EP0373148B1 - Hydraulic excavator - Google Patents

Hydraulic excavator Download PDF

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Publication number
EP0373148B1
EP0373148B1 EP89890312A EP89890312A EP0373148B1 EP 0373148 B1 EP0373148 B1 EP 0373148B1 EP 89890312 A EP89890312 A EP 89890312A EP 89890312 A EP89890312 A EP 89890312A EP 0373148 B1 EP0373148 B1 EP 0373148B1
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EP
European Patent Office
Prior art keywords
cylinder
boom
excavator
arm
plate
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
EP89890312A
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German (de)
French (fr)
Other versions
EP0373148A1 (en
Inventor
Arnulf Soyland
Josef Dipl.-Ing. Mocivnik
Konrad Schön
Johannes Dipl.-Ing. Jantscher
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BOEHLER LADETECHNIK VERTRIEBS- UND ENTWICKLUNGSGES
Original Assignee
Bohler Ladetechnik Vertriebs- und Entwicklungsgesellschaft Mbh
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Publication of EP0373148A1 publication Critical patent/EP0373148A1/en
Application granted granted Critical
Publication of EP0373148B1 publication Critical patent/EP0373148B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • 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
    • E02F3/30—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 a dipper-arm pivoted on a cantilever beam, i.e. boom
    • E02F3/302—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 a dipper-arm pivoted on a cantilever beam, i.e. boom with an additional link
    • 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
    • E02F3/30—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 a dipper-arm pivoted on a cantilever beam, i.e. boom
    • E02F3/308—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 a dipper-arm pivoted on a cantilever beam, i.e. boom working outwardly
    • 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
    • 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
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • E02F3/422—Drive systems for bucket-arms, front-end loaders, dumpers or the like

Definitions

  • the invention relates to a hydraulic excavator with a boom which can be pivoted in a vertical plane and is supported on a first frame part, the first frame part being mounted on a base frame so as to be pivotable about a substantially vertical axis, in which excavator the base frame has a chassis, which can be moved against the terrain by moving the excavator bucket, the cantilever arm for displacing the excavator bucket in a horizontal plane and for pivoting the excavator bucket about an essentially horizontal axis lying transversely to the displacement movement, with separate cylinder-piston units and for tilting the Bucket is articulated on the cantilever arm so as to be pivotable about a substantially horizontal axis, at least one thrust cylinder piston unit arranged to move the excavator bucket in the horizontal direction engaging the first frame part, with a cantilever arm on at least one disk m and at least one tilt-cylinder piston unit for pivoting the bucket are pivotally connected, the tilt-cylinder piston unit being connected to a link
  • the invention now relates to a design of a charging device of the type mentioned in the introduction, in which an additional travel drive for moving the entire charger is to be dispensed with, so that in particular compact and light designs are possible.
  • an additional travel drive for moving the entire charger is to be dispensed with, so that in particular compact and light designs are possible.
  • DE-A-25 32 453 it has already been proposed in DE-A-25 32 453 to guide the entire frame part carrying the cantilever arm on straight rails and relative to a lower frame in To make the longitudinal direction of the rails movable.
  • the loading shovel can be moved in a substantially horizontal plane to a position close to the front edge of the base frame and in a position relatively far in front of the front edge of the base frame.
  • support legs were extended in order to achieve a high degree of safety against tipping.
  • the sliding bearing on rails represents a relatively high level of design effort, which overall leads to a heavier construction.
  • the invention now aims to provide a compact device of the type mentioned in the introduction, in which a particularly high degree of adjustability of the loading shovel in the horizontal direction and in the vertical direction is possible using the lightest possible structural parts, and both a position can be achieved, in which the loading shovel comes to lie directly in front of the front edge of the base frame, as well as a puncture position in which the loading shovel can be largely inserted into material to be dismantled in the horizontal direction if the undercarriage is blocked during the insertion process.
  • the design according to the invention essentially consists in that the thrust cylinder piston unit acts between two struts forming a parallelogram linkage on a disc connecting the struts of the parallelogram linkage or in the area of the disc on one of the two struts of the parallelogram linkage and that on the Disc attacks at least one lifting cylinder piston unit for pivoting the cantilever arm in the vertical direction.
  • at least one thrust cylinder piston unit is used between two struts forming a parallelogram linkage for the displacement movement of the excavator bucket in a substantially horizontal direction, a high degree of stability is achieved in the case of comparatively light struts, since the thrust cylinder trusses the struts of the parallelogram linkage stiffened.
  • the measure of forming the part connecting the free ends of the struts of the parallelogram links as a disk offers the advantage of arranging the further link or cylinder-piston assemblies in a kinematically favorable manner on this disk, the disk itself being kept free from torsional forces, so that it is relatively flat and again light-weight panes can be used.
  • Both the lifting cylinder piston unit for pivoting an extension arm for the blade and the tilting cylinder piston unit for pivoting the blade on the extension arm can now be securely mounted on the disks which connect the two struts of the parallelogram linkage, the measure, to articulate the tilt cylinder for tilting the bucket on the cantilever arm on the disk and to connect it to a pivoting arm connected to the cantilever arm, which makes it possible to connect the bucket to the handlebar arm via a coupling rod, so that, if necessary, of the Material falling from the blade cannot reach the cylinder piston units, in particular the cylinder piston unit for tilting the blade, but only on the coupling rod. In this way, the tilt-cylinder piston unit is better protected against premature wear.
  • washers in the frame of the handlebar parallelogram makes it particularly possible use light cantilever arms or a particularly lightly designed lower strut of the parallelogram link, which is made possible, for example, by using hollow profiles for the lower strut or the cantilever arm.
  • the design is preferably such that the disks have an essentially triangular outline, all angles of the triangle being acute angles.
  • an essentially equilateral triangle appears to be particularly advantageous as an outline shape for the side disks, such an essentially triangular disk having particularly favorable and preferred articulation points for struts and hydraulic cylinder-piston units at their corner points.
  • a lightweight and torsion-resistant construction can be realized in a particularly simple manner in that the articulation axes of the cantilever arm, the tilt cylinder and the lifting cylinder are arranged on the disk essentially along a triangular side of the disk, preferably the articulation axes of the lifting cylinder, the tilt cylinder and the Upper strut of the parallelogram handlebars are arranged near the corner points of the substantially triangular disks.
  • Discs in which the articulation axes are arranged in the specified manner, are distinguished by the fact that a particularly low overall height can be maintained in all pivoting positions of the cantilever arm relative to the base frame, all forces being able to be safely absorbed by the discs at the same time simple and relatively thin-walled sheet metal disks can be used, which results in a further weight saving.
  • the design is such that the cantilever arm is cranked and is articulated between the two disks connected to the parallelogram links with the disks and the lower strut of the parallelogram links.
  • the extension arm which is pivotally connected to the disc is a cranked cantilever arm
  • a particularly extensive pivoting of the cantilever arm is also possible if the lower strut of the parallelogram is formed by a box profile.
