EP0474210B1 - Vertikal hebender Laderausleger - Google Patents

Vertikal hebender Laderausleger Download PDF

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Publication number
EP0474210B1
EP0474210B1 EP91114932A EP91114932A EP0474210B1 EP 0474210 B1 EP0474210 B1 EP 0474210B1 EP 91114932 A EP91114932 A EP 91114932A EP 91114932 A EP91114932 A EP 91114932A EP 0474210 B1 EP0474210 B1 EP 0474210B1
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EP
European Patent Office
Prior art keywords
lift arm
lift
main
link
links
Prior art date
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Expired - Lifetime
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EP91114932A
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English (en)
French (fr)
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EP0474210A1 (de
Inventor
Lonnie D. Hoechst
Orlan J. Loraas
Wally L. Kaczmarski
Larry E. Albright
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Doosan Bobcat North America Inc
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Clark Equipment Co
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/34—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with bucket-arms, i.e. a pair of arms, e.g. manufacturing processes, form, geometry, material of bucket-arms directly pivoted on the frames of tractors or self-propelled machines
    • E02F3/3405—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with bucket-arms, i.e. a pair of arms, e.g. manufacturing processes, form, geometry, material of bucket-arms directly pivoted on the frames of tractors or self-propelled machines and comprising an additional linkage mechanism
    • 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

