EP0099467A2 - Chariot élévateur à fourche transversale - Google Patents

Chariot élévateur à fourche transversale Download PDF

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Publication number
EP0099467A2
EP0099467A2 EP83105751A EP83105751A EP0099467A2 EP 0099467 A2 EP0099467 A2 EP 0099467A2 EP 83105751 A EP83105751 A EP 83105751A EP 83105751 A EP83105751 A EP 83105751A EP 0099467 A2 EP0099467 A2 EP 0099467A2
Authority
EP
European Patent Office
Prior art keywords
axle
frame
presses
steering
press
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP83105751A
Other languages
German (de)
English (en)
Other versions
EP0099467A3 (en
EP0099467B1 (fr
Inventor
Walter Schüssler
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.)
ALBERT IRION NACHFOLGER
Original Assignee
Kalmar Irion Vierwege- und Querstapler GmbH
Irion and Vosseler Zaehlerfabrik GmbH and Co
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 Kalmar Irion Vierwege- und Querstapler GmbH, Irion and Vosseler Zaehlerfabrik GmbH and Co filed Critical Kalmar Irion Vierwege- und Querstapler GmbH
Priority to AT83105751T priority Critical patent/ATE23514T1/de
Publication of EP0099467A2 publication Critical patent/EP0099467A2/fr
Publication of EP0099467A3 publication Critical patent/EP0099467A3/de
Application granted granted Critical
Publication of EP0099467B1 publication Critical patent/EP0099467B1/fr
Expired legal-status Critical Current

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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
    • B66F9/07586—Suspension or mounting of wheels on chassis

