylinder 34 acts as a bending spring and increases the flexural rigidity of the stator 19. Such a bending moment can be caused dynamically for a short time with a high amount, such as when the truck overruns a threshold when the load is picked up and the auxiliary lift 18 is lifted.
  • the cylinder section 34b lying between the two transverse struts 36 and 38 can serve as a tension and compression rod stiffening the upright 18, which can absorb forces acting on the upright 19 along the cylinder longitudinal axis 34.
  • the piston 32 is provided with a piston guide only in the region of the cylinder head 34 c, for example from the piston outlet end of the cylinder 34 to the lower edge of the upper transverse strut 36.
  • Another piston guide is not provided in the piston-cylinder system 30.
  • a relatively large distance between the piston outer wall and the cylinder inner wall can be held approximately in the longitudinal section 34b of the cylinder 34 located between the transverse struts 36 and 38. so that a load-related deformation of the cylinder 34 can be allowed without a retraction and / or extension movement of the piston 32 in the cylinder 34 into or out of this would be hindered.
  • Fig. 2 is schematically shown a cross section through the stator 19 of the additional stroke 18, wherein the cutting plane is orthogonal to the cylinder longitudinal axis L and the upper cross member 36 passes through.
  • Guideways 40, 42, 44 and 46 are provided on the profile carriers 26 and 28 on their outer legs 26a, 26b, 28a and 28b, on which guide rollers of the fork carrier 20 for guiding the in Fig. 2 Unroll fork carriage 20, not shown, in the direction of double arrow V.
  • the longitudinal ends 36a and 36b of the transverse strut 36 are welded to the middle limbs 26c and 28c of the profile beams 26 and 28, respectively.
  • the cross strut 36 has a passage opening 48 which is penetrated by the cylinder 34, the in Fig. 2 for the sake of clarity also not shown.
  • the cross strut 36 is also welded in the region of the through hole 48 with the outer surface 34 a of the cylinder 34, as indicated by a sector of the weld 50.
  • the compound of the cross member 38 with the profile beams 26 and 28 and with the cylinder 34 is to the in Fig. 2 described transverse strut 36 identical, so that can be dispensed with a separate representation of the cross member 38 with reference to the description of the cross member 36.
  • a profile carrier 50 of the mast 12 is shown, on which the driver's seat carrier 14 is guided for adjustment along the double arrow V.
  • the adjustment direction V is in Fig. 3 as already in Fig. 2 , orthogonal to the drawing plane.
  • the profile carrier 50 is not the only driver station carrier 14 in the adjustment direction V leading device, but that in the direction of adjustment V substantially orthogonal vehicle transverse direction Q spaced from the profile support 50 another profile support is arranged mirror-symmetrically to the illustrated.
  • the adjustment force necessary for adjusting the driver position carrier 14 is provided by a further piston-cylinder system 60.
  • the cylinder 64 as before the cylinder 34 of the additional stroke 18, rigidly connected to a profile carrier 50 of the mast 52, so that a torsional moment about the orthogonal to the plane of Fig. 2 oriented torsion axis T ', which coincides with the cylinder longitudinal axis L' of the cylinder 64, is transferable from the profile carrier 50 to the cylinder 64.
  • a bending moment parallel to the roller axis R or acting around a bending axis W 'orthogonal to both the roller axis R and the torsion axis T' can be introduced into the cylinder 64 by the profile carrier 50.
  • the cylinder 64 in the cylinder longitudinal direction L 'spaced apart further projections on which the projections 66 and 68 of Fig. 3 correspond, so that also orthogonal to the plane of the Fig. 3 acting tensile and compressive forces can be introduced at least in a cylinder in the longitudinal direction L 'between the spaced-apart projections cylinder section.
  • FIGS. 4 to 7 In connection with the FIGS. 4 to 7 In the following, a second embodiment of the present invention will be described. Same components as in the FIGS. 1 to 3 are in the FIGS. 4 to 7 provided with the same reference numerals, but increased by the number 100. The second embodiment of FIGS. 4 to 7 will be described below only insofar as it differs from the first embodiment, which in the FIGS. 1 to 3 is shown and their description is expressly incorporated by reference.
  • the in Fig. 4 shown cylinder 134 is designed such that it, as already described above, the piston 132 only at the outlet end of the cylinder 134 leads.
  • the cylinder 134 is formed by a front plate 170, a cover plate 172, which contains the guidance of the piston 132 and the outlet opening of the piston 132 from the cylinder 134, a bottom plate 174 and a in Fig. 4 not shown back plate 176 (s. Fig. 6 ).
  • These mentioned plate elements 170 to 176 are welded to one another and to the profiled supports 126 and 128 of the auxiliary handle 119 such that a closed pressure-tight cavity is formed in the interior of the cylinder 134 apart from the outlet opening of the piston 132. Facing surfaces 126a and 128a of the profiled beams 126 and 128 formed from inexpensive U-profile semi-finished products form boundary walls of the inner volume of the cylinder 134.
  • Fig. 5 the piston outlet from the cylinder 134 is shown enlarged.
  • Fig. 6 is a side view of invoicehub prior art 119 with integrally formed cylinder 134 can be seen.
  • the dashed line shows the piston 132 immersed in the cylinder interior 134a.
  • a diameter extension 133 at the submerged longitudinal end of the piston 132 prevents complete expulsion of the piston 132 from the cylinder 134.
  • the cylinder 134 has a supply port through which fluid can be delivered under pressure into the cylinder interior 134a to push the piston 132 out of the cylinder 134. It is likewise provided to be able to discharge the pressure of the fluid, preferably hydraulic oil, from the cylinder interior 134a in order to allow the piston 132 to be submerged in the cylinder 134.

