EP1630123B1 - Chariot élévateur avec un amortisseur pour les fourches - Google Patents

Chariot élévateur avec un amortisseur pour les fourches Download PDF

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Publication number
EP1630123B1
EP1630123B1 EP05018066A EP05018066A EP1630123B1 EP 1630123 B1 EP1630123 B1 EP 1630123B1 EP 05018066 A EP05018066 A EP 05018066A EP 05018066 A EP05018066 A EP 05018066A EP 1630123 B1 EP1630123 B1 EP 1630123B1
Authority
EP
European Patent Office
Prior art keywords
load
industrial truck
support structure
mounting means
damping arrangement
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 - Fee Related
Application number
EP05018066A
Other languages
German (de)
English (en)
Other versions
EP1630123A3 (fr
EP1630123A2 (fr
Inventor
Michael Dipl.-Ing. Schönauer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jungheinrich AG
Original Assignee
Jungheinrich AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Jungheinrich AG filed Critical Jungheinrich AG
Publication of EP1630123A2 publication Critical patent/EP1630123A2/fr
Publication of EP1630123A3 publication Critical patent/EP1630123A3/fr
Application granted granted Critical
Publication of EP1630123B1 publication Critical patent/EP1630123B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B66F9/12—Platforms; Forks; Other load supporting or gripping members

