EP2365133A2 - Engin de construction routière destiné à traiter les chaussées - Google Patents

Engin de construction routière destiné à traiter les chaussées Download PDF

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Publication number
EP2365133A2
EP2365133A2 EP20110000323 EP11000323A EP2365133A2 EP 2365133 A2 EP2365133 A2 EP 2365133A2 EP 20110000323 EP20110000323 EP 20110000323 EP 11000323 A EP11000323 A EP 11000323A EP 2365133 A2 EP2365133 A2 EP 2365133A2
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EP
European Patent Office
Prior art keywords
arm
road construction
construction machine
pivoting
articulated
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20110000323
Other languages
German (de)
English (en)
Other versions
EP2365133B1 (fr
EP2365133A3 (fr
Inventor
Jens Wagner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bomag GmbH and Co OHG
Original Assignee
Bomag GmbH and Co OHG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bomag GmbH and Co OHG filed Critical Bomag GmbH and Co OHG
Publication of EP2365133A2 publication Critical patent/EP2365133A2/fr
Publication of EP2365133A3 publication Critical patent/EP2365133A3/fr
Application granted granted Critical
Publication of EP2365133B1 publication Critical patent/EP2365133B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C23/00—Auxiliary devices or arrangements for constructing, repairing, reconditioning, or taking-up road or like surfaces
    • E01C23/06—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road
    • E01C23/08—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for roughening or patterning; for removing the surface down to a predetermined depth high spots or material bonded to the surface, e.g. markings; for maintaining earth roads, clay courts or like surfaces by means of surface working tools, e.g. scarifiers, levelling blades
    • E01C23/085—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for roughening or patterning; for removing the surface down to a predetermined depth high spots or material bonded to the surface, e.g. markings; for maintaining earth roads, clay courts or like surfaces by means of surface working tools, e.g. scarifiers, levelling blades using power-driven tools, e.g. vibratory tools
    • E01C23/088—Rotary tools, e.g. milling drums

Definitions

  • the invention relates to a road construction machine for working on roadways, in particular a cold milling machine for road surface removal.
  • a generic road construction machine is for example from the DE 196 31 042 C2 is known, whose basic structure is hereby incorporated by reference.
  • the milling machine disclosed there has a self-propelled chassis. On the self-propelled chassis a total of four support wheels, two front and two rear, are arranged, wherein also embodiments with only one front jockey wheel are known.
  • the front suspension axle is designed steerable.
  • a working device mounted in or on the machine frame is provided, which terminates approximately flush with the machine frame on one side, namely on the so-called zero side of the machine frame.
  • the working device is, for example, a cylindrical milling drum, which is arranged in the rear region of the machine frame.
  • the milling drum is arranged in such a way that it terminates with an end face almost flush with the side edge of the machine frame, the machine can also mill close to the edge, since the working device can be moved directly past the edge.
  • the two rear support wheels surround the milling drum along its axis of rotation to both sides and lie in the working direction of the mill at a height. It is therefore also known to arrange the rear support wheel located on the neutral side laterally from the front side of the working device, so that it projects laterally beyond the machine frame.
  • a pivoting unit on the milling cutter comprising an articulated region formed by the machine frame and a swivel arm which carries at one end the rear support wheel located on the neutral side and is pivotably articulated at its other end to the articulation region of the machine frame.
  • the articulation region of the swiveling unit designates that part of the machine frame in which the articulation bearing for the swiveling arm which can be pivoted in and out is arranged on the machine frame. This does not only apply to the immediate area of contact of the corresponding articulated connection, but rather also to the part of the machine frame adjacent to this area.
  • the swing unit is formed to swing between a "swing-out position" in which the rear support wheel located at the neutral side is swung out in an outer end position parallel to the longitudinal direction of the machine frame and a "swing-in position" at the zero side located rear support wheel is pivoted in a direction parallel to the longitudinal direction of the machine frame inner end position, is pivotable. If a close-to-edge milling is desired or if the road construction machine is to be as narrow as possible for transport purposes in the longitudinal direction, the rear support wheel located on the neutral side is thus pivoted into the "pivoting position". Alternatively, it is also possible to swing out the support wheel in its "Ausschwenkposition" and so for example to improve the handling characteristics of the road construction machine.