  • the boom arm is pivoted in, an almost parallel position of the boom arm to the lower strut of the parallelogram linkage can be realized in the retracted position of the blade, which in turn allows the blade to be used close to the front edge of the base frame with small dimensions. Overall, this results in a relatively large operating radius of the blade with particularly compact dimensions.
  • a particularly stable construction and good absorption of the dynamic forces when pivoting the cantilever arm or when inserting the shovel into material to be dismantled or loaded can be achieved in that the articulation axis of the lower strut of the parallelogram link and the cantilever arm is arranged approximately in one side center of a triangular side is.
  • disks of the type described above and the preferred configuration of the cantilever arm as a cranked cantilever arm allows, as already mentioned, a further weight saving, without loss of stability, with respect to the lower strut of the parallelogram link, which can preferably be designed as a box profile, and, as it corresponds to a preferred embodiment of the invention, is arranged between two disks, a separate upper strut of the parallelogram handlebar engaging each disk.
  • the push-cylinder piston unit or the push-cylinder piston units can be arranged protected between the disks, while using a box profile for the lower strut of the parallelogram link, extensive protection of these cylinder-piston units for the displacement drive of the Bucket can be offered in a substantially horizontal direction.
  • the design is advantageously made such that the thrust-cylinder piston assembly is pivotally supported near the articulation point of the upper strut of the parallelogram link on the frame part and at the upper end of the lower one Strut of the parallelogram and / or on the disc near this articulation point attacks.
  • a particularly stable, compact and lightweight construction can be achieved in that the disks are formed by box profiles, the articulation axes for the lifting and tilting cylinder piston units and possibly for the upper struts of the parallelogram linkage forming between free flanges of the disks .
  • stable disks are formed with low weight, which also offer protection of the articulation points of the cylinder-piston units and the struts.
  • FIG. 1 shows a perspective view of a hydraulic excavator according to the invention
  • FIGS. 2 and 3 show side views of the hydraulic excavator according to the invention with different positions of the cantilever arm and the bucket.
  • a hydraulic excavator which has a base frame 2 with a chassis for wheels 3.
  • a first frame part generally designated 4
  • various auxiliary units are mounted on the base frame and generally designated 6 and a driver's cab 7 is provided.
  • the hydraulic excavator 1 does not have its own drive, but instead a movement of the excavator bucket 8 is used to move the excavator, as will be explained in the following.
  • the articulation axes of the lower strut 9 on the frame and on the disks 11 arranged on both sides of the lower strut 9 are denoted by 12 and 13.
  • the articulation axis of the upper strut on the disks 11 is designated by 14.
  • a thrust-cylinder piston unit 15 is arranged, which is pivotally articulated on the frame between the two struts 9 and 10 and on the lower strut 9 in the region of the disks 11, as is shown in the following figures becomes clearer.
  • the cylinder-piston unit 15 When the cylinder-piston unit 15 is actuated, the blade 8 moves in a substantially horizontal direction relative to the ground via the parallelogram link 4.
  • a cranked cantilever arm 16 is further articulated about the articulation axis 13 of the lower strut 9 on the disks 11, whereby for a lifting movement of the cantilever arm 16 on both sides of the cantilever arm arranged stroke-cylinder-piston units 17 are used.
  • the articulation axes of the lifting cylinders 17 on the disks 11 and on the extension arm 16 are designated 18 and 19, respectively.
  • tilt-cylinder piston units 20 are provided, which are pivotably mounted on the coupling disks 11 and on link arms 21 articulated to the extension arm about pivot axes 22 and 23, respectively.
  • the articulation axes of the link arms 21 on the extension arm are designated by 24.
  • Coupling rods 25 are connected to the articulated handlebar arms 21 about pivot axes 26, these coupling rods 25 being connected to the blade outside the tilting axis of the blade 8 on the extension arm 16, as is shown in more detail in the following figures.
  • the disks 11 are formed by hollow box profiles, the bolts forming the respective articulation axes 13, 14, 18, 22 being arranged between free flanges of the disks and in this way the bearing eyes of the struts or cylinder-piston units are arranged in a protected manner between the disks.
  • Fig. 2 the boom arm or the bucket is shown in the erected position.
  • the cylinder-piston unit 15 provided between the struts 9 and 10 of the parallelogram link 4 is clearly visible, which is about a pivot axis 27 on the frame and in the region of the pivot axis 13 of the lower strut 9 on the disks 11, which is aligned with the pivot axis of the extension arm 16 the disks coincide, is pivoted about a pivot axis 28.
  • the articulation axis of the upper strut 10 on the frame is designated 29.
  • the articulation axis 30 of the blade 8 on the cantilever arm 16 and the articulation axis 31 of the coupling rod 25 provided outside this articulation axis are shown in more detail in FIG. 2.
  • the disks 11 have an essentially triangular outline and there are the articulation axes 18 and 22 of the lifting cylinder 17 and the tilting cylinder 20 as well as the articulation axis 14 of the upper strut 10 of the parallelogram arm 4 near the corner points of the almost equilateral triangle the discs 11 arranged.
  • the disks 11 For a suitable kinematics and low loading of the disks 11, as a result of which they can be made relatively thin-walled and light, as can be seen from FIG.
  • the articulation axes of the extension arm 16 and the lifting cylinder 17 and the tilting cylinder 20 are essentially along a triangular side arranged, the common articulation axis of the lower strut 9 on the disks 11 and the extension arm 16 on the disks 11 being provided substantially centrally between the articulation axes 18 and 22 of the cylinder-piston units.
  • the cranked design of the cantilever arm 16 is also clearly visible, which for achieving a position of the bucket 8 as close as possible to the chassis of the excavator, as is shown even more clearly in FIG. 3, when the lower strut 9 of the Parallelogram handlebar is particularly suitable as a box profile.
  • the push-cylinder-piston unit 15 is arranged essentially diagonally between the struts 9 and 10 of the parallelogram link or the first pivotable frame part 4 and is pivotably articulated near the articulation axes of the struts on the frame or on the disks 11, as a result of which With a lever arm that is as long as possible, good force absorption with the lowest possible bending forces on the struts can be achieved by the push-cylinder piston unit 15.
  • FIG. 2 Different positions of the excavator shovel 8 are shown in broken lines in FIG. 2. Starting from a position 8a, which is shown in more detail in FIG. 3 with the corresponding position of the cylinder-piston units and pivotable struts or the pivotable extension arm, results when only the thrust cylinder 15 is actuated, a movement of the bucket in a substantially horizontal direction into a position 8b in which the bucket can be erected into the position 8c by actuation of the tilting cylinder 20.
  • the excavator is moved by correspondingly supporting the bucket in the ground starting from position 8b, whereby after the blocking of the undercarriage has been released by actuating the push cylinder, the excavator is pulled up by the bucket buried in position 8b until the bucket 8 is self-supporting in turn is located close to the landing gear. A large displacement path of the excavator can thus be achieved in one operation.
  • actuation of the lifting cylinder 17 causes the bucket to be pivoted into the position 8d furthest away from the frame, with only the push cylinder 15 again moving the bucket into a position 8e substantially above the machine frame between the struts 9 and 10 is operated.
  • the movement takes place in such a way that material picked up remains securely in the bucket without additional compensating movements, for example of the tilting cylinder, being necessary.
  • the handlebar geometry or the arrangement of the cylinder-piston units is thus made such that for an arbitrary operation only one cylinder-piston unit has to be actuated, which makes handling much easier overall, since no complicated corrective movements of a second cylinder-piston unit are necessary.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Shovels (AREA)
  • Earth Drilling (AREA)
  • Operation Control Of Excavators (AREA)
  • Component Parts Of Construction Machinery (AREA)