Definitions

  • the present invention relates to an industrial truck with at least one elongate load-receiving means and a load-carrying means supporting support structure, wherein the load receiving means is connected to the support structure and is pivotable about a pivot axis relative to the support structure between a use position and non-use position, wherein the load-receiving means in the position of use supported on the support structure.
  • the pivot axis is usually arranged in relation to the at least one load receiving means that holds the load-carrying means due to its own weight in a position of use.
  • the pivot axis of the load-receiving means is arranged offset from the longitudinal center, so that a front part of the load-receiving means, which is located in front of the pivot axis, is longer than a rear part, which is supported on the support structure of the truck. Due to the longer front part, a bearing torque is generated about the pivot axis, so that the rear part of the load-receiving means can be supported on a support on the support structure, and the load-receiving means is held in this position.
  • Such a truck is in the DE 94 11019 U1 discloses which corresponds to the preamble of independent claim 1.
  • the load-carrying means Since the load-carrying means is supported only on the support structure, it can be temporarily deflected out of the supported position of use, for example when driving over bumps with the truck. After this deflection, the load-receiving means moves back into the use position due to the bearing torque described above, wherein the rear part of the lifting device strikes against the support of the support structure. On the one hand noise, and on the other hand, the blow or be the Blows transferred to the support structure, which may affect the stability of the support structure over a long period of time and repeated impacts.
  • the object is achieved by a generic industrial truck, in which on the load-receiving means and / or on the support structure, a damping arrangement is provided which has at least one elastic damper element. Due to the elasticity of the damper element, this deforms when striking the load-carrying means, whereby this is braked over a short period of time, but not jerky. This leads to lower force peaks in the support structure and also to a softer impact with reduced noise.
  • the damping arrangement comprises at least one substantially rigid element, preferably a steel element, with which the damper element is firmly connected, such as by gluing or vulcanization, and which can be arranged or arranged on the support structure and / or the load receiving means.
  • the rigid element which can also be referred to as a support element of the damper element, has such a high deformation stiffness in comparison with the damper element that deforms upon impact of the load-receiving means on the damping arrangement, the rigid element in comparison with the elastic damper element to a negligible extent.
  • the damping arrangement preferably comprises at least one spacer element which can be arranged or arranged between the damper element and the substrate supporting it, preferably between the rigid element and the substrate carrying the damping arrangement.
  • the spacer elements can be advantageously used, particularly when retrofitting an industrial truck with a damping arrangement according to the invention, if, for example, the elastic damping element is provided with the rigid carrier element as a standard component.
  • the damping arrangement may have at least one attachment geometry.
  • the damping arrangement with its side edges in a corresponding holder on the ground can be inserted or snapped.
  • the at least one attachment assembly may extend as a recess, for example, in a U-shape from a side edge of the damping assembly to the interior thereof, allowing the damping assembly to pass through the side opening of the recess to corresponding mold members attached to the support structure and / or the load handler can be arranged, inserted and attached.
  • a holding the damping assembly screw needs to be only slightly rotated.
  • the recess may at least partially surround a screw shank in the mounted state of the damping arrangement, so that the damping arrangement can be securely held by the clamping force of a screw on the ground.
  • the attachment geometry is a passage which can be penetrated by a fastening means, such as a screw, so that the damping arrangement can be fixed captive on the supporting ground.
  • the passage can, for example, as a slot be educated.
  • the attachment geometry is a bore which extends through the damping arrangement.
  • the fastening recess may comprise at least two successive recess sections in the direction of a support surface supporting the damping arrangement, of which the lower recess section has a larger inside width than the lower section of the recessed section.
  • the inside width represents the distance between two opposite walls bounding the recess section, wherein the clear width corresponds to the diameter of this bore, for example, in the case of a bore.
  • a fixing portion of a fastener such as the head of a screw, be included, so that the fixing portion in the assembled state of the damping assembly securely closer to the ground as a bearing surface of the damper element, on which rests the load receiving means or the support structure in operation .
  • the fixing section can then exert a holding force on the lower-surface recess section and thus hold the damping arrangement positively or even positively against the ground.
  • both the designated undercampusereherere recess portion and the designated undergroundfernere lie Recess section in the rigid support member, since this is better than the damper element due to its rigidity, to absorb fastening forces.
  • this is not intended to exclude that at least the lower sub-recessed portion may extend into the damper element.
  • the lower and lower recess sections are formed with the designated different clearances as a reduction, so that the sauvigereherere recess portion is penetrated by a screw shaft, while the undergroundfernere recess portion receives a screw head.
  • a countersink as this allows the use of screws with flat heads, so that the screw head hardly protrudes into the region of the damper element when it rests against the countersink in the support element, so that the damper element for receiving impact forces the largest possible deformation is available.
  • the recessed portions described above should also include the case that in the support member only a countersink, d. H. without a subsequent cylindrical portion is formed.
  • the larger opening of the countersink is to be understood as the recess portion with the larger clear width and the smaller countersink opening than the recess portion with the smaller clear width in the context of the present application. Then, the lower-surface recessed section passes steplessly into the lower-surface recessed section with a smaller clear width.