  • the invention is therefore an object of the invention to provide a road construction machine of the type mentioned, in particular a cold milling machine, which allows easy pivoting in and out of the rear located on the zero side jockey wheel, works reliably and at the same time has a small footprint.
  • the swivel gear is a three-dimensional gear with a vertically adjustable thrust member, and that it has a deflection device which is designed in such a way that it causes the vertical movement of the thrust member in a horizontal pivoting in and out of the Swivel arm deflects.
  • the invention thus goes in a completely new direction and suggests the use of a spatial transmission and not just a lying in a plane transmission.
  • a spatial gear is characterized in that link points of at least one gear element can perform a spatial movement relative to at least one other gear element.
  • An essential component of the pivoting gear according to the invention is the adjustable in the vertical direction thrust member.
  • the term "vertical direction" refers to the direction of the thrust member in the installed state on a generic road construction machine. In essence, it is important that the thrust member runs at right angles to the (horizontal) pivoting plane of the pivot arm.
  • the push member is connected to a suitable drive unit, which is specified below by way of example.
  • the driven by the drive unit vertical adjustment movement of the thrust member may consist both in a lifting and in a lowering movement along the vertical axis, depending on whether ultimately a pivoting or pivoting of the pivot arm is desired.
  • a plurality of concrete embodiments is conceivable, for example by the guidance of the thrust member along a vertically extending guide axis.
  • the spatial transmission has a deflection unit.
  • the deflection unit serves to deflect the vertical adjustment movement driven by the drive unit in such a way that the horizontally adjustable swing arm moves from its "pivoting position" into its "swing-out position”. and vice versa can be pivoted.
  • the deflection thus deflects the introduced via the thrust member in the spatial transmission vertical force ultimately in a horizontal force acting on the pivoting force.
  • the deflection device thus refers to that part of the spatial transmission which receives the vertical movement of the thrust member and thereby triggers the horizontal movement of the pivot arm.
  • at least part of the deflection device is moved spatially and not only in one plane.
  • the spatial pivoting gear according to the invention thus sets the linear vertical movement of the thrust member in a horizontal pivoting movement at least about the pivot axis of the pivot arm.
  • the spatial transmission is accordingly preferably designed as a coupling gear, wherein the coupling between the pivot arm and the thrust member is arranged.
  • the thrust member may be formed in different ways.
  • the thrust member along a vertically extending, in particular bolt-like, axis, particularly preferably along a pivot axis, guided, wherein the drive unit is arranged in the vertical direction next to the thrust member.
  • Such linearly guided slides can thus constructively realize in many ways and are characterized at the same time by a high functional reliability.
  • All alternative embodiments according to the invention have in common that the slide is guided along a vertically extending thrust axis.
  • the push axis refers to the axis of movement, along which the slider can be adjusted vertically.
  • the thrust axis refers to the respective center of a horizontal section through the slider.
  • the interposition of several intermediate links between the slide and the swivel arm is in principle possible.
  • the deflection can therefore also be designed Matchedrig.
  • the deflection device is arranged as directly as possible between the slider and the pivoting arm, in particular directly.
  • the direct articulation of the deflection on the one hand on the slider and on the other hand on the pivot arm allows a particularly favorable power transmission, since, for example, friction losses are particularly low.
  • the coupling of the deflecting device, for example on the slider and on the pivot arm preferably takes place via suitable articulated connections, such as ball joint connections.
  • the deflection device is preferably a rigid and, in particular, one-part deflection element.
  • a rigid and in particular one-piece gear member is, for example, particularly low maintenance.
  • the deflecting member may for example be designed rod-shaped, cylindrical, etc. Basically, such deflecting members are preferred due to their simple structure, which extend at least in a straight line direction.
  • the rigid deflecting member is articulated on one side via a first articulated connection, in particular directly, on the slide.