Definitions

  • the present invention relates to loader boom assemblies for self-propelled loaders which are controlled to maintain the forward ends of the boom assembly in a generally vertically linear path throughout a substantial portion of the upward travel of the boom assembly.
  • Loader boom assemblies which provide a generally vertical movement of a bucket used for lifting material have been used.
  • U.S. Patent 4,355,946 illustrates a lift arm control linkage structure for a loader which uses a long lift arm support link at the rear portions of the loader boom assembly, to provide an altered upward path of a front bucket, and at the same time provides bucket leveling.
  • FR-E-85 419 shows a lift boom assembly with a pair of lift arms coupled together.
  • Retractable power actuators extend upwardly and rearwardly and are coupled to the first lift arm.
  • a control link is mounted at a position above one pivotal mounting of the power actuators. The second lift arm moves forwardly under control of the control link as the main lift arm first raises.
  • the object underlying the present invention is to provide a lift boom assembly with a working tool, wherein the shortening of the forward reach of the working tool of the boom assembly in a raised position is avoided.
  • the present invention relates to a boom assembly for a loader which comprises a pair of lift arms, each including a pair of articulated links which are controlled in movement as the lift arms are raised to cause the outer ends of the lift arms to move generally vertically and substantially linearly when the lift arms are raised beyond a horizontal position.
  • the articulated links of each lift arm include a main forwardly extending lift arm link or section and a rear, substantially shorter lift arm link or section which has one end pivoted to the main lift arm link or section and the other end pivoted to the self propelled loader frame.
  • the path of movement of the main lift arm sections is partially controlled by a control link that is connected to the self propelled loader frame at a forward end of the frame and to the lift arm main section of the respective lift arm.
  • the lift arms are raised by operating hydraulic cylinders or actuators which react forces between the main lift arm sections and the loader main frame.
  • the rear lift arm link first is controlled to pivot about its pivot at the main loader frame so as to move the other or first end of the rear link which is pivoted to the main lift arm link rearwardly under control of the control link.
  • a loader assembly indicated generally at 10, made according to the present invention, is mounted onto a skid steer machine or prime mover 12 that has a main frame 14 that extends longitudinally in fore and aft direction, and is supported suitably on front and rear wheels 16. Wheels 16 are driven in a suitable manner through a drive train supported on the main frame 14, from an engine (not shown) in an engine compartment 15 mounted directly behind an operator's compartment indicated schematically at 18. Frame uprights 20 at the rear portion of the main frame are used for supporting the loader 10. Each of the uprights 20 comprises a part of spaced apart plates.
  • the main frame 14, frame uprights 20, the drive wheel configuration, fenders 22, and wide operator's compartment 18 are all features of the standard skid steer loaders.
  • the operator's compartment extends laterally across the entire main frame.
  • the operator's compartment extends substantially the full width between the inner plates of frame uprights 20 and fenders 22 (see Figure 4).
  • the present articulated boom is designed to fit onto the basic construction of the main frame, uprights and wide cab while permitting the usual access to service the machine in the same manner.
  • An engine compartment 15 is immediately behind the compartment 18 and the engine access door or panel 15A can be opened in the same manner as on existing machines because of the lack of interference from the rear links 32 and clearance of cross member 36 due to use of high pivots 40.
  • Skid steer loaders of the general type shown herein are well known and are manufactured by the Melroe Company, a business unit of Clark Equipment Company of Fargo, North Dakota, and are marketed under the registered trademark BOBCAT.
  • the loader 10 includes a lift boom assembly 24, which is, in the preferred embodiment, a two section boom.
  • the two section boom includes a main lift arm assembly 26 and a rear lift arm link assembly 28, which are pivotally mounted together.
  • the main lift arm assembly 26 includes a pair of laterally spaced main lift arm links or sections 30, and a pair of rear or second lift arm links or sections 32.
  • the main lift arm links 30 are on opposite sides of the main frame connected with suitable cross members at the forward ends thereof, for example with a cross member shown at 34, and the spaced rear lift arm links 32 on opposite sides of the main frame are connected together with a suitable cross member 36.
  • the main lift arm assembly 26 has forward and rear ends, and at its rear end the main lift arm sections are each pivotally connected with suitable pivot pins 38, forming a pivot axis, to first ends of the rear lift arm links 32.
  • the connection is made so the main lift arm sections 30 and the rear lift arm links 32 lie on a common plane along the side of the operators compartment.
  • each of the rear lift arm links 32 is pivotally connected on suitable pins 40 forming a pivot axis to the respective frame uprights 20, adjacent the rear portions of the main frame 14, and at the upper portions of the upright and between the plates forming the respective frame uprights 20.
  • the axis of the pins 40, which define the pivoting axis of the rear lift arm link assembly is raised a substantial distance above a supporting surface indicated generally at 42.