Definitions

  • the invention relates to a cross forklift truck with a U-shaped frame in plan view, between the legs of which a lifting mast which can be extended laterally with a carriage is arranged, and with a chassis which contains a steering axis and a driving axis, each of which has vertical axes on both sides of the vehicle's longitudinal axis Supports are provided for the frame, of which at least one is a double-acting hydraulic press on the steering axle and the driving axle
  • Cross-type forklifts of this type are designed and constructed in such a way that the overall center of gravity, which results from the weight of the vehicle frame and body and the maximum load absorbed, lies approximately in the longitudinal plane of the vehicle. Since the center of gravity of the load inevitably comes to lie laterally offset with respect to the median longitudinal plane of the vehicle, the center of gravity of the vehicle body without load on the side of the median plane of the vehicle facing away from the direction of travel of the lifting mast is also offset relative to the latter. This results in different positions of the respective center of gravity, which lead to different wheel pressures, depending on the loading condition of the cross-truck.
  • a three-point support of the frame is provided on the chassis, with one support point each above the steering axis and the driving axis, while a third, imaginary support point between the steering axis and the driving axis in the connecting line between the two on this side of the forklift is arranged double-acting hydraulic presses, which are connected in parallel.
  • the invention has for its object to provide a cross forklift of the type mentioned so that a Gün term wheel pressure distribution with respect to the drive axle is guaranteed in all load ranges.
  • This object is achieved in that the hydraulic presses can be switched depending on the loading condition for changing the overall support of the frame on the steering axle and the driving axle in such a way that the supports on the vehicle side facing away from the extension direction of the lifting mast are rigid supports for empty travel and low-load journeys are and the opposite second support of the steering axle is rendered ineffective, and that for journeys with greater load and for full load driving, the presses of the steering axle and the driving axle located on the same side of the vehicle are connected in parallel and the opposite second support of the steering axle is a rigid support.
  • the invention is based on the knowledge that only one change g run the total support between frame and chassis to a günsti - Geren R addruckverander with respect to the driving axle in all load conditions can result, which is achieved by an appropriate circuit of the hydraulic presses.
  • a forklift truck with a steering axle and drive axle designed as pendulum axles which are provided with rigid supports in the vertical direction on the side opposite the extension direction of the slide and on the other side with parallel-acting double-acting hydraulic presses
  • the Press assigned to the drive axle can be blocked by the hydraulic circuit and the press assigned to the steering axle can be emptied by the hydraulic circuit.
  • This switchover ensures that the frame is supported on one side only eccentrically to the longitudinal axis of the vehicle relative to the steering axis and that two further rigid support points lie above the drive axis, so that this drive axis is rigidly connected to the frame.
  • the hydraulic press assigned to the steering axle is deactivated in this circuit so that it is then not involved in supporting the frame with respect to the chassis.
  • a cross-lift truck according to the invention with a steering axle and drive axle designed in the manner of pendulum axles, the steering axle and the drive axle on the side facing the direction of extension of the carriage with rigid supports in the vertical direction and on the opposite side with double-acting hydraulic Presses are supported, it is provided that a further double-acting hydraulic press is used as a rigid support of the steering axle, wherein by means of the hydraulic circuit in an operating state up to a certain load this further press is emptied and the other two presses are blocked, and in another operating state with greater load the other press is blocked and the other two presses are connected in parallel.
  • this further press is emptied and the other two presses are blocked, and in another operating state with greater load the other press is blocked and the other two presses are connected in parallel.
  • the cross forklift trucks shown in Fig. 1 to 4 basically have the same structure and differ only in the suspension of the chassis.
  • the transverse forklifts have a U-shaped frame in plan view, between the legs 17 and 18 of which a lifting mast 9 can be extended to the side with a carriage, not shown, which carries a load fork 19.
  • the lifting mast 9 can be completely retracted together with the load fork 19 into the frame 1 of the forklift.
  • the load picked up or released by the load fork is deposited on the legs 17 and 18 during the process.
  • the frame On the side facing away from the load fork, the frame is provided with a driver's cab in the area of a front corner point in a manner not shown.
  • the 1 and 2 contains a steering axle 2 with two steered wheels 13 and 16 and a drive axle 3 with the drive wheels 14 and 15.
  • the drive axle 3 is designed as a pendulum axle, which with a self-aligning bearing, the one has in the longitudinal direction of the axis of rotation, mounted on the frame.