  • a second articulated connection is present on the deflecting member, via which the deflecting member is articulated on the pivoting unit.
  • the articulation of the rigid deflecting member on the slide is further preferably in such a way that the longitudinal axis between the two articulated joints at an angle ( ⁇ ) from 0 to less than 90 ° relative to the horizontal pivot plane of the pivot arm (10) in each case the smallest angle is determined.
  • the first articulated connection is at a right angle projection in the horizontal pivot plane eccentric to the thrust axis or not on the but next to the thrust axis.
  • the thrust axis of the thrust member and the pivot axis of the pivot arm are arranged coaxially.
  • This particular embodiment has the advantage that, for example, a bolt mounted along the pivot axis between the articulation area and the pivot arm can simultaneously be used to guide the push element.
  • the rigid deflecting member of the deflecting device is articulated via a second articulated connection to the horizontally pivotable pivoting unit.
  • a vertical displacement of the thrust member thus results in a spatial change in position of the rigid deflection member of the deflection, which triggers a horizontal pivoting of the pivot arm as a result of their simultaneous articulation on the horizontally pivotable pivot unit and the vertically displaceable slide.
  • This is possible in particular also because both the pivot arm relative to the articulation region (pivotable in the horizontal plane) and the thrust member relative to the leadership of the thrust member (displaceable along the vertical axis), for example, the hinge pin, each positively guided.
  • the deflection device in another preferred embodiment, another deflecting articulated on the thrust member, wherein the one deflecting member with its free end on the machine frame and the other Deflection member is articulated with its free end on the pivot arm.
  • the deflection device thus has two deflection members per push member. One of the two deflection members acts between the push member and the machine frame and the other of the two deflection members acts between the push member and the swing arm.
  • the two deflection members are of identical construction.
  • the total number required for the production of the road construction machine according to the invention required number of different parts can be reduced, which is advantageous for example for the production costs or for ensuring the spare parts supply.
  • the pivot arm is multi-membered and in particular formed in two parts, comprising an inner arm and an outer arm.
  • the inner arm of the swivel arm is hinged horizontally on the machine frame.
  • the outer arm connects to the support wheel is finally stored to the outside or directly to the outside.
  • the outer arm is pivotable horizontally relative to the inner arm. This results in a lying in the horizontal plane kinematic chain in the order machine frame, inner arm and outer arm.
  • This embodiment makes it possible for the pivot arm to be bendable or also pivotable between inner arm and outer arm.
  • a suitable transmission is provided, via which the pivoting of the outer arm is controlled relative to the inner arm.
  • This embodiment is advantageous in that the pivot arm can be "folded” even in the horizontal plane, which greatly facilitates the adjustment of the pivot arm between the "Einschwenkposition” and the “Ausschwenkposition”.
  • the adjustment of the outer arm relative to the inner arm takes place with a lying in a horizontal plane gear.
  • a spatial gear in particular with the basic structure set out above, via which the pivoting movement of the outer arm relative to the inner arm is achieved.
  • a further deflection device may be present, which is designed in such a way that it deflects the vertical movement of a vertically adjustable thrust member in a horizontal pivoting in and out of the outer arm relative to the inner arm.
  • a slider is also advantageously present, the thrust axis runs coaxially to the pivot axis between the inner arm and outer arm.
  • the spatial gear for pivoting the inner arm relative to the machine frame and the spatial transmission for pivoting the outer arm relative to the inner arm are thus preferably functionally similar.
  • the thrust axes of the existing slides and the pivot axes of the pivoting device between the articulation region and the inner arm and between the inner arm and the outer arm are parallel to one another. This ensures on the one hand that the inner arm and the outer arm are pivotable against each other and relative to the machine frame in a common plane. On the other hand, the thrust axes of the slides are orthogonal to this plane, which in particular a particularly compact design can be obtained.
  • a functional coupling is, in particular, an interconnection of the two slides in such a way that both slides can only be moved together. A movement of the one slider thus simultaneously leads to a movement of the other slider.