  • the damping assembly is preferably mounted on the support structure.
  • the distance between nearest edges of fastening recesses is preferably set such that it is greater than the width of the load-receiving means.
  • the mounting recesses are also freely accessible when the load-carrying means is supported in the position of use on the support structure.
  • the damper element is made of plastic, preferably of an elastomer, such as rubber.
  • the material of the damper element may be more or less elastic, ie have a larger or smaller modulus of elasticity.
  • the damping arrangement it is also conceivable for the damping arrangement to have several Having damper elements with different elastic material properties.
  • a distance between a footprint of the truck and an underside pointing towards the footprint of the load receiving means at least partially increased to at least one longitudinal end, preferably to both longitudinal ends of the load receiving means.
  • the section with the change in distance preferably contains a longitudinal end, particularly preferably both longitudinal ends, of the load receiving means.
  • the increase in the distance between the footprint of the industrial truck and the bottom surface facing the footprint of the lifting device is particularly useful in a rear portion of the lifting device, in which the load receiving means as described above rests on the support structure, as when driving over bumps with the truck small deflection of the lifting device can take place.
  • Increasing the distance to the footprint prevents the underside of the rear portion of the load handler from striking the ground during a deflection from the use position so that damage to the load-bearing member as well as to the ground or the footprint can be prevented.
  • a load handling device 10 is in Fig. 1 shown in a solid line in its position of use.
  • a top 12 is supported at a support point 14 of a schematically indicated support structure 16, wherein the load-receiving means 10 by means of a rotatable hinge 18, which, for example, arranged on a connector 20 sleeve 22 and a lying therein, not shown on one Area of the support structure 16 fixed hinge pin 24 comprises, is stored.
  • the load-receiving means 10 can by the by the bolt 24 is substantially orthogonal to the longitudinal direction L of the load-receiving means 10 and orthogonal to the plane of the Fig. 1 extending pivot axis SA are pivoted.
  • the load receiving means 10 In a non-use position of the load receiving means 10, which is shown as a dashed line, the load receiving means 10 is pivoted such that it is substantially orthogonal to the position of use. It should be noted that due to the relative to the longitudinal axis of the load receiving means 10 not centrally arranged joint 18, a torque M acts, which normally causes a pivotal movement of the load receiving means 10 in the position of use. Consequently, the load-carrying means 10 must be secured in the non-use position by means not shown holding devices.
  • the load-receiving means 10 When using the conveyor, the load-receiving means 10 is briefly moved, for example, when driving over bumps from the use position into a deflection position shown in phantom. In this case, the load-receiving means 10 pivots in the direction of the arrow S, whereby a front portion 26 of the load-lifting means is raised and a rear portion 28 of the load-receiving means 10 is lowered. Since the deflection takes place only briefly in the deflection position due to the restoring effect of the torque M, the load-receiving means 10 strikes in its rear section 28 with the upper side 12 against the support point 14 of the support structure 16.
  • a distance a between an underside 30 of the lifting device 10 and the footprint of the truck AF increases to the respective associated longitudinal ends out, which by a wedge-shaped design of Sections 26 and 28 is achieved.
  • Fig. 2 is a simplified perspective view of the in Fig. 1 schematically illustrated support point 14, wherein the viewing direction is selected from below obliquely.
  • the support structure 16 in this illustration shows a movable lifting frame 32, which is movable along a fixed lifting stand 34.
  • a movably mounted on the movable lifting frame 32 fork carriage 36 is displaceable along the lifting frame 32 together with the load receiving means 10 and a mounted on the fork carriage 36 damping arrangement 38.
  • the damping arrangement 38 comprises a substantially rigid element or carrier element 40 facing the fork carrier 36 and resting against it, with which an elastic damping element 42 is fixedly connected. An end portion of the upper surface 12 of the load receiving means 10 is supported on the elastic damper element 42, which is the in Fig. 1 described use position corresponds.
  • the damping arrangement 40 is fastened to the fork carrier 36 by means of two screw connections, wherein only one opening or bore 44 of a first screw connection is shown. Moves the truck over a bump, is caused by the deflection of the load receiving means 10 between the damper element 42 and the top 12 of the load receiving means 10 briefly a small distance. Upon return of the load receiving means 10 in the position of use, the top 12 of the load-bearing element 10 strikes again on the elastic damper element 42, wherein the damper element 42 attenuates the impact on the fork carriage 36 and hereby on the entire support structure 16 and greatly reduces the noise development.
  • Fig. 3a shows a damping assembly 38 with the rigid member or support member 40 and the associated elastic damper element 42.
  • the elastic damper element 42 may be made of plastic, such as rubber, polyurethane, silicone-based plastic or the like, wherein the damper element 42 in comparison to the carrier element 40 characterized by a lower modulus of elasticity, for example by a factor of 15-25 lower modulus of elasticity, whereby at a Striking the top 12 of the load receiving means 10 on the Dämfpungsan angel 38 substantially the damper element 42 is deformed and the support member 40 is befomt only to a negligible extent.
  • the distance c between the two bores 44 measured between nearest inner edges of the bores 44 is chosen such that it is greater than the width b of the load-receiving means 10.
  • Each bore 44 is arranged at substantially the same distance d from the edge of the load-receiving means 10.
  • Fig. 3b illustrated cross-section along the line III-III of Fig. 3a has on its base with respect to the figure orientation on the elastic damper element 42, which is connected to the overlying rigid element 40.
  • the two openings 44 show in cross-section that they are formed in the region of the damper element 42 as a cylindrical bore 46 and in the region of the rigid element 40 as a countersink 48.
  • a spacer element 43 is shown, which is arranged on the carrier element 40.
  • the spacer element has holes 45, in which an unillustrated screw shaft can be accommodated.
  • the formation of the bore 44 is in Fig.

