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
  • E02F9/0841—Articulated frame, i.e. having at least one pivot point between two travelling gear units
• • 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
  • E02F3/3411—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 of the Z-type

Definitions

• the invention relates to a mobile loading machine with front loading equipment, in particular construction machine, with a lifting frame which is rotatably mounted with the rear end on a front frame part of the loading machine in a lifting frame pivot point and which can be raised and lowered by means of at least one lifting cylinder, at the front end of the lifting frame in one
• a work shovel, fork or the like is articulated and a rocker arm is articulated in a rocker arm fulcrum in a central region of the lifting frame, the lower end of which is articulated in a rocker cylinder pivot point to a tilt cylinder which is articulated at the other end in a rocker cylinder pivot point on the frame part, and whose upper end is articulated in a tilting rod pivot point on a tilting rod which is articulated with its other end above the bucket pivot point in a tilting rod pivot point on the working bucket.
• the tensile strength designed for the requirements of material loosening has its maximum value in the area of the horizontal blade (bottom) position, but drops sharply with increasing tilt angle.
• the tear strength at the maximum tilt angle has dropped so far in the lifting height of the bucket that is usual for transport travel that, in the event of strong braking decelerations and / or very uneven terrain, the bucket can no longer be pressed with the necessary force, which causes strong impacts associated with corresponding noise development.
• Parallel kinematics are generally used for industrial purposes. Such parallel kinematics enable a blade guide that is parallel via the lifting movement of the lifting frame, and there is also a more favorable course of the holding forces in the upper lifting frame area when tipping out. There is also a continuous increase in the angular velocity, particularly in the last angular range, when tipping out, which enables material stuck in the blade to be tapped out.
• a disadvantage of this system is that to release the material, the tilting cylinder or cylinders are only subjected to hydraulic pressure on their annular surface, so that they must be dimensioned accordingly large.
• a generic loading machine with front loading equipment which in principle consists of only a three-part kinematic chain, namely a rocker cylinder, a rocker arm and a rocker arm, the rocker cylinder can be attached to the rocker arm in different positions, so that different kinematics geometries are feasible to meet different requirements.
• this known kinematics is still in need of substantial improvement.
• the object of the invention is to further improve the kinematics system of a generic loading machine in order to combine all the advantageous properties of the Z-kinematics, the parallel kinematics and the industrial kinematics and to avoid their disadvantages, the effort and thus the costs being those of a conventional Z - should not exceed kinematics.
• a second tilt cylinder pivot point for the tilt cylinder is provided on the rocker arm, the distance of the second upper tilt cylinder pivot point from the first lower tilt cylinder pivot point being between 0.01 and 0.12 in relation to the lifting frame length.
• the tear forces remain almost constant over the lifting height of the lifting frame. Therefore, with the system according to the invention, when the material is detached from a solid wall, it can still be broken with high tear strength even in the upper stroke area.
• the dumping is done by introducing hydraulic oil into the tilt cylinder annulus.
• the tipping speed of the implement increases disproportionately in the last rotation angle range, which means that the bucket moves up to a tipping angle of 30 to 35 °, at which the material is largely emptied, at a speed that can be easily controlled by the driver, but the stops at the maximum tipping angle with a high Speed reached, which allows the tapping of stuck material residues.
• the lifting frame advantageously has a crossbeam which is arranged between the rocker arm pivot point and the bucket pivot point and carries the rocker arm by means of the rocker arm bracket. This crossbar is preferably arranged at a distance from the rocker arm pivot point that is greater than the distance between the rocker arm pivot point and the rocker arm pivot point.
• the tilt cylinder is advantageously arranged approximately parallel to the longitudinal axis of the lifting frame.
• the rocker arm is arranged correspondingly far from the bucket pivot point and as high as possible above the frame axis, namely in such a way that the ratio of the distance from the rocker cylinder articulation point to the rocker arm pivot point to the lifting frame length between rocker arm and bucket pivot point is between 0.4 and 0.5.
• the requirement of high tearing forces is applied by applying the hydraulic pressure to the full surface of the tilt cylinder.
• the tearing forces decrease less with increasing tilt angle than with the Z-kinematics. It is a characteristic of the kinematics according to the invention that the tearing forces increase again at a tipping angle between 35 and 40 °, whereas in the Z-kinematics they would drop towards zero if the tipping was continued.
• the front end of the piston rod of the tilting cylinder is pressed against the tilting rod with high force in the region of the tilting rod pivot point on the blade, so that the latter does not detach from the stop even at higher deceleration values as a result of braking or uneven terrain, but instead maintains their position relative to the lifting frame and thus also to the vehicle.
• the property of the rupture force increasing again from the specified range of the tilt angle allows a larger maximum tilt angle to be carried out, as a result of which heaped material can be transported over uneven terrain with a reduced risk of partial loss.
• the upper part of the rocker arm which swivels backwards when the implement tilts, frees up a larger mounting space for this, which is restricted in the Z-kinematics by the rocker arm moving forward.
