EP2365133B1 - Street construction machine for working on road surfaces - Google Patents

Description

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. Furthermore, 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. In the case of a cold milling machine, the working device is, for example, a cylindrical milling drum, which is arranged in the rear region of the machine frame. The fact that 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. For a stable machine guide, however, it is advantageous if 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. In order to enable with one and the same milling machine on the one hand a close-edge milling and at the same time, if a close-edge milling is not desired to achieve a stable machine guide, located on the null side rear support wheel can be formed horizontally pivotable, so that it pivoted as needed or swung out position is positionable.

For this purpose, it is known to provide 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. In this case, 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. Concretely, 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.

In order to integrate the pivoting of the swivel wheel particularly well in the machine operation, it is also known to provide a swivel gear, which allows the automatic adjustment of the swivel unit between the "Ausschwenkposition" and the "Einschwenkposition" about a pivot axis. The pivot axis is typically vertical and the pivoting movement between the "Einschwenkposition" and the "Ausschwenkposition" in a horizontal plane. A disadvantage of in the DE 196 31 042 C2 However, given pivoting unit is inter alia in their still comparatively high space requirement, which is based causally on the arrangement of the transmission in a horizontal plane. This complicates the placement of the pivoting unit especially in compact road construction machines, especially in the "Einschwenkposition".

Also the DE 10 2004 059 881 shows a generic 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 solution of the problem is achieved with a road construction machine according to the independent claim. Preferred developments are specified in the dependent claims.

The essential idea of the invention lies in the fact that 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. In contrast to the pivot gears previously used in generic road construction machines, which provide the arrangement of the transmission in a horizontal plane, 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. By definition, 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. Although the motion of the individual gear members is thus not uniform in a common plane, the use of a three-dimensional transmission offers significant advantages, such as in particular a much more space-saving design of the entire pivot unit.

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. About the vertically adjustable thrust member ultimately required for the input and Ausschwenkvorgang drive energy is introduced into the spatial transmission. For this purpose, 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. In order to enable the vertical adjustability of the thrust member, a plurality of concrete embodiments is conceivable, for example by the guidance of the thrust member along a vertically extending guide axis.

Another essential aspect of the pivoting transmission according to the invention is that the spatial transmission has a deflection unit. Specifically, 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. For this purpose, at least part of the deflection device is moved spatially and not only in one plane. When the pivoting mechanism according to the invention, it is thus not necessary to arrange all the transmission elements in a horizontal plane. Thus, the swivel gear can be made much more compact and easier in a road construction machine, especially a cold milling machine, are integrated.

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. Thus, for example, it is possible to provide a vertically arranged worm gear on which the thrust member rises and falls vertically by rotation of the worm gear. Alternatively, 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 mehrgliedrig. However, it is advantageous if 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.

Specifically, the deflection device is preferably a rigid and, in particular, one-part deflection element. Such a rigid and in particular one-piece gear member is, for example, particularly low maintenance. At the same time a particularly efficient deflection of the vertical actuating force of the thrust member in a horizontal actuating force for pivoting the pivot arm succeeds. 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. At the other end, a second articulated connection is present on the deflecting member, via which the deflecting member is articulated on the pivoting unit. In relation to the vertical thrust axis, 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 (β) 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. It is further preferred if 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. This is of particular importance when the thrust axis of the thrust member and the pivot axis of the pivot arm according to a further preferred embodiment 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. On the other side, 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.

In order to further improve the ratio between the vertical displacement of the thrust member to the resulting pivoting or translation, 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. An essential feature of this embodiment is that 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.

Ideally, the two deflection members are of identical construction. Thus, 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.

Preferably, 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. At the free end of the inner arm, 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. In order to enable a swinging out and in of the outer arm relative to the inner arm, in this embodiment, 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".

Basically, the adjustment of the outer arm relative to the inner arm, for example, take place with a lying in a horizontal plane gear. For reasons of space, however, it is also better to provide 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. Thus, for example, 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.

For this purpose, 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. Thus, it is for example possible to use the same components for both spatial transmission, which is also advantageous in terms of production costs, etc.

Ideally, 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.

In principle, it is possible to provide a drive unit for the spatial gear between the machine frame and the inner arm and a further separate drive unit for the spatial gear between the inner arm and the outer arm. This special structure makes it possible in particular to make the pivoting from inner arm to outer arm and from inner arm to machine frame independently. However, a much simpler and therefore preferred structure is obtained when the gear units between inner arm and outer arm and between inner arm and machine frame are not applied independently, but rather are functionally coupled to each other. Preferred points of application for such a functional coupling, for example, the respective slide (or the slider of the spatial transmission between the articulation region and the inner arm and the slide of the spatial transmission between the inner arm and the outer arm). In this context, 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. Practically, such 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.