  • This self-aligning bearing 20 is located relatively close to the load-side drive wheel 15.
  • the oscillating axis is additionally supported on the frame 1 by a hydraulic press 7.
  • the vertical forces are absorbed by the hydraulic press 7 and the self-aligning bearing 20, while all other forces, such as horizontal forces, lateral forces and torsional forces, are absorbed by the self-aligning bearing 20 alone.
  • a drive motor is provided in a manner not shown, which is connected in a known manner to the drive wheels 14 and 15 via a gear and a differential.
  • the steering axle 2 consists of an axle body on which the steered wheels 13 and 16 are arranged so as to be pivotable about vertical axes.
  • the axle beam is in the vicinity of the steered wheels 13 and 16 via two double-acting hydraulic presses 6 and 8 in a vertical direction tion supported on the frame 1 under the leg 17.
  • the longitudinal forces, transverse forces and torsional forces are absorbed by longitudinal links 11 and a transverse link, not shown in FIGS. 1 and 2, which will be described in more detail later in connection with FIGS. 5 and 6.
  • the frame 1 is thus supported below the leg 17 on the steering axle 2 and below the leg 18 on the driving axle 3.
  • the double-acting press 8 on the side facing the extension direction of the mast 9 and thus on the load side is blocked, i.e. blocked against the supply or discharge of pressure medium, so that a rigid connection at the point of the press 8 between the steering axis 2 and the frame 1 is given.
  • the working spaces of the presses 6 and 7, which are arranged on the side facing away from the load, are connected in parallel with one another. For this purpose, their working spaces are hydraulically connected to one another, as will be explained in more detail later with reference to FIG. 8.
  • an imaginary support point B is thus formed between the frame 1 and the chassis.
  • the exact position of the support point B is determined by the ratio of the piston surfaces of the presses 6 and 7 and can therefore be selected in terms of design.
  • the self-aligning bearing 20 forms a further rigid support between the driving axis B and the frame 1.
  • the support is changed by switching the presses 6, 7 and 8, so that there is a support according to FIG. 2 ...
  • the double-acting press 8 becomes emptied, ie both working spaces are opened to a tank, as will be described in more detail with reference to FIG. 8.
  • the presses 6 and 7 are separated and blocked, so that they become rigid supports.
  • the steering axis 2 thus becomes a kind of pendulum axis which is rigidly supported on the frame 1 by the press 6. Since the blocked press 7 also results in a rigid support, the drive axis 3 is connected to the frame 1 in a completely rigid manner.
  • the drive wheels 14 and 15 thus form support points E and F for the frame on the road.
  • a third support point D is formed by the press 6 on the steering axle 2.
  • the extended connecting line between the press 6 and thus the support point D and the center of gravity S 1 in the unloaded state runs approximately through the longitudinal center of the driving axle 3, so that a uniform distribution of the wheel pressure is ensured when the vehicle is unladen.
  • the focus S 1 lies at a clear distance from the connecting lines D, E and D, F, which are to be regarded as tilting lines. This type of support also results in very high cornering stability.
  • the existing three-point support according to FIG. 2 offers advantages not only when the forklift is unladen, but also over a relatively large load range.
  • a switchover to the support according to FIG. 1 can expediently be carried out in the range between 50 and 70% of the maximum load. The exact values depend on the exact location of the focal points S 1 and S 2 , which result from the design.
  • the switch between the two types of support according to FIGS. 1 and 2 can be carried out by the operator by hand or can be controlled automatically via an additional device which detects the load condition.
  • a switchover device 10 ensures that the type of support according to FIG. 1 is always present between the frame and the undercarriage when the mast 9 is extended laterally.
  • the switching device which can be an electrical switch, for example, is arranged between the frame 1 and the lifting mast 9 or the carriage, not shown, that a forced switching to the support type according to FIG. 1 always takes place when the lifting mast is extended laterally becomes. Switching to the type of support according to FIG. 2 is only possible when the lifting mast 9 is at least approximately completely retracted.
  • the steering axis 4 and the driving axis 5 are designed as real pendulum axles, which have self-aligning bearings 21 and 22 on the side facing away from the load, that is to say the side opposite the extension direction of the slide, between the steering axis 4 and the frame 1 and between the drive shaft 5 and the frame 1 are arranged.
  • These self-aligning bearings 21 absorb the vertical, longitudinal, transverse and torsional forces.
  • the steering axle 4 and the driving axle 5 are additionally supported on the load-facing side with double-acting hydraulic presses 6 and 7 with respect to the frame 1, the working spaces of which are hydraulically connected to one another, so that these two presses 6 and 7 are connected in parallel.
  • the type of support according to FIG. 3 ensures a good distribution of the wheel pressure to the drive wheels 14 and 15 at maximum load, in which an overall center of gravity S 2 is established close to the longitudinal center plane of the vehicle.