• the possible tipping angle due to the given tilt cylinder stroke when the blade cutting edge is placed on the ground is so large that the angle is limited not only by the tilt cylinder but also by the stops between the blade and the lifting frame. In this bucket position, this means a tipping angle of significantly more than 90 °, which enables both vertical parting of excavation pit walls and the support by tilting the bucket to free the loader that is stuck in rough terrain. Since the Z-kinematics only has a tipping angle of approx.
• the bucket that is pierced into the bottom quickly releases from the bucket during the tilting movement.
• the blade lies against the lifting frame, so that the large forces resulting from the pushing force as well as the impacts resulting from the uneven yielding of the base directly through the blade stops in the vehicle to be directed.
• the kinematics according to the invention have a considerably higher holding force than the previously known designs, so that this does not give in due to the pressure relief valve of the tilting cylinder responding.
• the implement is tilted back during the lifting process.
• this parallelism can be achieved by changing the articulation point of the tilt cylinder eye on the lower part of the rocker arm. This can be done either by repositioning the tilt cylinder into the second upper tilt cylinder pivot point or by moving the pivot point within the two brackets of the rocker arm using conventional technical means.
• the holding force is reduced here, but it still exceeds the requirements that result from the payload permissible for the machine when using the forklift.
• the crossbar in the raised lifting frame position in order to achieve optimal visibility on the working tools as close as possible to the blade pivot point.
• the arrangement of the tilting cylinder in its position relative to the lifting frame is chosen such that its longitudinal axis is approximately parallel and below the lifting frame axis in each lifting frame position and therefore in the upper lifting range in which the emptying of the Shoveling into the transport vehicles takes place, the selected position results in favorable visibility, since only the relatively thin piston rod of the tilt cylinder is in the driver's field of vision. Even in the lower lifting frame position when picking up material, the tilt cylinder is in a position that does not obstruct the view.
• FIG. 1 in side view of a mobile according to the invention
• FIG. 6 in side view of a loading machine according to the invention in excavator operation when filling a transport vehicle
• Fig. 7 is a side view of the kinematics with lifting frame and tilted bucket in the transport position.
• a mobile loading machine is generally designated L.
• This loading machine L has a front frame part 13, to which the actual universal kinematics according to the invention is articulated, the exact structure of which can be seen from FIGS. 3 to 6.
• the kinematics initially have a lifting frame 1, the lifting frame axis of which is designated by 16.
• This lifting frame 1 is rotatably supported at its rear end in a lifting frame pivot point 14 on the frame part 13 of the loading machine.
• the lifting frame 1 usually consists of two parallel frame parts.
• On the frame part 13, an only indicated lifting cylinder 2 is rotatably mounted, which is articulated with its other end on the lifting frame 1.
• the lifting frame 1 can thus be raised and lowered, namely by the Lifting frame pivot point 14.
• a working shovel 5 is articulated in a bucket pivot point 6, and in the region of the front end the lifting frame 1 has a crossbar 10 between its two lifting frame parts, on which two parallel rocker arm brackets 11 are arranged, at the ends of which in a rocker arm pivot point 15 a rocker arm 3 is articulated.
• the lower end of the rocker arm 3 is articulated in a lower first rocker cylinder pivot point 8 or an upper second rocker cylinder pivot point 9 located above it with a rocker cylinder 7 which is articulated at its other end in a rocker cylinder pivot point 11 on the frame part 13 of the loading machine.
• the upper end of the rocker arm 3 is articulated in a rocker rod pivot point 17 on a rocker rod 4, which is articulated with its other end above the bucket pivot point 6 in a rocker rod pivot point 21 on the working blade 5.
• the rocker arm 3 can be moved with the rocking rod 4 by extending or retracting the piston rod 12 of the rocking cylinder 7 and the bucket 5 can thus be pivoted. If the piston rod 12 of the tilt cylinder 7 is articulated in the tilt cylinder articulation point 8 on the rocker arm 3, the kinematics are suitable for a bucket function, and the function is then the same as for a Z kinematics (FIG. 1).
• a / 1 0.3 to 0.35
• b / 1 0.14 to 0.17
• c / 1 0.2 to 0.3
• h / 1 0.08 to 0.12
• s / 1 0.4 to 0.5
• g / 1 0.07 to 0.08
• f / 1 0.06 to 0.07
• k / 1 0.65 to 0.75. It is also provided that the distance d between the crossmember 10 between the rocker arm pivot point 15 and the blade pivot point 6 is greater than b + r.
• a stop 19 of the eye of the piston rod 12 of the tilt cylinder 7 is provided against the eye of the tilt rod 4 or against the blade 6.
• two blade stops 20 are provided against the lifting frame 1 in the tilted-out position.
• FIG. 7 Transport position shown.
• the ratio of the distance m of the axis of the piston rod 12 of the rocker cylinder 7 to the rocker arm pivot point 15 to the distance n of the axis of the rocker rod 4 to the blade pivot point 6, that is to say m / n is on the order of 0.65 to 0.7.

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• Engineering & Computer Science (AREA)
• Mining & Mineral Resources (AREA)
• Civil Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Structural Engineering (AREA)
• Mechanical Engineering (AREA)
• Shovels (AREA)
• Vehicle Body Suspensions (AREA)

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• 1998
  • 1998-01-05 DE DE19800164A patent/DE19800164A1/de not_active Withdrawn
  • 1998-09-04 AU AU92662/98A patent/AU9266298A/en not_active Abandoned
  • 1998-09-04 JP JP2000527716A patent/JP2002500301A/ja not_active Withdrawn
  • 1998-09-04 AT AT98945307T patent/ATE238464T1/de not_active IP Right Cessation
  • 1998-09-04 BR BR9813122-2A patent/BR9813122A/pt active Search and Examination
  • 1998-09-04 DE DE59808101T patent/DE59808101D1/de not_active Expired - Lifetime
  • 1998-09-04 EP EP98945307A patent/EP1045941B1/fr not_active Expired - Lifetime
  • 1998-09-04 WO PCT/EP1998/005602 patent/WO1999035344A1/fr active IP Right Grant

Non-Patent Citations (1)

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