  • the main lift arm sections 30 include downwardly extending forward arms 44 thereon, which extend downwardly and forwardly, just ahead of the forward wheels 16, with the lift boom assembly 24 in a lowered position.
  • an attachment pin 46 which defines a pivot axis for supporting a working implement.
  • the working implement is a bucket 48 that is supported on a subframe 50.
  • the subframe in turn is pivotally mounted on the pins 46, and is controlled by a tilt cylinder or actuator illustrated schematically at 52, in a conventional manner.
  • the tilt cylinder 52 is connected at its based end to a support 53 which is mounted on cross members 34.
  • the subframe 50 is an attachment frame that is sold by Melroe Company, a business unit of Clark Equipment Company, located at Fargo, North Dakota, under the trademark BOB-TACH.
  • any desired mounting for the implement or bucket 48 can be utilized, and in most instances there is a defined point such as the axis of pin 46 or the front lip of the bucket 48 that can be used for determining the path of movement of the forward ends of the main lift arms 30 during raising and lowering motion.
  • the main lift arm sections or links 30, have control arms 54 fixed thereto, at a location spaced forwardly from the pivot pin 38.
  • the control arms 54 are made of two spaced plates and extend downwardly along the sides of the operator's compartment 18, as can be seen, to a location just above the fenders 22.
  • Hydraulic actuator or cylinder attachment plate sections 56 are secured to the main lift arm section 30 on each side of the boom assembly in a suitable manner, or can be part of the plates forming control arms 54.
  • a separate double acting hydraulic actuator or cylinder assembly 58 is mounted on each of the sides of the main frame, and has a rod that is extendable and retractable.
  • the rod has a rod end that is connected with a suitable pin 60 between the respective spaced plates 56.
  • the base end of each actuator or cylinder 58 is connected with a suitable pin 62 to the main frame 14 and, as shown, is located between the plates forming uprights 20. It should be noted that the base end pin 62 for the double acting hydraulic actuator or cylinder 58 is substantially lower than the pivot pins 40.
  • the actuator extends upwardly and forwardly from the pivot pin 62 to pin 60.
  • a control link which in the form of the invention is a fixed length or rigid link, is indicated generally at 66.
  • Each of the links 66 has a forward end pivotally mounted with a suitable pin 68 to a bracket fixed on the respective fender 22 and thus to main frame 14 of machine 12.
  • the opposite end of the rigid link 66 is connected with a suitable pin 70 to an end of the respective control arm 54 on each of the main lift arm sections 30 and is positioned between the plates forming the respective control arm 54.
  • Each link 66 is substantially horizontal with the boom assembly 24 in its lowered position.
  • the horizontal links 66 are substantially parallel to the direction of rearward force and will tend to hold each of the individual main lift arm sections 30 and rear lift arm links 32 from rearward movement. Part of this rearward load of course will also be transferred through the pins 38 to the rear lift arm links 32 and thus to the pivot 40 on the frame uprights, but with the articulated lift arms, that is, two lift arm sections pivoted together, there would be a tendency to cause folding of the main lift arm sections and rear lift arm links from horizontal load vectors acting rearwardly against the pin 46.
  • the links 66, actuator 58, the main lift arm section 30, and the rear lift arm section or link on each side of the boom assembly lie in a common plane to save lateral space and to fit existing skid steer machines without reducing the width of the operator's compartment or increase the overall width of the machine.
  • the actuators or cylinder assemblies 58 can be operated using a valve and a source of hydraulic pressure (not shown) to raise the boom assembly 24 to a raised, dumping position. As the boom assembly raises, the path of travel of the axis of the pin 46, or front edge of the bucket will define a substantially vertical path throughout the upper part of the working range used for dumping of buckets. Referring to Figure 1, the boom assembly 24 is shown at its lowered position.
  • the path of movement of the pin 46 is illustrated, and after the pin 46 reaches a height above the support surface 42 substantially equal to the level of the pin 40 (as shown by a horizontal dashed line in Figure 3), instead of moving on an arc rearwardly at the same time that the lift arms are raised further, the axis of the pin 46 moves substantially vertically to the full raised position of the lift arms.
  • the tilt cylinder 52 can be operated as desired for tilting the subframe 50 and the bucket 48 about the axis of pins 46, in the usual manner. It also follows that in any particular tilted position of the bucket 48, each point of the bucket, such as the leading edge, will move along a path corresponding to the path of the axis of the pin 46.
  • the main lift arm section or link 30 and the rear lift arm section or link 32 on each side of the loader form an included angle between the center line of the rear link 32, between the axes of pivot pins 38 and 40, and the center line of the main lift arm section 30.
  • This included angle is represented by the double arrow 74.
  • the lift cylinder or actuator 58 is operated to start to raise the boom assembly 24 and, therefore, the bucket 48, the included angle represented at 74 will first decrease as the rear lift arm links 32 will be forced to move rearwardly by the rigid link 66, which pivots about pin 68 in an upward arc.