Landscapes

  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Vibration Dampers (AREA)
  • Forklifts And Lifting Vehicles (AREA)

Claims (12)

  1. Chariot de manutention avec au moins un moyen de réception de charge (10) oblong, et une structure porteuse (16) soutenant le moyen de réception de charge (10), ledit moyen de réception de charge (10) étant relié à la structure porteuse (16) et pivotant par rapport à la structure porteuse (16) autour d'un axe de pivotement (SA), entre une position d'utilisation et une position de non-utilisation, ledit moyen de réception de charge (10) s'appuyant contre la structure porteuse (16) en position d'utilisation, caractérisé en ce que
    un dispositif amortisseur (38) est prévu sur le moyen de réception de charge (10) et/ou sur la structure porteuse (16), lequel comporte au moins un élément élastique d'amortissement (42), et en ce que le dispositif amortisseur (38) comprend au moins un élément essentiellement rigide (40) au moyen duquel l'élément d'amortissement (42) est fixement raccordé, et qui est disposable ou disposé contre la structure porteuse (16) et/ou le moyen de réception de charge (10).
  2. Chariot de manutention selon la revendication 1, caractérisé en ce que l'élément rigide (40) est en acier.
  3. Chariot de manutention selon la revendication 1 ou 2, caractérisé en ce que l'élément rigide (40) est raccordé par collage ou par vulcanisation à l'élément d'amortissement (42).
  4. Chariot de manutention selon l'une des revendications 1 à 3, caractérisé en ce que le dispositif amortisseur (38) comprend en outre au moins un élément d'écartement (43) disposable ou disposé entre l'élément d'amortissement (42), de préférence entre l'élément rigide (40) et le substrat (10) supportant le dispositif amortisseur (38).
  5. Chariot de manutention selon l'une des revendications précédentes, caractérisé en ce que le dispositif amortisseur (38) comporte au moins une géométrie de fixation (44).
  6. Chariot de manutention selon la revendication 5, caractérisé en ce que la géométrie de fixation (44) est un évidement de fixation, comprenant au moins deux parties d'évidement (46, 48) se succédant vers une base supportant le dispositif amortisseur (38), dont la partie d'évidement (46) la plus distante de la base présente une largeur intérieure supérieure à celle de la partie d'évidement (48) la plus proche du substrat.
  7. Chariot de manutention selon la revendication 5 ou 6, caractérisé en ce que l'espacement (c) entre les évidements de fixation (44) est supérieur à la largeur (b) du moyen de réception de charge (10).
  8. Chariot de manutention selon l'une des revendications précédentes, caractérisé en ce que le dispositif amortisseur (38) est appliqué contre la structure porteuse (16).
  9. Chariot de manutention selon l'une des revendications précédentes, caractérisé en ce que l'élément d'amortissement (42) est en matière synthétique.
  10. Chariot de manutention selon la revendication 9, caractérisé en ce que l'élément d'amortissement (42) est produit à partir d'un élastomère.
  11. Chariot de manutention selon l'une des revendications précédentes, caractérisé en ce qu'une distance (a) entre une surface de contact au sol (AF) du chariot de manutention et une face inférieure (30) du moyen de réception de charge (10) opposée à la surface de contact au sol (AF) est au moins agrandie partiellement vers au moins une extrémité longitudinale (28) du moyen de réception de charge (10).
  12. Chariot de manutention selon la revendication 11, caractérisé en ce que la distance (a) entre la surface de contact au sol (AF) du chariot de manutention et la face inférieure (30) du moyen de réception de charge (10) est agrandie vers les deux extrémités longitudinales (26, 28) du moyen de réception de charge (10).
EP05018066A 2004-08-20 2005-08-19 Chariot élévateur avec un amortisseur pour les fourches Expired - Fee Related EP1630123B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004040529A DE102004040529A1 (de) 2004-08-20 2004-08-20 Flurförderzeug mit Gabeldämpfer