Abstract

In a hydraulic excavator (1) having a boom (16) which can be swivelled in a vertical plane and has a running gear which is arranged on the base frame and can be moved towards the ground by moving the excavator shovel (8), at least one thrust cylinder-piston assembly (15) on the frame, said assembly being provided for the purpose of displacing the excavator shovel (8) in the horizontal direction, engages between two stays (9, 10) forming a parallelogram link on a plate (11) connecting the stays (9, 10) of the parallelogram link (4) or, in the region of the plate (11), on one of the two stays (9, 10). Also connected swivellably to the plate (11) are the boom arm (16) and at least one lifting cylinder-piston assembly (17) for swivelling the boom arm (16) in the vertical direction and at least one tilting cylinder-piston assembly (20) for tilting the shovel (8), the tilting cylinder-piston assembly (20) being connected to a link arm (21) pivotably supported on the boom arm (16) and a connecting rod (25) connected to the link arm (21) in articulated fashion being connected to the shovel (8) in articulated fashion outside the tilting axis (30) on the boom arm (16). <IMAGE>

Description

Die Erfindung bezieht sich auf einen Hydraulikbagger mit einem in einer vertikalen Ebene schwenkbaren Ausleger, welcher an einem ersten Rahmenteil abgestützt ist, wobei der erste Rahmenteil an einem Grundrahmen um eine im wesentlichen vertikale Achse schwenkbar gelagert ist, bei welchem Bagger der Grundrahmen ein Fahrwerk aufweist, welches durch Bewegung der Baggerschaufel gegen das Gelände verfahrbar ist, wobei der Auslegerarm zur Verschiebung der Baggerschaufel in einer horizontalen Ebene und zum Schwenken der Baggerschaufel um eine quer zur Verschiebebewegung liegende, im wesentlichen horizontale Achse mit gesonderten Zylinder-Kolbenaggregaten beaufschlagbar ist und wobei zum Kippen die Schaufel um eine im wesentlichen horizontale Achse schwenkbar am Auslegerarm angelenkt ist, wobei wenigstens ein zum Verschieben der Baggerschaufel in horizontaler Richtung angeordnetes Schub-Zylinder-Kolbenaggregat an dem ersten Rahmenteil angreift, wobei an wenigstens einer Scheibe ein Auslegerarm und wenigstens ein Kipp-Zylinder-Kolbenaggregat zum Kippen der Schaufel schwenkbar angeschlossen sind, wobei das Kipp-Zylinder-Kolbenaggregat mit einem am Auslegerarm schwenkbar abgestützten Lenkerarm verbunden ist und eine am Lenkerarm gelenkig angeschlossene Koppelstange gelenkig mit der Schaufel außerhalb der Kippachse am Auslegerarm verbunden ist.The invention relates to a hydraulic excavator with a boom which can be pivoted in a vertical plane and is supported on a first frame part, the first frame part being mounted on a base frame so as to be pivotable about a substantially vertical axis, in which excavator the base frame has a chassis, which can be moved against the terrain by moving the excavator bucket, the cantilever arm for displacing the excavator bucket in a horizontal plane and for pivoting the excavator bucket about an essentially horizontal axis lying transversely to the displacement movement, with separate cylinder-piston units and for tilting the Bucket is articulated on the cantilever arm so as to be pivotable about a substantially horizontal axis, at least one thrust cylinder piston unit arranged to move the excavator bucket in the horizontal direction engaging the first frame part, with a cantilever arm on at least one disk m and at least one tilt-cylinder piston unit for pivoting the bucket are pivotally connected, the tilt-cylinder piston unit being connected to a link arm pivotally supported on the extension arm and a coupling rod articulated on the link arm being pivotally connected to the bucket outside the tilt axis on the extension arm is.

Ladegeräte, insbesondere Bagger, sind in unterschiedlichster Ausbildung bekanntgeworden. Die meisten bekannten Baggereinrichtungen verfügen über ein Fahrwerk mit eigenem Antrieb, so daß eine Reihe von komplexen Bewegungen der Ladeschaufel durch Verfahren des gesamten Baggers ohne weiteres bewerkstelligt werden können. Dies gilt insbesondere für das mit einem verfahrbaren Bagger mit eigenem Antrieb üblicherweise durch den Fahrantrieb erfolgende Einstechen der Schaufel in zu ladendes Material.Chargers, especially excavators, have become known in a wide variety of forms. Most known excavator devices have a chassis with their own drive, so that a series of complex movements of the loading shovel can be easily accomplished by moving the entire excavator. This applies in particular to the plunging of the bucket into the material to be loaded, which is usually carried out by the traction drive with a movable excavator with its own drive.

Aus der US-A 3 952 890 ist ein Hydraulikbagger der eingangs genannten Art bekanntgeworden, wobei diese bekannte Ausbildung offensichtlich einen eigenen Antrieb für das Fahrwerk aufweist. Hiebei ist ein Auslegerarm mit zwei einander kreuzenden Zylinder-Kolbenaggregaten verbunden, welche am Rahmen angelenkt sind, wobei durch Zusammenwirken der Zylinder mit Parallelogrammlenkern eine im wesentlichen horizontale Position der Schaufel in unterschiedlichen Höhen erzielbar sein soll.From US-A 3 952 890 a hydraulic excavator of the type mentioned has become known, this known design obviously has its own drive for the chassis. Hiebei is a cantilever arm connected to two intersecting cylinder-piston units, which are articulated to the frame, wherein by interacting the cylinder with parallelogram links, an essentially horizontal position of the blade at different heights should be achievable.

Die Erfindung bezieht sich nun auf eine Ausbildung einer Ladeeinrichtung der eingangs genannten Art, bei welcher ein zusätzlicher Fahrantrieb für das Verfahren des gesamten Ladegerätes entfallen soll, so daß insbesondere kompakte und leichte Ausbildungen möglich werden. Um bei derartigen Einrichtungen einen hinreichenden Aktionsradius bei im Gelände festgelegter Position des Ladegerätes zu erzielen, wurde in der DE-A-25 32 453 bereits vorgeschlagen, den gesamten, den Auslegerarm tragenden Rahmenteil auf geradlinig verlaufenden Schienen zu führen und relativ zu einem unteren Rahmengestell in Längsrichtung der Schienen verfahrbar auszubilden. Durch eine solche Ausbildung wurde bei relativ kompakten Abmessungen erreicht, daß die Ladeschaufel bis nahe an die Vorderkante des Grundrahmens und in eine relativ weit vor der Vorderkante des Grundrahmens liegende Position in einer im wesentlichen horizontalen Ebene verschiebbar wird. Bei einer derartigen Ausbildung wurden daher je nach Verschiebeposition des oberen Rahmenteiles Stützbeine ausgefahren, um eine weitgehende Kippsicherheit zu erzielen. Im übrigen stellt die Verschiebelagerung auf Schienen einen relativ hohen konstruktiven Aufwand dar, welcher insgesamt zu einer schwereren Konstruktion führt.The invention now relates to a design of a charging device of the type mentioned in the introduction, in which an additional travel drive for moving the entire charger is to be dispensed with, so that in particular compact and light designs are possible. In order to achieve a sufficient radius of action with such devices when the charger is positioned in the field, it has already been proposed in DE-A-25 32 453 to guide the entire frame part carrying the cantilever arm on straight rails and relative to a lower frame in To make the longitudinal direction of the rails movable. With such a design it was achieved with relatively compact dimensions that the loading shovel can be moved in a substantially horizontal plane to a position close to the front edge of the base frame and in a position relatively far in front of the front edge of the base frame. With such a design, depending on the displacement position of the upper frame part, support legs were extended in order to achieve a high degree of safety against tipping. In addition, the sliding bearing on rails represents a relatively high level of design effort, which overall leads to a heavier construction.