  • a functional coupling can be achieved in a particularly favorable manner, for example with a connecting element, in particular a one-piece connecting web, between the two slides. With this connecting bar, both slides are thus mechanically interconnected.
  • the main advantage of a functional coupling of the two slides is particularly in the fact that so that the control of the two slides on a common linear actuator is possible.
  • the drive unit of the transmission or the linear actuator for the slide can be obtained in different ways.
  • the linear actuator is in the Formed that he can adjust the slider along its vertical axis of thrust up and down.
  • a suitable thrust drive for example, be a corresponding worm gear, along which, depending on the embodiment, the slide is driven directly or indirectly via corresponding connecting elements.
  • the linear actuator is designed as a cylinder-piston unit, in particular as a hydraulic cylinder-piston unit.
  • road construction machines and in particular milling already have a hydraulic system, for example for driving the support wheels via corresponding hydraulic motors and / or for driving the working device on.
  • a thrust drive is provided in the form of a cylinder-piston unit, it is thus possible to connect the thrust drive to the hydraulic system which is usually already present in a road construction machine and in particular a milling machine. Even so, for example, the production costs or maintenance costs can be reduced.
  • the thrust drive is also preferably mounted on the inner arm.
  • Such storage is advantageous in that a simultaneous mechanical transmission of the force exerted by the thrust drive on the thrust member actuating force on the respective slide of the spatial transmission between the inner arm and outer arm or between the inner arm and the machine frame succeeds particularly easy. All transmitting elements, such as a connecting web for mechanical coupling of the two slides can then be stored together on the inner arm and are moved with this.
  • the inner arm is also preferably L-shaped, wherein the L-shaped configuration refers to the contour of the inner arm in the horizontal pivot plane of the pivot arm.
  • the shorter leg of the L-shaped inner arm is advantageously articulated in this embodiment on the machine frame, whereas the longer leg is articulated on the outer arm.
  • This embodiment has proven to be advantageous in that it allows a particularly space-saving articulation on the machine frame, without affecting the pivoting of the swing arm negative.
  • a ball-and-socket joint is known to comprise a joint ball and a partial socket comprising it.
  • the sockets in the deflector and the corresponding joint balls on the opposite gear part, such as the machine frame, the slider, the inner arm or the outer arm.
  • Fig. 1 is a schematic plan view of a road construction machine, specifically a cold planer. Thereafter, the road construction machine 1 has a total of two front support wheels 2 and 3 and two rear support wheels 4 and 5. Furthermore, a working device 6 is provided, which on one side (in Fig. 1 on the right side) almost flush with the machine frame. According to the embodiment Fig. 1 is it in the working device 6 concretely to a substantially cylindrical milling drum, which is suitable for example for the removal of road surfaces made of concrete, asphalt or the like.
  • the working device 6 is lowered onto the surface to be processed, set in rotation and the road construction machine 1 is moved over the road surface in the direction of the arrow a.
  • the arrow direction a is thus in Fig. 1 and also in the following figures, the movement of the road construction machine in "forward direction”.
  • Fig. 1 also shows that the support wheel 5 between a "Ausschwenkposition” 5a and a “Einschwenkposition” 5b is pivotable.
  • the support wheel 5 can thus from the in Fig. 1 indicated swung-out position 5a, in which it protrudes laterally beyond the machine frame, are pivoted into the position shown in dashed lines 5b, in which it no longer protrudes laterally beyond the machine frame.
  • the road construction machine can be moved with the support wheel 5 in position 5b, for example, on building walls, etc. and a near-edge milling is possible on the side at which the working device 6 is almost flush with the machine frame. This side of the machine frame is referred to below zero page 7.
  • the road construction machine has a pivot unit with a pivoting gear, which in the FIGS. 2a to 4b is specified in more detail.
  • the position of this pivoting unit is given only for rough orientation by the dotted circle.
  • the running direction of the pivotable support wheel 5 to.
  • the support wheel 5 form in such a way that it maintains its running direction in the positions 5a and 5b.