  • the center of gravity S 1 of the body is at a relatively large distance from the body when the cross-truck is not loaded Longitudinal center plane of the vehicle, so that an unfavorable wheel pressure distribution also arises here.
  • a special circuit for the hydraulic presses 6 and 7 is also provided here, so that it is possible to switch to the type of support according to FIG Support type according to Fig. 2 is identical.
  • the double-acting press 6 is emptied, so that the steering axle 4 is supported alone in the self-aligning bearing 21 at point K.
  • the press 7, on the other hand, is blocked so that it forms a rigid support between the driving axis 5 and the frame 1. 2 there is a rigid support of the drive axle on both sides by means of the self-aligning bearing 22 and the press 7 and a rigid support in the self-aligning bearing 21 of the steering axle 4.
  • This results in a support in the three points K, L and M. which corresponds to the support in points D, E and F according to FIG. 2.
  • the presses 6, 7 and 8 of the two embodiments open up additional adjustment options with which it is possible to adapt to the existing conditions when picking up or when placing a load. It is possible to simultaneously supply or remove a pressure medium from the presses 6 and 8, while the supply to the press 7 is then interrupted. This makes it possible to raise or lower the frame 1 around the driving axis, so that it also moves accordingly turn the fork 19 and the mast 9. It is also possible, in the embodiment of FIGS. 1 and 2, to simultaneously supply or discharge the presses 6 and 7, so that the frame 1 is then pivoted about the connecting line of the load-side support points A and C, which leads to a corresponding inclination of the load fork 19 and the mast 9 leads.
  • the presses 6 and 7 arranged on the load side can be jointly raised or lowered by supplying or A b-feeding pressure medium, which leads to an inclination of the frame 1 around the connecting line of the support points G and H of the load away Side and thus leads to a corresponding inclination of the fork 19 and the mast 9.
  • FIG. 7 shows a construction of a suspension of the driving axle 3 for an exemplary embodiment corresponding to FIGS. 1 and 2.
  • the load-side drive wheel 15 is rigidly suspended on a part of the frame 1 below the leg 18.
  • the driving wheel 14, on the other hand, is movably attached to the frame 1 in the vertical direction and is supported in the vertical direction by a double-acting hydraulic press 7.
  • the hydraulic press 7 is articulated on a wheel carrier 23 which receives the drive wheel 14 and is supported by two longitudinal and transverse links 24 arranged one above the other in a parallelogram arrangement.
  • the plate-shaped longitudinal and cross members 24 are each mounted on the frame 1 and the wheel carrier 23 about horizontal axes 25 and 26 running transversely to the vehicle longitudinal direction. This results in an independent wheel suspension which arises with respect to the support of the drive axle on the frame speaking the drive axis 3 designed as a pendulum axis behaves.
  • the drive wheel 14 By blocking the double-acting hydraulic press 7 , the drive wheel 14 can also be rigidly connected to the frame 1.
  • a driving axis 5 for the exemplary embodiment according to FIGS. 3 and 4 can also be designed by means of a corresponding, mirror-image arrangement of the driving wheel 15 fixedly connected to the frame and the vertically movably suspended driving wheel 14.
  • the steering axle 2 is suspended on the frame 1 in addition to the double-acting hydraulic presses 6 and 8 via trailing arms 11 and at least one wishbone 12, which are shown in more detail in FIGS. 5 and 6.
  • DieLhackslenker 11 consist of at least three extending in the vehicle longitudinal direction of longitudinal struts 27 which are articulated to the axle of the steering shaft 2 and two T eilen28 of the frame 1 parallel to each other in a parallelogram arrangement.
  • a double-acting hydraulic press 12 serves as a control arm, which is arranged between a part 29 of the frame 1 and a holder 30 fastened to the axle body of the steering axle 2.
  • the hydraulic presses 6 and 8 and the trailing arms 11 are expediently or the like with all-round movable joints in the form of ball joints or universal joints. provided so that an additional adjustment by means of the hydraulic press 12 is given.
  • the frame 1 By supplying pressure medium into one of the two working chambers of the hydraulic press 12, the frame 1 can be pivoted relative to the steering axis 2 about an imaginary vertical axis lying in the region of the driving axis. This makes it possible to quickly and easily align the entire frame 1 and thus also the load fork 19 and the lifting mast 9 exactly parallel to a stack if it is not approached precisely.
  • the hydraulic presses 6 and 8 pivot by the angle m according to FIG. 5. With this design of the trailing arms 11 and the wishbones 12 according to FIG.
  • Fig. 8 a hydraulic circuit is shown, through which the switching of the support types according to Fig. 1 and 2 and the multiple pivoting of the frame relative to the chassis is possible.
  • a motor M drives a pump 32, which sucks in the hydraulic medium from a reservoir 33 and under pressure via a distributor 34, to which other consumers can be connected, via valves 35, 36, 37 to the individual presses 6, 7, 8 and 12 feeds.
  • the valves 35, 36, 37 which are designed as electromagnetically actuated multi-way valves, the supply of pressure medium is interrupted.
  • a valve 40 is arranged which interrupts the connection in the position shown and releases the connection in its second position.