Die Erfindung zielt nun darauf ab, eine kompakte Einrichtung der eingangs genannten Art zu schaffen, bei welcher ein besonders hohes Maß an Verstellbarkeit der Ladeschaufel in horizontaler Richtung und in vertikaler Richtung unter Verwendung möglichst leichter Konstruktionsteile möglich wird, und sowohl eine Position erreicht werden kann, bei welcher die Ladeschaufel unmittelbar vor der Vorderkante des Grundrahmens zu liegen kommt, als auch eine Einstechposition, bei welcher die Ladeschaufel in horizontaler Richtung in hohem Maße in abzubauendes Material eingeschoben werden kann, wenn das Fahrwerk während des Einschiebevorganges blockiert ist. Zur Lösung dieser Aufgabe besteht die erfindungsgemäße Ausbildung im wesentlichen darin, daß das Schub-Zylinder-Kolbenaggregat zwischen zwei einen Parallelogrammlenker ausbildenden Streben an einer die Streben des Parallelogrammlenkers verbindenden Scheibe oder im Bereich der Scheibe an einer der beiden Streben des Parallelogrammlenkers angreift und daß an der Scheibe wenigstens ein Hub-Zylinder-Kolbenaggregat zum Verschwenken des Auslegerarmes in vertikaler Richtung angreift. Dadurch, daß wenigstens ein Schub-Zylinder-Kolbenaggregat zwischen zwei einen Parallelogrammlenker ausbildenden Streben für die Verschiebebewegung der Baggerschaufel in im wesentlichen horizontaler Richtung verwendet wird, wird bei vergleichsweise leicht ausgebildeten Streben ein hohes Maß an Stabilität erzielt, da der Schubzylinder die Streben des Parallelogrammlenkers fachwerkartig versteift. Die Maßnahme, den die freien Enden der Streben der Parallelogrammlenker verbindenden Teil als Scheibe auszubilden, bietet den Vorteil, die weiteren Lenker- bzw. Zylinder-Kolbenaggregate kinematisch günstig an dieser Scheibe anzuordnen, wobei die Scheibe selbst von Verwindungskräften freigehalten ist, so daß relativ flache und wiederum leicht bauende Scheiben Verwendung finden können. An den Scheiben, welche die beiden Streben des Parallelogrammlenkers verbinden, können nun sowohl das Hub-Zylinder-Kolbenaggregat zum Verschwenken eines Auslegerarmes für die Schaufel als auch das Kipp-Zylinder-Kolbenaggregat zum Verschwenken der Schaufel am Auslegerarm sicher gelagert werden, wobei die Maßnahme, den Kippzylinder für das Kippen der Schaufel am Auslegerarm an der Scheibe anzulenken und mit einem schwenkbar am Auslegerarm verbundenen Lenkerarm zu verbinden, die Möglichkeit schafft, die Schaufel über eine Koppelstange mit dem Lenkerarm zu verbinden, so daß gegebenenfalls von der Schaufel abfallendes Material nicht unmittelbar auf die Zylinder-Kolbenaggregate, insbesondere das Zylinder-Kolbenaggregat für das Kippen der Schaufel, sondern lediglich auf die Koppelstange gelangen kann. Auf diese Weise wird das Kipp-Zylinder-Kolbenaggregat besser gegen vorzeitigen Verschleiß geschützt. Die Verwendung von Scheiben im Rahmen des Lenkerparallelogrammes erlaubt es, besonders leichte Auslegerarme bzw. eine besonders leicht ausgebildete untere Strebe des Parallelogrammlenkers einzusetzen, was beispielsweise durch Verwendung von Hohlprofilen für die untere Strebe bzw. den Auslegerarm ermöglicht wird. Hiebei ist bevorzugt die Ausbildung so getroffen, daß die Scheiben im wesentlichen dreieckförmigen Umriß aufweisen, wobei alle Winkel des Dreieckes spitze Winkel sind. Besonders vorteilhaft erscheint in diesem Zusammenhang ein im wesentlichen gleichseitiges Dreieck als Umrißform für die seitlichen Scheiben, wobei eine derartige, im wesentlichen dreieckförmige Scheibe besonders günstige und bevorzugte Anlenkpunkte für Streben und hydraulische Zylinder-Kolbenaggregate an ihren Eckpunkten aufweist. Eine leichtbauende und verwindungssteife Konstruktion läßt sich hiebei in besonders einfacher Weise dadurch verwirklichen, daß die Anlenkachsen des Auslegerarmes, des Kippzylinders und des Hubzylinders an der Scheibe im wesentlichen längs einer Dreieckseite der Scheibe angeordnet sind, wobei vorzugsweise die Anlenkachsen des Hubzylinders, des Kippzylinders und der oberen Strebe des Parallelogrammlenkers nahe den Eckpunkten der im wesentlichen dreieckförmigen Scheiben angeordnet sind. Scheiben, bei welchen die Anlenkachsen in der angegebenen Art angeordnet sind, zeichnen sich dadurch aus, daß in allen Schwenkstellungen des Auslegerarmes relativ zum Grundrahmen eine besonders niedrige Bauhöhe eingehalten werden kann, wobei gleichzeitig alle Kräfte auch dann sicher von den Scheiben aufgenommen werden können, wenn einfache und relativ dünnwandige Blechscheiben verwendet werden, wodurch sich eine weitere Gewichtsersparnis ergibt.The invention now aims to provide a compact device of the type mentioned in the introduction, in which a particularly high degree of adjustability of the loading shovel in the horizontal direction and in the vertical direction is possible using the lightest possible structural parts, and both a position can be achieved, in which the loading shovel comes to lie directly in front of the front edge of the base frame, as well as a puncture position in which the loading shovel can be largely inserted into material to be dismantled in the horizontal direction if the undercarriage is blocked during the insertion process. To achieve this object, the design according to the invention essentially consists in that the thrust cylinder piston unit acts between two struts forming a parallelogram linkage on a disc connecting the struts of the parallelogram linkage or in the area of the disc on one of the two struts of the parallelogram linkage and that on the Disc attacks at least one lifting cylinder piston unit for pivoting the cantilever arm in the vertical direction. The fact that at least one thrust cylinder piston unit is used between two struts forming a parallelogram linkage for the displacement movement of the excavator bucket in a substantially horizontal direction, a high degree of stability is achieved in the case of comparatively light struts, since the thrust cylinder trusses the struts of the parallelogram linkage stiffened. The measure of forming the part connecting the free ends of the struts of the parallelogram links as a disk offers the advantage of arranging the further link or cylinder-piston assemblies in a kinematically favorable manner on this disk, the disk itself being kept free from torsional forces, so that it is relatively flat and again light-weight panes can be used. Both the lifting cylinder piston unit for pivoting an extension arm for the blade and the tilting cylinder piston unit for pivoting the blade on the extension arm can now be securely mounted on the disks which connect the two struts of the parallelogram linkage, the measure, to articulate the tilt cylinder for tilting the bucket on the cantilever arm on the disk and to connect it to a pivoting arm connected to the cantilever arm, which makes it possible to connect the bucket to the handlebar arm via a coupling rod, so that, if necessary, of the Material falling from the blade cannot reach the cylinder piston units, in particular the cylinder piston unit for tilting the blade, but only on the coupling rod. In this way, the tilt-cylinder piston unit is better protected against premature wear. The use of washers in the frame of the handlebar parallelogram makes it particularly possible use light cantilever arms or a particularly lightly designed lower strut of the parallelogram link, which is made possible, for example, by using hollow profiles for the lower strut or the cantilever arm. In this case, the design is preferably such that the disks have an essentially triangular outline, all angles of the triangle being acute angles. In this context, an essentially equilateral triangle appears to be particularly advantageous as an outline shape for the side disks, such an essentially triangular disk having particularly favorable and preferred articulation points for struts and hydraulic cylinder-piston units at their corner points. A lightweight and torsion-resistant construction can be realized in a particularly simple manner in that the articulation axes of the cantilever arm, the tilt cylinder and the lifting cylinder are arranged on the disk essentially along a triangular side of the disk, preferably the articulation axes of the lifting cylinder, the tilt cylinder and the Upper strut of the parallelogram handlebars are arranged near the corner points of the substantially triangular disks. Discs, in which the articulation axes are arranged in the specified manner, are distinguished by the fact that a particularly low overall height can be maintained in all pivoting positions of the cantilever arm relative to the base frame, all forces being able to be safely absorbed by the discs at the same time simple and relatively thin-walled sheet metal disks can be used, which results in a further weight saving.

In besonders bevorzugter Weise ist die Ausbildung so getroffen, daß der Auslegerarm gekröpft ausgebildet ist und zwischen zwei mit den Parallelogrammlenkern verbundenen Scheiben mit den Scheiben und der unteren Strebe der Parallelogrammlenker gelenkig verbunden ist. Bei Ausbildung des Auslegerarmes, welcher an der Scheibe schwenkbar angeschlossen ist, als gekröpfter Auslegerarm wird ein besonders weitgehendes Einschwenken des Auslegerarmes auch kann möglich, wenn die untere Strebe des Parallelogrammlenkers von einem Kastenprofil gebildet ist. Bei Einschwenken des Auslegerarmes läßt sich auf diese Weise eine nahezu parallele Lage des Auslegerarmes zur unteren Strebe des Parallelogrammlenkers in zurückgezogener Stellung der Schaufel realisieren, wodurch wiederum bei kleinen Abmessungen die Schaufel bis nahe an die Vorderkante des Grundrahmens herangezogen werden kann. Insgesamt ergibt sich auf diese Weise bei besonders kompakten Abmessungen ein relativ großer Aktionsradius der Schaufel.In a particularly preferred manner, the design is such that the cantilever arm is cranked and is articulated between the two disks connected to the parallelogram links with the disks and the lower strut of the parallelogram links. When forming the extension arm, which is pivotally connected to the disc is a cranked cantilever arm, a particularly extensive pivoting of the cantilever arm is also possible if the lower strut of the parallelogram is formed by a box profile. When the boom arm is pivoted in, an almost parallel position of the boom arm to the lower strut of the parallelogram linkage can be realized in the retracted position of the blade, which in turn allows the blade to be used close to the front edge of the base frame with small dimensions. Overall, this results in a relatively large operating radius of the blade with particularly compact dimensions.