  • FIGS. 2a to 2d and 4a give details of the pivot unit in the "Ausschwenkposition” 5a and the FIGS. 3a to 3c and 4b in the "Einschwenkposition” 5b.
  • Both FIGS. 2a, 2b 3a 3b are each in the plan view, where in the FIGS. 2b and 3b in proportion to the FIGS. 2a and 3a the upper base plate 15a is removed in each case, so that the view of the pivoting arm 10 is released.
  • the Figures 2c and FIG. 3c are perspective and perspective views Fig. 2d shows the pivot arm 10 with corresponding gear parts.
  • Fig. 4a is an enlarged detail of a portion of the pivot gear Fig. 2b
  • Fig. 4b is an enlarged detail of a portion of the pivot gear of Fig. 3c.
  • the swivel unit 8 initially comprises an articulated region 9 formed by the machine frame and a swivel arm 10.
  • the swivel arm 10 is horizontally pivotable (in the xy plane) and articulated via a suitable articulated connection 13 on the machine frame side articulation region 9.
  • the articulated connection 13 (and also the joint connection 14 mentioned below) each have a hinge pin whose longitudinal axis extends in the vertical direction and is coaxial with the pivot axis 17 or 18. The sake of clarity is not further below between the pivot axis 17 and 18 and the coaxial with the pivot axis 17 and 18 ver noteworthydem Joint pin differentiated.
  • the hinge region 9 is thus part of the machine frame, whose further course in the FIGS.
  • the articulation region 9 comprises the region of the machine frame surrounding the articulated connection 13, as shown in FIG Fig. 2a is indicated with the dotted area.
  • the articulation region 9 also includes, in particular, the part of the machine frame on which the deflecting device, which is specified in greater detail below, is articulated on the machine frame side.
  • the articulation region 9 thus comprises at least the part of the machine frame on which the articulated connection 13 is mounted to the pivot arm 10 and the part of the machine frame, on which the deflection device is articulated on the machine frame side.
  • the outer arm 11 is located at the outer free end of the pivot arm 10 and the inner arm 12 connects the outer arm 11 with the machine frame side articulation area 9.
  • the outer arm 11 has a suspension, not shown, on which the support wheel 5 is suspended, as in Fig. 2a is further illustrated by the support wheel 5 shown in dashed lines.
  • the outer arm 12 is mounted horizontally pivotable relative to the inner arm 11.
  • a hinge connection 14 is present, which is concretely a vertically extending hinge pin, which is guided by the outer arm 12 and by the inner arm 11.
  • the hinge pin also extends coaxially to the corresponding pivot axis 18 of the articulated connection 14.
  • the inner arm 11 is in turn pivoted horizontally pivotably on the articulation region 9 of the machine frame with the articulated connection 13.
  • the articulation region 9 has two horizontal base plates 15a and 15b, which are interconnected via an intermediate plate 15c.
  • This articulation area comprising the base plates 15a and 15b and the intermediate plate 15c, is fixedly connected to the rest of the machine frame of the road construction machine 1 and thus also forms part of the machine frame.
  • the pivot arm 10 connects with its outer arm 11 and the inner arm 12 at.
  • the outer arm 11 carries a suspension shown only 16, at the lower end ultimately the rear support wheel 5 (only in Fig. 2a shown in dashed lines) is arranged.
  • the inner arm 12 is mounted horizontally (xy plane) pivotably on the articulation region by means of the articulated connection 13.
  • the articulated connection 13 makes it possible for the inner arm 12 to be mounted pivotably about the rotation axis 17 on the articulation region 9.
  • a further articulated connection 14 connects the outer arm 11 pivotally with the inner arm 12.
  • the pivot axis 17 of the articulated connection 13 and the pivot axis 18 of the articulated connection 14 each pass through a hinge pin of the respective articulated connection 13 or 14 and lie parallel to one another.
  • the inner arm 12 is fork-like enclosed by the overlapping part with the base plates 15a and 15b and also has an upper plate 19a and a lower plate 19b. Also, the two plates 19a and 19b of the inner arm 12 are interconnected via an intermediate plate 19c.