  • the control arm 54 positions the pivot pin 70 for the rear end of link 66 in a location such that rearward movement of the lift arm link 32 occurs as the arms swing.
  • Pin 46 then moves upwardly along a path 47 that is shown in Figure 3, and when the cylinder or actuator 58 has been extended to a point where the boom assembly 24 is about one-third of its total upward travel the included angle indicated by arrow 74 stops decreasing, and then starts increasing again as the two lift arm sections, comprising the main lift arm section or link 30 and the rear lift arm section or link 32 start to unfold as the end of link 66 moves forward on an arc.
  • the effective length of the boom assembly 24 from pivot pin 40 to the front end increases during the upper two-thirds of its upward travel to cause the vertical path of movement of the pin 46 and associated parts of the bucket.
  • the rigid control link 66 thus controls the path of pivotal movement of the pivot pin 38 as lift arm link 32 pivots about the pin 40.
  • the link geometry including the length of the link 66 to be of a substantial length, preferably longer than the rear lift arm link 32 and approximately twice the length of the rear lift arm link 32, and keeping rear lift arm link 32 much shorter than lift arm link or section 30, the desired path of travel of the pin 46 and bucket 48 can be achieved.
  • the same path of travel is followed when the lift arms are lowered, because the control link 66 is fixed in length.
  • the present boom assembly achieves the objective of having a longer reach in the upper portions of the path of movement of the boom assembly so that it is easier to dump a bucket into a truck, and also that it is easier to make a pile that is higher, while maintaining the advantages of having a high pivot boom point 40 that is present in existing skid steer loaders, improved lifting capacity, and still having a compact loader which is as maneuverable as the prior skid steer loaders.
  • the plane defined by the axes of pins 68 and 70 is above the axes of the pin 62 for the lift cylinders or actuators 58, and the pin 70 is rearwardly of the pin 68 so that from the generally horizontal position of link 66 with the boom lowered, the pin 70 will move upwardly and forwardly which will cause the rear link 32 to first move rearwardly.
  • the axis of pin 70 crosses a plane defined by the axis of pins 68 and 38 and goes "overcenter" as it raises.
  • the rigid link 66 will cause the rear or second lift arm links to start to move forwardly as the main lift arm sections are further raised, again causing the included angle indicated by arrow 74 to start to increase.
  • the effective length of the boom assembly comprising the main lift arm sections or links 30 and the rear lift arm links 32 increases as raising continues.
  • the link 66 could be made adjustable in length to suit individual conditions that are desired for the path of movement, and provide for different control paths of the pin 46.
  • the mechanical linkage illustrated herein provides the desirable vertical path of movement of the pin 46 when the bucket has been raised to a desired level. In other words, the bucket raised along a substantially vertical path after it has reached a desired level near the level of the pivot axis of pin 40.
  • the loader assembly with the short rear lift arm links, that are mounted on a high pivot improves the rigidity of the lift boom assembly 24 so the lift arms travel in a definite path with clearance maintained along the sides of the operator's compartment.
  • the rear lift arm links 32 mounted on the high pivot 40 to the frame uprights 20, provides a boom assembly having the benefits of an articulated boom without extending into the space needed for the rear engine compartment opening, so that there is good service access for the engine compartment. It does not extend rearwardly beyond the rear access door 15A of the engine compartment 15.
  • the articulated boom loader of the present invention has a large degree of commonality of basic frame and drive structure with conventional skid steer loaders.
  • the path of movement of the bucket 48, and the forward ends of the lift arms, as stated, is such that the rear lift arm links 32 move rearwardly upon initial lifting, as guided by the rigid links 66. This tends to move the bucket in a more vertical path initially, so that the bucket 48 and its load stay close to the front tires and front of the main frame 14 as the bucket is first lifted, rather than moving out on a radius.
  • the rearward movement of the rear lift arm links has important features in defining the initial lifting path of the bucket.
  • the present invention provides a vertical lift path in the range of movement of a loader boom where the reach of the boom normally is reduced. This permits the operation of the loader in filling trucks and piling material to proceed more easily.
  • the control linkage provides a positive and reliable control for obtaining the vertical path of movement.
  • the present invention provides a vertical lift path in the range of movement of a radial arc boom machine where the reach of the boom normally increases or moves forwardly.
  • This mechanical linkage system of providing both inward movement initially and increased reach near full lift height can be packaged on a conventional skid steer machine design. This maintains the existing features of machine design, production processes, and field service procedures in the areas of operator compartment, controls, engine, transmission, hydraulics and hydrostatics, cooling system, electrical system, service access features and means of connecting attachment tools to the skid steer machine.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • General Engineering & Computer Science (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Shovels (AREA)