Eine besonders stabile Konstruktion und gute Aufnahme der dynamischen Kräfte beim Verschwenken des Auslegerarmes bzw. beim Einschieben der Schaufel in abzubauendes bzw. zu verladendes Material läßt sich dadurch verwirklichen, daß die Anlenkachse der unteren Strebe des Parallelogrammlenkers und des Auslegerarmes etwa in einer Seitenmitte einer Dreieckseite angeordnet ist.A particularly stable construction and good absorption of the dynamic forces when pivoting the cantilever arm or when inserting the shovel into material to be dismantled or loaded can be achieved in that the articulation axis of the lower strut of the parallelogram link and the cantilever arm is arranged approximately in one side center of a triangular side is.

Die Verwendung von Scheiben der oben bezeichneten Art und die bevorzugte Ausbildung des Auslegerarmes als gekröpfter Auslegerarm erlaubt, wie bereits erwähnt, eine weitere Gewichtsersparnis, ohne Einbuße an Stabilität, in bezug auf die untere Strebe des Parallelogrammlenkers, welche bevorzugt als Kastenprofil ausgebildet sein kann und, wie es einer bevorzugten Ausbildung der Erfindung entspricht, zwischen zwei Scheiben angeordnet ist, wobei an jeder Scheibe eine gesonderte obere Strebe des Parallelogrammlenkers angreift. Bei einer derartigen Ausbildung kann das Schub-Zylinder-Kolbenaggregat bzw. die Schub-Zylinder-Kolbenaggregate geschützt zwischen den Scheiben angeordnet werden, wobei bei Verwendung eines Kastenprofiles für die untere Strebe des Parallelogrammlenkers gleichzeitig ein weitgehender Schutz dieser Zylinder-Kolbenaggregate für den Verschiebeantrieb der Schaufel in im wesentlichen horizontaler Richtung geboten werden kann. Um für diesen Verschiebeantrieb mit relativ kompakten Zylinder-Kolbenaggregaten einen großen Verstellweg zu gewährleisten, ist mit Vorteil die Ausbildung so getroffen, daß das Schub-Zylinder-Kolbenaggregat nahe dem Anlenkpunkt der oberen Strebe des Parallelogrammlenkers am Rahmenteil schwenkbar abgestützt ist und am oberen Ende der unteren Strebe des Parallelogrammlenkers und/oder an der Scheibe nahe dieser Anlenkstelle angreift. Ein wesentlicher Vorteil dieser Anordnung ist hiebei darin zu überblicken, daß keine nennenswerten Biegekräfte durch die Schub-Zylinder-Kolbenaggregate in die Streben eingeleitet werden und die Verschiebekräfte des Schub-Zylinder-Kolbenaggregates über einen relativ langen Hebelarm zur Wirkung gelangen, wodurch zum einen ein leichteres und kompakteres Schub-Zylinder-Kolbenaggregat Verwendung finden kann und zum anderen die Lenkerkonstruktion bzw. die Dimensionierung der Streben leichter und kompakter gewählt werden kann.The use of disks of the type described above and the preferred configuration of the cantilever arm as a cranked cantilever arm allows, as already mentioned, a further weight saving, without loss of stability, with respect to the lower strut of the parallelogram link, which can preferably be designed as a box profile, and, as it corresponds to a preferred embodiment of the invention, is arranged between two disks, a separate upper strut of the parallelogram handlebar engaging each disk. With such a design, the push-cylinder piston unit or the push-cylinder piston units can be arranged protected between the disks, while using a box profile for the lower strut of the parallelogram link, extensive protection of these cylinder-piston units for the displacement drive of the Bucket can be offered in a substantially horizontal direction. In order to ensure a large adjustment path for this displacement drive with relatively compact cylinder-piston assemblies, the design is advantageously made such that the thrust-cylinder piston assembly is pivotally supported near the articulation point of the upper strut of the parallelogram link on the frame part and at the upper end of the lower one Strut of the parallelogram and / or on the disc near this articulation point attacks. A major advantage of this arrangement is to be overlooked in that no significant bending forces are introduced into the struts by the push-cylinder piston units and the displacement forces of the push-cylinder piston unit come into effect via a relatively long lever arm, which on the one hand makes it easier and more compact thrust-cylinder piston unit can be used and on the other hand the handlebar design or the dimensioning of the struts can be chosen lighter and more compact.

Eine besonders stabile, kompakte und leichte Konstruktion läßt sich dadurch erzielen, daß die Scheiben von Kastenprofilen gebildet sind, wobei zwischen freien Flanschen der Scheiben Bolzen die Anlenkachsen für die Hub- und Kipp-Zylinder-Kolbenaggregate sowie ggf. für die oberen Streben des Parallelogrammlenkers ausbilden. Auf diese Weise werden bei geringem Gewicht stabile Scheiben ausgebildet, welche darüberhinaus einen Schutz der Anlenkstellen der Zylinder-Kolbenaggregate sowie der Streben bieten.A particularly stable, compact and lightweight construction can be achieved in that the disks are formed by box profiles, the articulation axes for the lifting and tilting cylinder piston units and possibly for the upper struts of the parallelogram linkage forming between free flanges of the disks . In this way, stable disks are formed with low weight, which also offer protection of the articulation points of the cylinder-piston units and the struts.

Die Erfindung wird nachfolgend an Hand eines in der Zeichnung schematisch dargestellten Ausführungsbeispieles näher erläutert. In dieser zeigen: Fig. 1 eine perspektivische Ansicht eines erfindungsgemäßen Hydraulikbaggers und die Fig. 2 und 3 Seitenansichten des erfindungsgemäßen Hydraulikbaggers mit unterschiedlichen Stellungen des Auslegerarmes und der Schaufel.The invention is explained in more detail below on the basis of an exemplary embodiment schematically illustrated in the drawing. 1 shows a perspective view of a hydraulic excavator according to the invention and FIGS. 2 and 3 show side views of the hydraulic excavator according to the invention with different positions of the cantilever arm and the bucket.

In Fig. 1 ist mit 1 ein Hydraulikbagger bezeichnet, welcher einen Grundrahmen 2 mit einem Fahrwerk für Räder 3 aufweist. Am Grundrahmen 2 ist ein allgemein mit 4 bezeichneter ersten Rahmenteil um eine im wesentlichen vertikale Achse schwenkbar gelagert, wobei ein Drehkranz mit 5 angedeutet ist. Weiters sind am Grundrahmen diverse Hilfsaggregate gelagert und allgemein mit 6 bezeichnet und es ist eine Führerkabine 7 vorgesehen. Der Hydraulikbagger 1 weist dabei keinen eigenen Antrieb auf, sondern es wird für eine Verschiebung des Baggers eine Bewegung der Baggerschaufel 8 herangezogen, wie dies im folgenden noch erläutert werden wird.In Fig. 1, 1 denotes a hydraulic excavator, which has a base frame 2 with a chassis for wheels 3. On the base frame 2, a first frame part, generally designated 4, is pivotally mounted about an essentially vertical axis, a turntable being indicated by 5. Furthermore, various auxiliary units are mounted on the base frame and generally designated 6 and a driver's cab 7 is provided. The hydraulic excavator 1 does not have its own drive, but instead a movement of the excavator bucket 8 is used to move the excavator, as will be explained in the following.