  • the outer arm 11 is fixedly arranged on the one hand on the suspension 16. It further includes for connection to the inner arm, the plates 19a and 19b, which are connected to each other with the intermediate plate 19c. In the region of the articulated connection 14, the plates 19a and 19b surround the outer arm in the axial direction of the pivot axis 18 on both sides.
  • the pivoting gear furthermore has two annular slides 21 and 22 which are guided along the hinge pins between the articulation region 9 and inner arm 12 or inner arm 12 and outer arm 11 in the vertical direction or along the pivot axis 17 and 18, respectively.
  • the slides 21 and 22 are thus traversed in the vertical direction in each case by one of the articulated joints.
  • Another element of the swivel gear is mounted on the inner arm 12 thrust drive 27 comprising a cylinder 28 and a piston 29.
  • the cylinder 28 and the piston 29 in their entirety form a hydraulically actuated cylinder-piston unit.
  • Essential to the basic structure of the pivoting unit according to the FIGS. 2a to 4b is also a connecting web 30 which connects the two slides 21 and 22 together and is driven by the piston 29 of the pusher unit 27.
  • the position of the thrust drive 27 is selected in such a way that the piston 29 is articulated centrally.
  • the thrust drive 27 is in other words in the horizontal plane thus exactly between the two pivot axes 17 and 18, along which the slides 21 and 22 are adjustable, arranged.
  • the linear actuator 27 is also connected to the hydraulic system of the road construction machine 1, which is not shown in detail in the figures for the sake of simplicity.
  • four rigid deflecting members 23, 24, 25 and 26 are present, whose arrangement and function will be described in more detail.
  • Fig. 2a shows the pivot unit 8 in plan view.
  • the plate 15a is in Fig. 2b removed and gives the view of the swing arm 10 free (the same applies, moreover, for Fig. 3b in relation to Fig. 3a ).
  • the deflecting members 23, 24, 25 and 26 are at their ends respectively via ball joint connections 123a, 123b, 124a, 124b, 125a, 125b, 126a and 126b (the numbering of the respective ball joint connection is given by the number of the deflector and a prefixed 1; "upper” ball joint is respectively connected with “a” and the lower one in each case with “b") with the corresponding functionally adjacent gear member.
  • This goes, for example, in particular from the Figures 2c . 2d , 3c and 4a out.
  • Numerals 123a, 123b, 124a, 124b, 125a, 125b, 126a and 126b each indicate a ball and socket joint and each includes a socket and a ball head.
  • the respective joint socket of each articulation of the deflecting members 23, 24, 25 and 26 is formed on the respective deflecting member, whereas the corresponding joint ball is arranged on the by the deflecting member 23, 24, 25 or 26 hinged gear member, such as the inner arm 12.
  • the individual figures only the visible ball joint connections 123a, 123b, 124a, 124b, 125a, 125b, 126a and 126b are designated. The interaction of the individual listed components will be explained in more detail below.
  • the drive of the Einschwenkterrorism takes place by the retraction of the piston 29 in the direction of arrow c.
  • Arrow direction c is vertical (in the z direction) or orthogonal to the pivot plane (xy plane) of the pivot arm 10.
  • the two pivot axes 17 and 18 also extend vertically.
  • the connecting web 30 is likewise moved in the direction of the arrow c, that is to say in the vertical direction upwards.
  • the connecting web 30 is connected at its two ends with the sliders 21 and 22, along the respective hinge pin of the hinge connection 13 and 14 are guided.
  • the connecting web 30 is rigid and thus transmits the movement of the thrust unit 27 on the two slides 21 and 22.
  • the sliders 21 and 22 each have two ball joint heads which are part of the ball joint connections 123b, 124b, 125b and 126b, respectively, and establish an articulated connection from the sliders 21 and 22 to the corresponding deflection members 23, 24, 25 and 26. With the slides 21 and 22, therefore, also move on the slide 21 and 22 respectively mounted ends of the deflecting members 23, 24, 25 and 26 upwards.