  • the outflow of pressure medium from the working spaces of the press 7 is blocked, which is arranged on the side of the drive axis facing away from the load.
  • This press thus creates a rigid connection between the driving axle 3 and the frame 1.
  • the valve 37 controlling the feed to the presses 6 and 7 is also in the closed position, so that the working spaces of the double-acting press 6 are also closed to supply and discharge of pressure medium, ie the press 6 is blocked.
  • the working spaces of the press 8 are connected to the reservoir 33 in the position shown via a valve 41.
  • the press 12 serving as a wishbone is filled with pressure medium in both work spaces and blocked by the valve 35 in the position shown. 2, in which the driving axle is connected to the frame by two rigid supports, while the steering axis is connected to the frame 1 with a rigid support via the press 6 on the side facing away from the load is supported.
  • the two working spaces of the press 8 are short-circuited via the valve 41, so that they.
  • Fig. 8 thus corresponds to the type of support according to Fig. 2, in which the drive axle 3 is supported on the frame with two rigid supports and the steering axis 2 on the side facing away from the load via the press 6 also with a rigid support on the frame is supported.
  • valves 40 and 41 are actuated. This can be done manually or by a load-dependent actuation, which actuates the corresponding solenoid valves 40 and 41.
  • the valves 40 and 41 are switched from the position shown to the other position by the switching device 10. In this position, the respective working spaces of the presses 6 and 7 are connected to one another, while the working spaces of the press 8 are blocked via the valve 36.
  • the parallel presses 6 and 7 then form the support point B (Fig. 1), while the press 8 then a rigid Support point A forms.
  • valve 37 In order to tilt the frame around the axis formed by the two support points A and C, the valve 37 is actuated together with the valves 40 and 41. The presses 6 and 7 can then be raised or lowered, depending on the position of the valve 37.
  • valve 36 is switched in series with the valve 37, while the valve 4 is 0 then brought into the illustrated position in which the press is blocked. 7
  • the valve 41 connects the press 8 to the valve 36.
  • valve 35 is actuated, which acts on the press 12.
  • FIGS. 9 and 10 differs from the embodiment according to FIGS. 1 and 2 by a simplified construction of the steering axis 2. With the exception of the pivoting possibilities of the frame 1 with respect to the longitudinal axis of the vehicle, the same functions are obtained, so that this refers to the description the embodiment of FIGS. 1 and 2 can be referenced.
  • a longitudinal link 44 is rigidly attached to the axle body of the steering axle 2 and is located on the side facing the extension direction of the lifting mast 9, which is gimbally suspended on the frame.
  • trailing arms 11 are provided both on the axle body and on the frame 1 on the opposite side, which are articulated on both the axle body and the frame 1.
  • Double-acting hydraulic presses 6 and 8 are provided as vertical supports of the steering axle 2 to the frame, one of which, depending on the operating state, is blocked as a rigid support.
  • the steering axis 2 executes pendulum movements about pendulum axes 52 or 53, which run obliquely to the longitudinal direction of the vehicle and which are determined by the respective rigid support and the articulation point of the trailing arm 44 on the frame 1.
  • the hydraulic press 8 can be rendered ineffective, for example, in accordance with the hydraulic circuit shown in FIG. 13.
  • the two working spaces of the hydraulic press 8 are connected to a reservoir 51 via lines and a valve 46.
  • Check valves 47, 48, 49 and 50 are arranged in the lines in such a way that in the position of the valve 46 shown, the two working spaces of the press 8 are connected to one another, with a volume compensation corresponding to the volume of the piston rod also being made possible.
  • the hydraulic press 8 is free and ineffective in this position.
  • the working spaces of the hydraulic press 8 are separated from one another and also from the reservoir 51, so that the press 8 is blocked and acts as a rigid support.
  • the construction of the steering axle has been modified compared to the embodiment according to FIGS. 9 and 10 in that a longitudinal link 45 which is rigidly suspended on the axle body of the steering axle 2 and gimbally on the frame 1 on the extension direction of the lifting mast 9 is arranged opposite side, while additional, both on the axle body of the steering axle 2 and the frame gimbaled longitudinal link 11 are arranged on the opposite side.
  • This training corresponds in principle to Embodiment according to FIGS. 9 and 10 and thus also the embodiment according to FIGS. 1 and 2, but in the two different operating states (in FIG.
  • FIG. 11 Another principle has been implemented in the embodiment according to FIG. 11, with which the hydraulic press 8 can be rendered ineffective.
  • This principle can of course also be used in the embodiments according to FIGS. 1 and 2 and 9 and 10.
  • the hydraulic press 8 is not firmly connected to the axle body of the steering axle 2 in the embodiment according to FIG. 12, but rather is supported by a spherical plate 54 on the axle body, which expediently or the like with a corresponding bowl-shaped plate made of plastic. is provided, which is not shown.
  • the hydraulic press 8 When driving empty and driving up to about half the load, the hydraulic press 8 is rendered ineffective in that the piston is retracted and the spherical plate 54 is lifted off the axle body of the steering axle 2.