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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)

Claims (10)

  1. Chariot de manutention avec un dispositif de déplacement de charge qui comporte deux parties de dispositif (19 ; 119) réglables de manière relative l'une par rapport à l'autre essentiellement le long d'un axe de déplacement (V) et au moins un système à piston et cylindre (30 ; 130) pour la mise à disposition d'une force nécessaire au déplacement relatif des parties de dispositif (19 ; 119), un piston (32 ; 132) du système à piston et cylindre (30 ; 130) étant attaché à l'une des parties de dispositif et un cylindre (34 ; 134) du système à piston et cylindre (30 ; 130) étant prévu respectivement sur l'autre des parties de dispositif (19 ; 119),
    au moins un composant structurel (26, 28 ; 126, 128) de la partie de dispositif (19 ; 119) associée au cylindre (34 ; 134) formant une section de paroi de boîtier du cylindre (34 ; 134),
    caractérisé en ce qu'un moyen de guidage de piston (pour 34c ; pour 172) est prévu comme seul guidage d'un déplacement du piston (32 ; 132) par rapport au cylindre (34 ; 134) essentiellement dans le sens longitudinal du cylindre (L, L') sur la zone de sortie (pour 34c ; pour 172) du piston (32 ; 132) hors du cylindre (134) sur la tête de cylindre (34c), alors que l'extrémité longitudinale (pour 133) du piston (132) plongée durablement dans l'espace intérieur de cylindre (134a) n'est pas guidée.
  2. Chariot de manutention (10) selon la revendication 1,
    caractérisé en ce que le cylindre (34, 64) est rigidement attaché à la partie de dispositif (12, 19) qui lui est associée de telle manière que des moments de torsion agissant autour d'un axe de torsion (T) s'étendant dans le sens longitudinal du cylindre (L, L') et/ou des forces de traction et/ou de pression agissant essentiellement dans le sens longitudinal du cylindre (L, L') et/ou des moments de flexion agissant autour d'un axe de flexion (W, W') s'étendant essentiellement orthogonalement au sens longitudinal du cylindre (L, L') puissent être transmis de la partie de dispositif (12, 19) au moins à une section longitudinale (34b) du cylindre (34, 64) en particulier de l'enveloppe de cylindre.
  3. Chariot de manutention selon la revendication 1 ou 2,
    caractérisé en ce que le cylindre (34, 64) est attaché, en particulier soudé directement et/ou indirectement par complémentarité de formes ou liaison de matière à la partie de dispositif (12, 19) qui lui est associée.
  4. Chariot de manutention selon la revendication 1, 2 ou 3,
    caractérisé en ce que le cylindre (34, 64) est rigidement attaché sur au moins deux points de jonction (pour 36 et 38) prévus à distance l'un de l'autre dans le sens longitudinal du cylindre (L, L') à la partie de dispositif (12, 19) qui lui est associée pour la transmission de forces de torsion et/ou de forces de traction et/ou de forces de pression et/ou de moments de flexion au cylindre (34, 64).
  5. Chariot de manutention selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'au moins un système à piston et cylindre (30, 60) est prévu de telle manière que l'axe longitudinal (L, L') du système à piston et cylindre (30, 60) soit disposé parallèlement à un axe de guidage qui est défini par des éléments de guidage du dispositif de déplacement de charge (12, 14, 16, 18, 20) qui guident les parties de dispositif (12, 14, 19, 20) lors de leur déplacement relatif le long de l'axe de déplacement (V), et en déport par rapport à celui-ci.
  6. Chariot de manutention selon la revendication 5,
    caractérisé en ce que la partie de dispositif (12, 19) associée au cylindre (34, 64) présente un support profilé (26, 28, 50) s'étendant le long de l'axe de déplacement (V), le cylindre (34, 64) étant disposé avec son axe longitudinal (L, L') parallèlement au support profilé (26, 28, 50) sur la partie de dispositif (12, 19), l'axe longitudinal du cylindre (L, L') étant décalé par rapport au support profilé (26, 28, 50) vers le côté s'écartant d'un moyen de réception de charge (22, 24) du chariot de manutention (10).
  7. Chariot de manutention selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le moyen de guidage de piston est prévu sur une surface périphérique intérieure tournée vers l'axe longitudinal du cylindre (L, L') de la tête de cylindre (34c) et repose sur une surface périphérique extérieure s'écartant de l'axe de cylindre du piston (32).
  8. Chariot de manutention selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le cylindre (134) comporte des éléments de plaque (170, 172, 174, 176), de préférence des éléments de plaque plans (170, 172, 174, 176) qui sont rigidement attachés les uns aux autres en vue de former une cavité (134a) pour le logement mobile du piston (132) ainsi qu'à l'au moins un composant structurel (126, 128), de préférence par soudage.
  9. Chariot de manutention selon l'une quelconque des revendications précédentes,
    caractérisé en ce que la partie de dispositif (119) associée au cylindre (134) présente au moins un, de préférence deux supports profilés (126, 128) s'étendant essentiellement le long de l'axe de déplacement (V) comme l'au moins un composant structurel (126, 128).
  10. Chariot de manutention selon la revendication 9,
    caractérisé en ce que la partie de dispositif (119) associée au cylindre (134) présente deux supports profilés (126, 128) parallèles, le cylindre (134) étant réalisé entre les supports profilés (126, 128).
EP05019040A 2004-09-01 2005-09-01 Chariot de manutention avec cylindre rigidement attaché au dispositif de déplacement de charge Expired - Lifetime EP1632452B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004042336A DE102004042336A1 (de) 2004-09-01 2004-09-01 Flurförderzeug mit starr mit Lastverlagerungsvorrichtung verbundenem Zylinder