Der am Grundrahmen um eine im wesentlichen vertikale Achse schwenkbar gelagerte erste Rahmenteil 4 wird dabei von Parallelogrammlenkern gebildet, wobei eine untere, insbesondere als Hohlkastenprofil ausgebildete Strebe 9 sowie obere Streben 10 sowohl im Bereich der Drehlagerung 5 als auch an die Streben 9 und 10 des Parallelogrammlenkers 4 verbindenden Scheiben 11 schwenkbar gelagert ist. Die Anlenkachsen der unteren Strebe 9 am Rahmen sowie an den beidseitig der unteren Strebe 9 angeordneten Scheiben 11 sind dabei mit 12 und 13 bezeichnet. Die Anlenkachse der oberen Strebe an den Scheiben 11 ist mit 14 bezeichnet. Zwischen den Streben 9 und 10 des Parallelogrammlenkers ist ein Schub-Zylinder-Kolbenaggregat 15 angeordnet, welches am Rahmen zwischen den beiden Streben 9 und 10 und an der unteren Strebe 9 im Bereich der Scheiben 11 schwenkbar angelenkt ist, wie dies in den folgenden Figuren noch deutlicher ersichtlich wird. Bei einer Betätigung des Zylinder-Kolbenaggregates 15 erfolgt eine Bewegung der Schaufel 8 in im wesentlichen horizontaler Richtung relativ zum Boden über die Parallelogrammlenker 4.The first frame part 4, which is pivotably mounted on the base frame about a substantially vertical axis, is formed by parallelogram links, with a lower strut 9, in particular designed as a hollow box profile, and upper struts 10 both in the region of the pivot bearing 5 and on the struts 9 and 10 of the parallelogram link 4 connecting disks 11 is pivotally mounted. The articulation axes of the lower strut 9 on the frame and on the disks 11 arranged on both sides of the lower strut 9 are denoted by 12 and 13. The articulation axis of the upper strut on the disks 11 is designated by 14. Between the struts 9 and 10 of the parallelogram, a thrust-cylinder piston unit 15 is arranged, which is pivotally articulated on the frame between the two struts 9 and 10 and on the lower strut 9 in the region of the disks 11, as is shown in the following figures becomes clearer. When the cylinder-piston unit 15 is actuated, the blade 8 moves in a substantially horizontal direction relative to the ground via the parallelogram link 4.

An den Scheiben 11 ist weiters ein gekröpft ausgebildeter Auslegerarm 16 um die Anlenkachse 13 der unteren Strebe 9 an den Scheiben 11 schwenkbar angelenkt, wobei für eine Hubbewegung des Auslegerarmes 16 zu beiden Seiten des Auslegerarmes angeordnete Hub-Zylinder-Kolbenaggregate 17 Verwendung finden. Die Anlenkachsen der Hubzylinder 17 an den Scheiben 11 bzw. am Auslegerarm 16 sind mit 18 bzw. 19 bezeichnet. Für ein Kippen der Baggerschaufel 8 sind Kipp-Zylinder-Kolbenaggregate 20 vorgesehen, welche an den Koppelscheiben 11 und an gelenkig mit dem Auslegerarm verbundenen Lenkerarmen 21 um Anlenkachsen 22 bzw. 23 schwenkbar gelagert sind. Die Anlenkachsen der Lenkerarme 21 am Auslegerarm sind dabei mit 24 bezeichnet. Zur Erzielung einer ausreichenden Verwindungssteifigkeit der Arme 21 sind diese über eine Strebe 34 miteinander verbunden. Mit den gelenkigen Lenkerarmen 21 sind Koppelstangen 25 um Schwenkachsen 26 verbunden, wobei diese Koppelstangen 25 mit der Schaufel außerhalb der Kippachse der Schaufel 8 am Auslegerarm 16 verbunden sind, wie dies in den nachfolgenden Figuren näher dargestellt wird.On the disks 11, a cranked cantilever arm 16 is further articulated about the articulation axis 13 of the lower strut 9 on the disks 11, whereby for a lifting movement of the cantilever arm 16 on both sides of the cantilever arm arranged stroke-cylinder-piston units 17 are used. The articulation axes of the lifting cylinders 17 on the disks 11 and on the extension arm 16 are designated 18 and 19, respectively. For tilting the excavator bucket 8, tilt-cylinder piston units 20 are provided, which are pivotably mounted on the coupling disks 11 and on link arms 21 articulated to the extension arm about pivot axes 22 and 23, respectively. The articulation axes of the link arms 21 on the extension arm are designated by 24. To achieve sufficient torsional rigidity of the arms 21, these are connected to one another via a strut 34. Coupling rods 25 are connected to the articulated handlebar arms 21 about pivot axes 26, these coupling rods 25 being connected to the blade outside the tilting axis of the blade 8 on the extension arm 16, as is shown in more detail in the following figures.

Die Scheiben 11 sind dabei von hohlen Kastenprofilen gebildet, wobei die die jeweiligen Anlenkachsen 13, 14, 18, 22 bildenden Bolzen zwischen freien Flanschen der Scheiben angeordnet sind und derart die Lageraugen der Streben bzw. Zylinder-Kolbenaggregate geschützt zwischen den Scheiben angeordnet sind.The disks 11 are formed by hollow box profiles, the bolts forming the respective articulation axes 13, 14, 18, 22 being arranged between free flanges of the disks and in this way the bearing eyes of the struts or cylinder-piston units are arranged in a protected manner between the disks.

In Fig. 2 ist der Auslegerarm bzw. die Schaufel in der aufgerichteten Stellung dargestellt. Dabei ist deutlich das zwischen den Streben 9 und 10 der Parallelogrammlenkers 4 vorgesehene Zylinder-Kolbenaggregat 15 ersichtlich, welches um eine Anlenkachse 27 am Rahmen und im Bereich der Anlenkachse 13 der unteren Strebe 9 an den Scheiben 11, welche mit der Anlenkachse der Auslegerarmes 16 an den Scheiben zusammenfällt, um eine Anlenkachse 28 schwenkbar angelenkt ist. Die Anlenkachse der oberen Strebe 10 am Rahmen ist mit 29 bezeichnet. Weiters sind in Fig. 2 noch die Anlenkachse 30 der Schaufel 8 am Auslegerarm 16 sowie die außerhalb dieser Anlenkachse vorgesehene Anlenkachse 31 der Koppelstange 25 näher dargestellt.In Fig. 2 the boom arm or the bucket is shown in the erected position. The cylinder-piston unit 15 provided between the struts 9 and 10 of the parallelogram link 4 is clearly visible, which is about a pivot axis 27 on the frame and in the region of the pivot axis 13 of the lower strut 9 on the disks 11, which is aligned with the pivot axis of the extension arm 16 the disks coincide, is pivoted about a pivot axis 28. The articulation axis of the upper strut 10 on the frame is designated 29. Furthermore, the articulation axis 30 of the blade 8 on the cantilever arm 16 and the articulation axis 31 of the coupling rod 25 provided outside this articulation axis are shown in more detail in FIG. 2.

Wie aus Fig. 2 deutlich ersichtlich, weisen die Scheiben 11 im wesentlichen dreieckförmigen Umriß auf und es sind die Anlenkachsen 18 und 22 des Hubzylinders 17 und des Kippzylinders 20 sowie die Anlenkachse 14 der obere Strebe 10 des Parallelogrammlenkers 4 nahe den Eckpunkten des nahezu gleichseitigen Dreiecks der Scheiben 11 angeordnet. Für eine geeignete Kinematik und geringe Belastung der Scheiben 11, wodurch diese relativ dünnwandig und leicht ausgebildet werden können, wie dies aus Fig. 1 ersichtlich ist, sind weiters die Anlenkachsen des Auslegerarmes 16 sowie der Hubzylinder 17 und der Kippzylinder 20 im wesentlichen längs einer Dreieckseite angeordnet, wobei die gemeinsame Anlenkachse der unteren Strebe 9 an den Scheiben 11 sowie des Auslegerarmes 16 an den Scheiben 11 im wesentlichen mittig zwischen den Anlenkachsen 18 und 22 der Zylinder-Kolbenaggregate vorgesehen ist. Aus Fig. 2 ist weiters deutlich die gekröpfte Ausbildung des Auslegerarmes 16 ersichtlich, welche für ein Erreichen einer dem Fahrwerk des Baggers möglichst nahe Position der Schaufel 8, wie dies in Fig. 3 noch deutlicher dargestellt ist, bei einer Ausbildung der unteren Strebe 9 des Parallelogrammlenkers als Kastenprofil besonders geeignet ist. Es ist ersichtlich, daß das Schub-Zylinder-Kolbenaggregat 15 im wesentlichen diagonal zwischen den Streben 9 und 10 des Parallelogrammlenkers bzw. ersten schwenkbaren Rahmenteiles 4 angeordnet ist und nahe den Anlenkachsen der Streben am Rahmen bzw. an den Scheiben 11 schwenkbar angelenkt ist, wodurch sich bei einem möglichst langen Hebelarm eine gute Kräfteaufnahme bei möglichst geringen Biegekräften auf den Streben durch das Schub-Zylinder-Kolbenaggregat 15 erzielen läßt.As can be clearly seen from FIG. 2, the disks 11 have an essentially triangular outline and there are the articulation axes 18 and 22 of the lifting cylinder 17 and the tilting cylinder 20 as well as the articulation axis 14 of the upper strut 10 of the parallelogram arm 4 near the corner points of the almost equilateral triangle the discs 11 arranged. For a suitable kinematics and low loading of the disks 11, as a result of which they can be made relatively thin-walled and light, as can be seen from FIG. 1, the articulation axes of the extension arm 16 and the lifting cylinder 17 and the tilting cylinder 20 are essentially along a triangular side arranged, the common articulation axis of the lower strut 9 on the disks 11 and the extension arm 16 on the disks 11 being provided substantially centrally between the articulation axes 18 and 22 of the cylinder-piston units. From Fig. 2, the cranked design of the cantilever arm 16 is also clearly visible, which for achieving a position of the bucket 8 as close as possible to the chassis of the excavator, as is shown even more clearly in FIG. 3, when the lower strut 9 of the Parallelogram handlebar is particularly suitable as a box profile. It can be seen that the push-cylinder-piston unit 15 is arranged essentially diagonally between the struts 9 and 10 of the parallelogram link or the first pivotable frame part 4 and is pivotably articulated near the articulation axes of the struts on the frame or on the disks 11, as a result of which With a lever arm that is as long as possible, good force absorption with the lowest possible bending forces on the struts can be achieved by the push-cylinder piston unit 15.