Claims (11)

  1. Hubauslegeranordnung (24) für einen Lader auf einer Kraftmaschine (12) mit einem Längshauptrahmen (14) mit Hubarmstützen (20), die fest an dem Rahmen (14) an der Hinterseite des Hauptrahmens (14) angebracht sind, wobei die Hubarmstützen (20) obere Enden haben, einem Paar Hubarme (30, 32), die auf gegenüberliegenden Seiten des Rahmens angeordnet und zusammengekoppelt sind, wobei die Hubarme vordere Enden zum Befestigen eines Arbeitswerkzeugs und hintere Enden haben und das Paar Hubarme jeweils aufweist: ein erstes Haupthubarmglied (30), das von dem vorderen Abschnitt des Rahmens (14) nach hinten verläuft, und ein zweites Hubarmglied (32), das kürzer als das Haupthubarmglied (30) ist, mit einem ersten Ende, das schwenkbar an einem hinteren Ende des Haupthubarmglieds (30) befestigt ist, und mit einem zweiten Ende (40), das schwenkbar an einem jeweiligen oberen Ende der Hubarmstütze (20) befestigt ist, sowie ausfahrbaren und einziehbaren Kraftstellgliedern (58), die schwenkbar an dem Hauptrahmen (14) befestigt und jeweils mit dem Haupthubarmglied (30) gekoppelt sind, und einem Steuerglied (66), das mit mindestens einem Haupthubarmglied (30) verbunden ist, zum Steuern des Bewegungswegs von Schwenkzapfen (38) zwischen den Haupthubarmgliedern (30) und den jeweiligen zweiten Hubarmgliedern (32), wenn die Hubarme (30, 32) durch das Kraftstellglied (58) angehoben und abgesenkt werden, wobei das Steuerglied (66) ein erstes Ende hat, das schwenkbar an dem Hauptrahmen (14) angrenzend an vordere Abschnitte des Hauptrahmens (14) befestigt ist, und ein zweites Ende hat, das nach hinten verläuft und schwenkbar über einen zweiten Schwenkzapfen (70) mit dem jeweiligen Haupthubarmglied (30) verbunden ist, wobei sich der zweite Schwenkzapfen (70) des Steuerglieds (66) in einem Bogen bewegt, wenn die Hubauslegeranordnung (24) durch die Kraftstellglieder (58) angehoben wird, und sich das Steuerglied (66) über der Schwenkbefestigung (62) der Kraftstellglieder (58) an dem Hauptrahmen (14) befindet, gekennzeichnet dadurch, daß die Kraftstellglieder (58) nach oben und nach vorn von ihrer Schwenkbefestigung an dem Hauptrahmen (14) verlaufen, das zweite Hubarmglied (32) nach oben und nach vorn von seinem Schwenkzapfen (40) an der Hubarmstütze verläuft, und das Steuerglied (66) unter beiden Schwenkanordnungen (38, 40) der zweiten Hubarmglieder (32) positioniert ist, wenn sich die Hubarme (30, 32) in einer abgesenkten Position befinden, und sich der Schwenkzapfen (38) zwischen jedem Haupthubarmglied und seinem jeweiligen zweiten Glied (32) nach hinten unter Steuerung des Steuerglieds (66) bewegt, wenn sich die Haupthubarmglieder (30) zuerst anheben, und nachdem sie um einen vorbestimmten Betrag angehoben sind, sich der Schwenkzapfen (38) zwischen den Haupthubarmgliedern und den zweiten Gliedern nach vorn bewegt, wenn das vordere Ende (44) der Hubauslegeranordnung angehoben wird.
  2. Hubauslegeranordnung nach Anspruch 1, wobei jedes zweite Glied (32) einen ersten eingeschlossenen Winkel zu dem zugehörigen Haupthubarmglied (30) in einer abgesenkten Position bildet, und wobei das Steuerglied (66) bewirkt, daß sich der eingeschlossene Winkel (74) zuerst verringert, und nach Erreichen der vorbestimmten Position der Schwenkzapfen (70) an dem zweiten Ende des Steuerglieds (66) die Mitte gegenüber einer Ebene überschreitet, die durch die Schwenkzapfen an den ersten Enden der zweiten Glieder und das erste Ende (68) des Steuerglieds (66) gebildet ist, und der erste eingeschlossene Winkel (74) zunimmt.
  3. Hubauslegeranordnung nach Anspruch 1 oder 2, wobei das Steuerglied (66) schwenkbar an mindestens einem der ersten Haupthubarmglieder über einen zweiten Arm (54) befestigt ist, der an dem jeweiligen Haupthubarmglied (30) befestigt ist und den Schwenkzapfenpunkt (70) zwischen dem Steuerglied und dem jeweiligen Haupthubarmglied (30) von der Schwenkverbindung (38) zwischen dem Haupthubarmglied (30) und dem zweiten Glied (32) auf jeder Seite der Hubauslegeranordnung (24) im wesentlichen nach unten versetzt anordnet.