  • deflecting members 23, 24, 25 and 26 Due to the rigid design of the deflecting members 23, 24, 25 and 26, however, they press with their slides 21 and 22 opposite free ends against the outer arm 11 (deflector 23) and the inner arm 12 (deflectors 24 and 25) or the articulation area 9 (deflecting 26) in Einschwenkraum.
  • the 13 and 14 each alone a horizontal movement is possible by the above-described arrangement of the two articulated joints.
  • This deflection of the force applied by the thrust unit 27 in the vertical direction in a pivoting movement in the horizontal direction is thus essentially the result of exclusively horizontal pivoting of the outer arm 11, the inner arm 12 and the Anlenk Schemes 9, which thus represents a kind of forced operation.
  • FIGS. 5a and 5b show in a plan view the basic structure of a hinge connection, specifically using the example of the articulated connection 13 between the inner arm 12 and the articulation region 9, wherein only the area adjacent to the articulated connection 13 is shown in FIGS. 5a and 5b.
  • the FIGS. 5a and 5b make the movement thus in one Top view along the pivot axis 17, ie in the horizontal xy plane, is.
  • Fig. 5a is doing the "Ausschwenkposition” 5a again and Fig. 5b the "Einschwenkposition” 5b.
  • the angle ⁇ between the articulation region 9 and the inner arm 12 in the horizontal plane is indicated by ⁇ 1 to ⁇ 2.
  • the slider 22 is adjusted along the pivot axis or along the hinge pin of the hinge joint 13 in the vertical direction, specifically from Fig. 5a starting in the direction of the viewer in Fig. 5b shifted, this leads to a relative change in length of the deflecting members 25 and 26 in the horizontal plane, which is characterized by L1 and L2. This triggered by the vertical movement of the slider 22 relative change in length in the horizontal plane ultimately represents an essential aspect of the deflection.
  • Another essential aspect resulting from the figures is the relative positional arrangement of the ball-and-socket joints 123b, 124b, 125b and 126b on respectively associated slides 21 and 22. Accordingly, the ball joint lies next to the pivot axis 17 or 18 when projecting into the horizontal pivot plane or eccentric to the pivot axis. As a result, the respective deflection element 23, 24, 25 or 26 can transmit the required energy in the pivoting direction to the inner arm 12 or outer arm 13 to be pivoted.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Jib Cranes (AREA)
  • Transmission Devices (AREA)
  • Manipulator (AREA)
  • Vehicle Body Suspensions (AREA)
EP11000323.3A 2010-03-02 2011-01-17 Engin de construction routière destiné à traiter les chaussées Active EP2365133B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010009834 2010-03-02
DE102010034662A DE102010034662A1 (de) 2010-03-02 2010-08-18 Straßenbaumaschine zum Bearbeiten von Fahrbahnen

Publications (3)

Publication Number Publication Date
EP2365133A2 true EP2365133A2 (fr) 2011-09-14
EP2365133A3 EP2365133A3 (fr) 2015-03-11
EP2365133B1 EP2365133B1 (fr) 2015-12-23

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US (1) US8297876B2 (fr)
EP (1) EP2365133B1 (fr)
CN (1) CN102191741B (fr)
DE (1) DE102010034662A1 (fr)

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DE102012214929A1 (de) * 2012-08-22 2014-02-27 Wirtgen Gmbh Straßenfräsmaschine zum Bearbeiten von Straßenbelägen, sowie Verfahren zum Verschwenken eines Laufwerks einer Straßenfräsmaschine
DE102012021379B4 (de) * 2012-10-31 2021-09-09 Bomag Gmbh Bodenfräsmaschine mit schwenkbarer Fahreinrichtung
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EP2365133B1 (fr) 2015-12-23
CN102191741A (zh) 2011-09-21
CN102191741B (zh) 2013-10-30
DE102010034662A1 (de) 2011-09-08
EP2365133A3 (fr) 2015-03-11
US20110217120A1 (en) 2011-09-08
US8297876B2 (en) 2012-10-30

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