Publications (3)

Publication Number Publication Date
EP1630123A2 EP1630123A2 (fr) 2006-03-01
EP1630123A3 EP1630123A3 (fr) 2006-12-20
EP1630123B1 true EP1630123B1 (fr) 2008-11-05

Family

ID=35385912

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05018066A Expired - Fee Related EP1630123B1 (fr) 2004-08-20 2005-08-19 Chariot élévateur avec un amortisseur pour les fourches

Country Status (4)

Country Link
US (1) US20060055132A1 (fr)
EP (1) EP1630123B1 (fr)
CN (1) CN100584739C (fr)
DE (2) DE102004040529A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015114564A1 (de) * 2015-09-01 2017-03-02 Jungheinrich Aktiengesellschaft Flurförderzeug

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1567331A (en) * 1922-04-14 1925-12-29 Baker R & L Company Industrial truck
US2956701A (en) * 1958-06-06 1960-10-18 Int Harvester Co Stringer impact device for fork type lift trucks
US3080080A (en) * 1961-07-20 1963-03-05 Paul O Miller Shock absorbing attachment for fork lift trucks
US3272287A (en) * 1964-08-18 1966-09-13 Jimmy D Worthey Materials handling apparatus
DE1893487U (de) * 1963-09-17 1964-05-21 Siemens Elektrogeraete Gmbh Gabelhubgeraet mit gabelzinken.
US3232380A (en) * 1963-11-22 1966-02-01 Elmer K Hansen Fork and carriage assembly for lift vehicles
FR1504813A (fr) * 1966-10-28 1967-12-08 Nodet Gougis Surface de stockage permettant la manutention sans palette
US3559828A (en) * 1967-02-07 1971-02-02 Miles Druce & Co Ltd Method of removing stack from a warehouse with a lift truck
FR2085472A1 (fr) * 1970-04-24 1971-12-24 Guichard Jean
DE2049414C3 (de) * 1970-10-08 1974-08-29 O & K Orenstein & Koppel Ag, 1000 Berlin Stoßdämpfende Federung eines Hubschlittens für Hublader
DE3318388C2 (de) * 1983-05-20 1985-04-04 Carl Falkenroth Söhne GmbH & Co KG, 5885 Schalksmühle Traggabel für insbesondere Hubstapler
DE3340286C1 (de) * 1983-11-08 1985-05-15 Carl Falkenroth Söhne GmbH & Co KG, 5885 Schalksmühle Gabeltraeger fuer insbesondere Hubstapler
US5230600A (en) * 1991-12-12 1993-07-27 Salvatore Marino Attachment for lift trucks
CN2194351Y (zh) * 1993-05-27 1995-04-12 广东玻璃厂职工技术协作服务部 二吨叉车倾翻装置
US5560451A (en) * 1993-11-18 1996-10-01 Venture U.S.A. Incorporated Forklift vehicles
DE9411019U1 (de) * 1994-07-04 1994-09-01 Max Boll Maschinen- und Stahlbau GmbH, 79585 Steinen Ladegabel zur Befestigung an einer Hubeinrichtung an einem Schlepper, Gabelstapler o.dgl.
DE19615535C2 (de) * 1996-04-19 2003-04-30 Vetter Umformtechnik Gmbh Gabelzinken
EP1015377A4 (fr) * 1997-05-02 2002-02-13 Southland Sod Farms Mecanisme permettant de replier et de deployer des fourches de chariot elevateur
US6632064B1 (en) * 2001-06-29 2003-10-14 American Container And Recycling, Incorporated Method and apparatus to mitigate noise during unloading of refuse containers

Also Published As

Publication number Publication date
DE102004040529A1 (de) 2006-02-23
DE502005005865D1 (de) 2008-12-18
EP1630123A3 (fr) 2006-12-20
CN1737403A (zh) 2006-02-22
CN100584739C (zh) 2010-01-27
EP1630123A2 (fr) 2006-03-01
US20060055132A1 (en) 2006-03-16

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