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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)
  • Vehicle Body Suspensions (AREA)
  • Body Structure For Vehicles (AREA)
EP83105751A 1982-07-22 1983-06-11 Chariot élévateur à fourche transversale Expired EP0099467B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83105751T ATE23514T1 (de) 1982-07-22 1983-06-11 Quergabelstapler.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3227398 1982-07-22
DE3227398A DE3227398A1 (de) 1982-07-22 1982-07-22 Quergabelstapler

Publications (3)

Publication Number Publication Date
EP0099467A2 true EP0099467A2 (fr) 1984-02-01
EP0099467A3 EP0099467A3 (en) 1984-06-06
EP0099467B1 EP0099467B1 (fr) 1986-11-12

Family

ID=6169051

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83105751A Expired EP0099467B1 (fr) 1982-07-22 1983-06-11 Chariot élévateur à fourche transversale

Country Status (3)

Country Link
EP (1) EP0099467B1 (fr)
AT (1) ATE23514T1 (fr)
DE (2) DE3227398A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0129082A1 (fr) * 1983-06-10 1984-12-27 Albert Irion Nachfolger Chariot élévateur à fourche latérale

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202012100213U1 (de) 2012-01-20 2013-04-23 Hubtex Maschinenbau Gmbh & Co. Kg Flurförderzeug
DE102017103024A1 (de) 2017-02-15 2018-08-16 Hubtex Maschinenbau Gmbh & Co. Kg Flurförderzeug

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE868963C (de) * 1951-02-15 1953-03-02 Miag Fahrzeugbau G M B H Feststellvorrichtung fuer die Pendelachsen von Kranfahrzeugen
GB910236A (en) * 1959-06-12 1962-11-14 Rudolf Hauser Improvements in and relating to side loading fork lift trucks
DE1431696A1 (de) * 1965-12-20 1969-01-02 Irion & Vosseler Flurfoerdergeraet
DE1906079A1 (de) * 1968-04-18 1969-10-23 Ernst Wagner Appbau Transportfahrzeug,insbesondere Hubstapler mit Pendelachse
DE1953112A1 (de) * 1969-10-22 1971-04-29 Irion & Vosseler Einrichtung fuer Seitenlader mit querverschiebbarem Hubmast
DE1954208B2 (de) * 1969-10-28 1973-04-05 Steinen, Kurt, 8560 Lauf Front- und seitenlader mit einem freitragend verschiebbaren und um eine vertikale schwenkachse schwenkbaren hubmast

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE868963C (de) * 1951-02-15 1953-03-02 Miag Fahrzeugbau G M B H Feststellvorrichtung fuer die Pendelachsen von Kranfahrzeugen
GB910236A (en) * 1959-06-12 1962-11-14 Rudolf Hauser Improvements in and relating to side loading fork lift trucks
DE1431696A1 (de) * 1965-12-20 1969-01-02 Irion & Vosseler Flurfoerdergeraet
DE1906079A1 (de) * 1968-04-18 1969-10-23 Ernst Wagner Appbau Transportfahrzeug,insbesondere Hubstapler mit Pendelachse
DE1953112A1 (de) * 1969-10-22 1971-04-29 Irion & Vosseler Einrichtung fuer Seitenlader mit querverschiebbarem Hubmast
DE1954208B2 (de) * 1969-10-28 1973-04-05 Steinen, Kurt, 8560 Lauf Front- und seitenlader mit einem freitragend verschiebbaren und um eine vertikale schwenkachse schwenkbaren hubmast

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0129082A1 (fr) * 1983-06-10 1984-12-27 Albert Irion Nachfolger Chariot élévateur à fourche latérale

Also Published As

Publication number Publication date
EP0099467A3 (en) 1984-06-06
DE3227398A1 (de) 1984-01-26
EP0099467B1 (fr) 1986-11-12
DE3367581D1 (en) 1987-01-02
ATE23514T1 (de) 1986-11-15

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