In Fig. 2 sind strichliert unterschiedliche Stellungen der Baggerschaufel 8 dargestellt. Ausgehend von einer Stellung 8a, welche in Fig. 3 mit der entsprechenden Stellung der Zylinder-Kolbenaggregate und schwenkbaren Streben bzw. dem schwenkbaren Auslegerarm genauer dargestellt ist, ergibt sich bei Betätigung lediglich des Schubzylinders 15 eine Bewegung der Schaufel in im wesentlichen horizontaler Richtung in eine Position 8b, in welcher durch eine Betätigung des Kippzylinders 20 die Schaufel in die Stellung 8c aufgerichtet werden kann. Eine derart nahezu horizontale Bewegung der Schaufel bei Betätigung des Schubzylinders 15 ist insbesondere wichtig, da der Hydraulikbagger keinen Antrieb aufweisen soll und in einer gewählten Stellung lediglich das Fahrwerk blockiert wird und allein durch die Bewegung der Baggerschaufel 8 ein Einstechen in darin aufzunehmende Materialien erfolgen muß. Weiter ist ersichtlich, daß ein überaus langer, im wesentlichen horizontaler Verschiebeweg der Schaufel zur Verfügung steht, so daß große Bereiche ohne ein Versetzen des Baggers eingeräumt werden können. Ein Versetzen des Baggers erfolgt durch ein entsprechendes Abstützen der Schaufel in den Boden ausgehend von der Position 8b, wobei nach einem Lösen der Blockierung des Fahrwerkes durch Betätigung des Schubzylinders der Bagger durch die in der Position 8b eingegrabene Schaufel herangezogen wird, bis die Schaufel 8 sich wiederum nahe vor dem Fahrwerk befindet. Es kann somit ein großer Verschiebeweg des Baggers in einem Arbeitsgang erzielt werden.Different positions of the excavator shovel 8 are shown in broken lines in FIG. 2. Starting from a position 8a, which is shown in more detail in FIG. 3 with the corresponding position of the cylinder-piston units and pivotable struts or the pivotable extension arm, results when only the thrust cylinder 15 is actuated, a movement of the bucket in a substantially horizontal direction into a position 8b in which the bucket can be erected into the position 8c by actuation of the tilting cylinder 20. Such an almost horizontal movement of the bucket when actuating the thrust cylinder 15 is particularly important since the hydraulic excavator should not have a drive and, in a selected position, only the undercarriage is blocked and the movement of the excavator shovel 8 requires a plunge into the materials to be accommodated therein. It can also be seen that an extremely long, essentially horizontal displacement path of the bucket is available, so that large areas can be cleared without moving the excavator. The excavator is moved by correspondingly supporting the bucket in the ground starting from position 8b, whereby after the blocking of the undercarriage has been released by actuating the push cylinder, the excavator is pulled up by the bucket buried in position 8b until the bucket 8 is self-supporting in turn is located close to the landing gear. A large displacement path of the excavator can thus be achieved in one operation.

Nach einem Kippen der Schaufel in die Position 8c erfolgt durch Betätigung der Hubzylinder 17 ein Verschwenken der Schaufel in die am weitesten vom Rahmen entfernte Position 8d, wobei für eine Bewegung der Schaufel in eine im wesentlichen über dem Maschinenrahmen liegende Position 8e wiederum lediglich der Schubzylinder 15 zwischen den Streben 9 und 10 betätigt wird. Wie aus den unterschiedlichen Stellungen der Schaufel ersichtlich, erfolgt auch bei einem Anheben der Schaufel die Bewegung jeweils derart, daß aufgenommenes Material sicher in der Schaufel verbleibt, ohne daß zusätzliche Ausgleichsbewegungen, beispielsweise des Kippzylinders, notwendig sind. Die Lenkergeometrie bzw. die Anordnung der Zylinder-Kolbenaggregate ist somit so getroffen, daß für einen beliebigen Arbeitsvorgang nur jeweils ein Zylinder-Kolbenaggregat betätigt werden muß, wodurch die Handhabung insgesamt wesentlich erleichtert wird, da keine komplizierten Korrekturbewegungen eines jeweils zweiten Zylinder-Kolbenaggregates notwendig sind.After the bucket has been tilted into position 8c, actuation of the lifting cylinder 17 causes the bucket to be pivoted into the position 8d furthest away from the frame, with only the push cylinder 15 again moving the bucket into a position 8e substantially above the machine frame between the struts 9 and 10 is operated. As can be seen from the different positions of the bucket, even when the bucket is raised, the movement takes place in such a way that material picked up remains securely in the bucket without additional compensating movements, for example of the tilting cylinder, being necessary. The handlebar geometry or the arrangement of the cylinder-piston units is thus made such that for an arbitrary operation only one cylinder-piston unit has to be actuated, which makes handling much easier overall, since no complicated corrective movements of a second cylinder-piston unit are necessary.

In der in Fig. 3 dargestellten möglichst maschinennahen Position der Ladeschaufel 8 ist ersichtlich, daß der Auslegerarm 16 nahezu parallel zur unteren Strebe 9 des Parallelogrammlenkers 4 angeordnet ist, wobei dies vor allem durch die gekröpfte Ausbildung des Auslegerarmes 16 im Bereich seiner Anlenkachse 13 bereits an den Scheiben 11 ermöglicht wird. Es ergibt sich somit insgesamt eine sehr kompakte Stellung der einzelnen Lenker und Streben bzw. des Auslegerarmes sowie der für die Betätigung vorgesehenen Zylinder-Kolbenaggregate. In Fig. 3 sind ebenso wie in Fig. 2 wiederum unterschiedliche Stellungen der Ladeschaufel dargestellt. Darüberhinaus ist dargestellt, daß ausgehend von der Stellung 8a bei einem Verkippen der Ladeschaufel unmittelbar vor dem Fahrwerk in die Bodenebene 32 eingestochen werden kann, wobei die entsprechende Bewegung der Spitze 33 der Ladeschaufel in diesem Fall durch die Umrißlinie II, welche die entferntesten Raumpunkte der Spitze 33 der Ladeschaufel zum Rahmen des Hydraulikbaggers beschreibt, dargestellt ist, während die Umrißlinie für die oben geschilderte Bewegung mit I bezeichnet ist. Bei einer Bewegung der Schaufelspitze 33 von Position 8a in 8b gilt, daß jeweils nur ein Zylinder-Kolbenaggregat für eine entsprechende Bewegung betätigt werden muß und Korrekturbewegungen anderer Zylinder-Kolbenaggregate nicht notwendig sind.In the position of the loading shovel 8 that is as close to the machine as possible in FIG. 3, it can be seen that the extension arm 16 is arranged almost parallel to the lower strut 9 of the parallelogram link 4, this being particularly due to the cranked configuration of the extension arm 16 in the region of its articulation axis 13 the disks 11 is made possible. The overall result is a very compact position of the individual links and struts or of the cantilever arm and of the cylinder-piston units provided for actuation. In FIG. 3, as in FIG. 2, different positions of the loading shovel are shown. In addition, it is shown that starting from position 8a, when the loading shovel is tilted, it can be pierced into the ground plane 32 directly in front of the undercarriage, the corresponding movement of the tip 33 of the loading shovel in this case by the outline II, which represents the most distant spatial points of the tip 33 describes the loading shovel for the frame of the hydraulic excavator, is shown, while the outline for the movement described above is designated by I. When the blade tip 33 moves from position 8a to 8b, only one cylinder-piston unit has to be actuated for a corresponding movement and corrective movements of other cylinder-piston units are not necessary.