  4. Hubauslegeranordnung nach Anspruch 1, wobei die Haupthubarmglieder (30) und die zweiten Glieder (32), die die Hubarme bilden, in einer eingeklappten Position sind, wenn sich die Haupthubarmglieder in der abgesenkten Position befinden, das Steuerglied (66) länger als die zweiten Hubarmglieder (32) ist, und bei Bewegung der Haupthubarmglieder (30) durch die Kraftstellglieder (58) nach oben die Haupt- und zweiten Hubarmglieder (30, 32) zuerst zusammenklappen und anschließend aufklappen, wenn das Steuerglied (66) die Mitte gegenüber dem Schwenkzapfen des ersten Endes des Steuerglieds (66) und der Schwenkachse (38) zwischen den zweiten und Haupthubarmgliedern überschreitet, um zu bewirken, daß sich die vorderen Enden (44) der Haupthubarmglieder (30) auf einem im wesentlichen geradlinigen Aufwärtsweg bewegen, wenn die Hubauslegeranordnung (24) über die gewünschte Höhe angehoben wird.
  5. Hubauslegeranordnung nach Anspruch 1, wobei sich Steuerglieder (66) an jedem der Hubarme befinden, und das Kraftstellglied (58) und das Steuerglied (66) auf jeder Seite der Hubauslegeranordnung (24) in einer gemeinsamen Ebene sowie über einem Seitenabschnitt des Hauptrahmens (14) liegen.
  6. Hubauslegeranordnung nach einem der vorausgegangenen Ansprüche, wobei die Kraftstellglieder erste Enden (60) haben, die schwenkbar angrenzend an die hinteren Abschnitte des Hauptrahmens (14) an einer Position im wesentlichen unter den Schwenkzapfen (38) des zweiten Glieds (32) an dem Hauptrahmen (14) befestigt sind, sowie zweite Enden (62) haben, die schwenkbar mit den jeweiligen Haupthubarmgliedern (30) zwischen ihrer Schwenkverbindung (38) mit den zweiten Gliedern (32) und dem vorderen Ende (44) der Haupthubarmglieder (30) verbunden sind.
  7. Hubauslegeranordnung nach Anspruch 1, wobei das Steuerglied (66) schwenkbar an dem Hauptrahmen (14) in einer senkrechten Höhe im wesentlichen unter dem Schwenkzapfen (38) zwischen den zweiten Hubarmgliedern und den Hubarmstützen (20) befestigt ist und sich aus einer im wesentlichen waagerechten Position bewegt, wenn sich die Haupthubarmglieder (30) in einer abgesenkten Position befinden, und bei Bewegung der Haupthubarmglieder (30) nach oben bewirkt, daß die Haupthubarmglieder (30) und zweiten Hubarmglieder (32) relativ zueinander schwenken, um die effektive Länge des Bewegungsbogens der vorderen Enden der Haupthubarmglieder (30), gemessen zwischen dem Schwenkzapfen (40) der zweiten Hubarmglieder (32) an den Hubarmstützen (20) und den vorderen Enden der Haupthubarmglieder, zuerst zu verringern und danach zu erhöhen.
  8. Hubauslegeranordnung nach einem der Ansprüche 1, 2, 3, 5, 6 oder 7, wobei das Steuerglied (66) im wesentlichen doppelt so lang wie die zweiten Hubarmglieder (32) ist.
  9. Hubauslegeranordnung nach einem der Ansprüche 1, 4 oder 8, wobei das Steuerglied (66) im wesentlichen waagerecht ist, wenn sich die Hubauslegeranordnung in ihrer abgesenkten Position befindet.
  10. Hubauslegeranordnung nach Anspruch 1, wobei der zweite Schwenkzapfen (70) des Steuerglieds (66) unter einer Bezugsebene liegt, die durch Schwenkachsen (38) zwischen dem Haupt- und zweiten Hubarmglied (30, 32) und der Schwenkbefestigung (68) des ersten Endes des Steuerglieds (66) gebildet ist, wenn sich die Hubauslegeranordnung (24) in einer abgesenkten Position befindet, und wobei sich der zweite Schwenkzapfen (70) des Steuerglieds über die Bezugsebene bewegt, wenn die Hubauslegeranordnung (24) in eine angehobene Position bewegt wird.
  11. Hubauslegeranordnung nach Anspruch 8, wobei ein Paar Steuerglieder (66) vorhanden ist, die Steuerglieder (66) auf gegenüberliegenden Seiten einer Bedienerkabine (18) auf dem Hauptrahmen (14) liegen, die Steuerglieder (66) schwenkbar mit einem jeweiligen Hubarm (30, 32) verbunden sind, die Hubarme (30, 32) auf jeder Seite der Bedienerkabine (18) sowie die jeweiligen Steuerglieder (66) und Kraftstellglieder (58) sämtlich in einer senkrechten Ebene angrenzend an die Seiten des Hauptrahmens (14) ausgerichtet sind, um den verfügbaren Raum für die seitliche Breite der Bedienerkabine (18) zu maximieren und die Gesamtbreite der Hubauslegeranordnung (24) zu minimieren.
EP91114932A 1990-09-05 1991-09-04 Vertikal hebender Laderausleger Expired - Lifetime EP0474210B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US57764590A 1990-09-05 1990-09-05
US577645 1990-09-05