Publications (3)

Publication Number Publication Date
EP1632452A2 EP1632452A2 (fr) 2006-03-08
EP1632452A3 EP1632452A3 (fr) 2006-04-26
EP1632452B1 true EP1632452B1 (fr) 2010-09-08

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US (1) US20060104783A1 (fr)
EP (1) EP1632452B1 (fr)
DE (2) DE102004042336A1 (fr)

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EP2447203B1 (fr) * 2010-11-01 2013-04-17 BT Products AB Camion industriel, procédé et programme information pour le commander
WO2015200289A1 (fr) 2014-06-26 2015-12-30 Crown Equipment Corporation Ensemble chariot pour véhicule de manutention de matériaux et procédé de fabrication de celui-ci
DE102014216736A1 (de) * 2014-08-22 2016-02-25 Jungheinrich Aktiengesellschaft Verfahren zum Steuern einer kombinierten Dreh-Schub-Bewegung
JP6952873B2 (ja) * 2017-08-15 2021-10-27 シーグリッド コーポレーション 横方向に動作する積載物取扱装置
CN110695940A (zh) * 2019-10-18 2020-01-17 南通金牛机械制造有限公司 一种智能旋转多层车

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US20060104783A1 (en) 2006-05-18
DE502005010206D1 (de) 2010-10-21
EP1632452A2 (fr) 2006-03-08
DE102004042336A1 (de) 2006-03-02
EP1632452A3 (fr) 2006-04-26

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