Claims (9)

  1. Hydraulic excavator (1) with a boom (16) which can be swivelled in a vertical plane, which is supported on a first frame member (4), where the first frame member (4) is mounted on a chassis (2) so as to swivel about an essentially vertical axis, on which excavator the chassis (2) possessing a running gear which, through movement of the excavator shovel (8) is movable in relation to the ground, where the boom (16), for the purpose of displacing the excavator shovel (8) in a horizontal plane and for the purpose of swivelling the excavator shovel (8) about a horizontal axis essentially at right angles to the displacement motion, can be impinged upon with separate cylinder-and-piston units, and where for the purpose of tilting, the shovel (8) is linked to the boom (16) so as to permit swivelling about an essential horizontal axis, where at least one thrust cylinder-and piston unit (15) for displacement of the excavator shovel (8) in the horizontal direction acts on the first frame member (4), where, on at least one plate (11), one boom (16) and at least one tilt cylinder-and-piston unit (20) are swivel-mounted for the purpose of tilting the shovel (8), where the tilt cylinder-and-piston unit (20) is connected to a connecting arm (21) swivel-supported on the boom (16) and a coupling rod (25) pivot-mounted on the connecting arm (21) pivots on the shovel (8) outside the hinge pin (30) on the boom (16), characterized by the fact that the thrust cylinder-and-piston unit (15) acts between two struts (9, 10) forming a pantograph arm on one of the plates (11) joining the struts of the pantograph arm or in the region of the plate (11) on one of the two struts of the pantograph arm, and that at least one lift cylinder-and-piston unit (17) for swivelling the boom (16) acts in the vertical direction on the plate (11).
  2. Hydraulic excavator in accordance with Claim 1, characterized by the fact that the boom (16) is cranked in form and, between two plates (11) joined to the pantograph arms (9, 10), is pivot-mounted on the plates and the bottom strut (9) of the pantograph arms.
  3. Hydraulic excavator in accordance with Claim 1 or 2, characterized by the fact that the plate (11) is essentially triangular in outline, all angles of the triangle forming acute angles.
  4. Hydraulic excavator in accordance with Claim 1, 2 or 3, characterized by the fact that the link pins (13, 18, 22) of the boom (16), of the tilt cylinder (20) and of the lift cylinder (21) are located on the plate (11) essentially along one triangle side of the plate (11).
  5. Hydraulic excavator in accordance with one of Claims 1 to 4, characterized by the fact that the link pins (14, 18, 22) of the lift cylinder (17), of the tilt cylinder (20) and of the top strut (10) of the pantograph arm are located close to the corners of the essentially triangular plate (11).
  6. Hydraulic excavator in accordance with one of Claims 1 to 5, characterized by the fact that the link pin (13, 18) of the bottom strut (9) of the pantograph arm and of the boom (16) is located approximately in the centre of one side of the triangle.
  7. Hydraulic excavator in accordance with one of Claims 1 to 6, characterized by the fact that the bottom strut (9) of the pantograph arm takes the form of a box profile and is located between two plates (11), where a separate top strut (10) of the pantograph arm acts on each plate.
  8. Hydraulic excavator in accordance with one Claims 1 to 7, characterized by the fact that the thrust cylinder-and-piston unit (15) is swivel-mounted close to the linkage point (29) of the top strut (10) of the pantograph arm on the frame member and acts on the top end of the bottom strut (9) of the pantograph arm and/or on the plate (11) close to this linkage point.
  9. Hydraulic excavator in accordance with one of Claims 1 to 8, characterized by the fact that the plates (11) are formed by box profiles where, between free flanges of the plates, pins form link pins (14, 18, 22) for the lift and tilt cylinder-and-piston units (17, 20) and if necessary for the top struts (10) of the pantograph arm.
EP89890312A 1988-12-05 1989-12-05 Hydraulic excavator Expired - Lifetime EP0373148B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT2980/88 1988-12-05
AT0298088A AT396266B (en) 1988-12-05 1988-12-05 HYDRAULIC EXCAVATOR

Publications (2)

Publication Number Publication Date
EP0373148A1 EP0373148A1 (en) 1990-06-13
EP0373148B1 true EP0373148B1 (en) 1994-08-24

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP89890312A Expired - Lifetime EP0373148B1 (en) 1988-12-05 1989-12-05 Hydraulic excavator

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EP (1) EP0373148B1 (en)
AT (2) AT396266B (en)
BG (1) BG50498A3 (en)
DE (1) DE58908234D1 (en)
ES (1) ES2063166T3 (en)

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Publication number Priority date Publication date Assignee Title
DE102009013626A1 (en) * 2009-03-11 2010-09-16 Gerd Bär GmbH Liftable and lowerable platform device for attachment to a vehicle, in particular to a land vehicle or to a watercraft
CN104594403A (en) * 2014-12-25 2015-05-06 广西大学 Electromagnetic type active metamorphic multi-closed-chain connecting rod controllable excavation mechanism

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DE4219720A1 (en) * 1992-06-17 1993-12-23 Hausherr & Soehne Rudolf Excavator for reducing heave in tunnel floors or mine workings - consists of tracked vehicle mounting full circle slewing jib with excavator shovel
CN103726520A (en) * 2013-12-16 2014-04-16 广西大学 Nine-bar two-degree-of-freedom light-weight mechanical loading mechanism
CN103726532A (en) * 2013-12-17 2014-04-16 广西大学 Controllable symmetrical-and-parallel mechanism type loader
CN103741740A (en) * 2014-01-16 2014-04-23 上海交通大学 Excavation mechanism for electrohydraulic hybrid drive mining excavators
CN104631524A (en) * 2014-12-25 2015-05-20 广西大学 Multi-connecting-rod controllable excavation mechanism based on electromagnetic initiative metamorphism
CN108274066A (en) * 2018-01-18 2018-07-13 天津莱茵克拉电梯有限公司 A kind of liftable shearing machine material receiver
DE102019100075B3 (en) * 2019-01-03 2020-03-19 Mecalac Baumaschinen GmbH Wheel loader
CN111997114A (en) * 2020-09-28 2020-11-27 徐工集团工程机械股份有限公司科技分公司 Angle-adjustable translational lifting machine
CN113338367B (en) * 2021-06-28 2022-01-11 徐工集团工程机械股份有限公司科技分公司 Single-side movable arm structure of four-connecting-rod two-oil-cylinder skid-steer loader and lifting method

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US4143778A (en) * 1977-06-03 1979-03-13 Harnischfeger Corporation Shovel attachment means for hydraulic excavator
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009013626A1 (en) * 2009-03-11 2010-09-16 Gerd Bär GmbH Liftable and lowerable platform device for attachment to a vehicle, in particular to a land vehicle or to a watercraft
CN104594403A (en) * 2014-12-25 2015-05-06 广西大学 Electromagnetic type active metamorphic multi-closed-chain connecting rod controllable excavation mechanism

Also Published As

Publication number Publication date
BG50498A3 (en) 1992-08-14
AT396266B (en) 1993-07-26
EP0373148A1 (en) 1990-06-13
ES2063166T3 (en) 1995-01-01
DE58908234D1 (en) 1994-09-29
ATE110431T1 (en) 1994-09-15
ATA298088A (en) 1992-11-15

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