Publications (2)

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EP0474210A1 EP0474210A1 (de) 1992-03-11
EP0474210B1 true EP0474210B1 (de) 1996-10-30

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EP (1) EP0474210B1 (de)
JP (1) JP3133793B2 (de)
KR (1) KR0162497B1 (de)
BR (1) BR9103803A (de)
CA (1) CA2050565C (de)
DE (1) DE69122933T2 (de)

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USD832551S1 (en) 2017-10-12 2018-10-30 Clark Equipment Company Loader
USD832552S1 (en) 2017-10-12 2018-10-30 Clark Equipment Company Lift arm for loader
US10626576B2 (en) 2016-12-16 2020-04-21 Clark Equipment Company Loader with telescopic lift arm

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Publication number Priority date Publication date Assignee Title
GB9311770D0 (en) * 1993-06-08 1993-07-28 Bamford Excavators Ltd Loader vehicle
GB2278826B (en) * 1993-06-08 1997-01-22 Bamford Excavators Ltd Loader vehicles
KR100360347B1 (ko) * 1999-03-31 2002-11-13 대우종합기계 주식회사 로더용 리프트 붐조립체
US6854951B2 (en) 2000-09-26 2005-02-15 Komatsu Ltd. Vertical lift type arm device
JP4687152B2 (ja) 2005-03-09 2011-05-25 株式会社豊田自動織機 作業車両におけるリフトアーム装置、及びそれを備える作業車両
US8453785B2 (en) 2007-03-28 2013-06-04 Clark Equipment Company Lift arm assembly for a power machine or vehicle
JP5094649B2 (ja) * 2008-09-03 2012-12-12 株式会社クボタ ローダ作業機
JP5119094B2 (ja) * 2008-09-03 2013-01-16 株式会社クボタ ローダ作業機
CN112723251A (zh) * 2021-04-02 2021-04-30 山东工力机械有限公司 车载货物装卸叉车

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FR85419E (fr) * 1961-09-13 1965-08-06 Pelleteuse-chargeuse
US3215292A (en) * 1964-09-14 1965-11-02 Sperry Rand Corp Material handling apparatus-front lift type
FR1578437A (de) * 1968-02-07 1969-08-14
US4355946A (en) * 1980-09-29 1982-10-26 Deere & Company Lift arm and control linkage structure for loader buckets

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10626576B2 (en) 2016-12-16 2020-04-21 Clark Equipment Company Loader with telescopic lift arm
USD832551S1 (en) 2017-10-12 2018-10-30 Clark Equipment Company Loader
USD832552S1 (en) 2017-10-12 2018-10-30 Clark Equipment Company Lift arm for loader

Also Published As

Publication number Publication date
AU8359591A (en) 1992-03-12
DE69122933D1 (de) 1996-12-05
CA2050565A1 (en) 1992-03-06
BR9103803A (pt) 1992-05-19
KR0162497B1 (ko) 1998-12-01
JP3133793B2 (ja) 2001-02-13
KR920006223A (ko) 1992-04-27
EP0474210A1 (de) 1992-03-11
CA2050565C (en) 2003-04-15
DE69122933T2 (de) 1997-05-22
JPH0626068A (ja) 1994-02-01
AU649263B2 (en) 1994-05-19

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