In principle, 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. Preferably, however, the linear actuator is designed as a cylinder-piston unit, in particular as a hydraulic cylinder-piston unit. Usually, 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. If 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.

The aforementioned articulations of the baffle can be varied in a variety of ways. However, ball joint connections have proven to be particularly suitable, since these allow spatial movements of the interconnected members to one another. Ball joint connections are also particularly robust and at the same time comparatively simple. A ball-and-socket joint is known to comprise a joint ball and a partial socket comprising it. In the joints of the deflection, in particular for the case that it is designed as a rigid deflecting member, it has to be advantageous proven to arrange 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

eine Draufsicht auf eine Straßenbaumaschine;

Figuren 2a bis 2d

verschiedene Ansichten der Schwenkeinheit in "Ausschwenkposition";

Figuren 3a bis 3c

verschiedene Ansichten der Schwenkeinheit in "Einschwenkposition";

Figuren 4a und 4b

eine Ausschnittsvergrößerung der Umlenkeinheit in "Ausschwenkposition" (Fig. 4a) und in "Einschwenkposition (Fig. 4b);

Figuren 5a und 5b

eine Prinzipskizze eines räumlichen Gelenks in der Horizontalebene in "Ausschwenkposition" (Fig. 5a) und in "Einschwenkposition" (Fig. 5b); und

Figuren 6a und 6b

eine Prinzipskizze zur Funktionsweise der Umlenkeinrichtung.

In the following the invention will be explained in more detail with reference to drawings. They show schematically:

Fig. 1

a plan view of a road construction machine;

FIGS. 2a to 2d

different views of the swivel unit in "Ausschwenkposition";

FIGS. 3a to 3c

different views of the pivot unit in "Einschwenkposition";

FIGS. 4a and 4b

an enlarged detail of the deflection in "Ausschwenkposition" ( Fig. 4a ) and in "Einwenkposition ( Fig. 4b );

FIGS. 5a and 5b

a schematic diagram of a spatial joint in the horizontal plane in "Ausschwenkposition" ( Fig. 5a ) and in "Einwenkposition" ( Fig. 5b ); and

Figures 6a and 6b

a schematic diagram of the operation of the deflection.

Below the same components are provided with the same reference numerals. For the sake of clarity, not every component repeated in the figures is again marked in each figure.

The basic arrangement of the support wheels in relation to the machine frame and the working equipment goes out Fig. 1 out. 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. For this purpose, 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".

Out 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. Thus, 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. For pivoting the support wheel 5, the road construction machine has a pivot unit with a pivoting gear, which in the FIGS. 2a to 4b is specified in more detail. In Fig. 1 the position of this pivoting unit is given only for rough orientation by the dotted circle. When swiveling in and out, the in Fig. 1 shown embodiment, the running direction of the pivotable support wheel 5 to. However, it is also possible that the support wheel 5 form in such a way that it maintains its running direction in the positions 5a and 5b.

The 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 3c are perspective oblique views and 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 and Fig. 4b is an enlarged detail of a portion of the pivot gear Fig. 3c ,

First, the basic structure of the pivot gear will be explained in detail. For clarity, the entirety of the FIGS. 2a to 4b recourse and not repeatedly to each element in each figure received.

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 verlaufendem Joint pin differentiated. The hinge region 9 is thus part of the machine frame, whose further course in the FIGS. 2a and 3a is indicated by the two dashed lines by way of example. Concretely, 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.

In the in the FIGS. 2a to 4b 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. For this purpose, 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.

Further details of the basic structure of the pivoting gear of the illustrated embodiment, for example, go in particular from the perspective oblique view in Fig. 2c out. The viewing direction for the representation of the pivoting unit 8 in Fig. 2c is in Fig. 2a indicated by the arrow b. 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. At the articulation region 9, 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.

Finally, 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.

An essential aspect of the invention lies in the design of the pivoting gear as a spatial transmission, as will be described in more detail below. In addition to the transmission elements already mentioned, 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. Furthermore, 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. In comparison, 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. In 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.

First, for a more detailed explanation of the operation of the pivoting gear in the FIGS. 2a to 4b a Einschwenkvorgang be described. The support wheel 5 is thus initially in the "Ausschwenkposition" 5a and is pivoted into its "Einschwenkposition" 5b. Starting point of this movement is thus in the FIGS. 2a to 2d and in Fig. 4a specified position of the swivel gear. End point of the pivoting movement, however, is in the FIGS. 3a to 3c as well as in the Fig. 4b specified position of the swivel gear. The basic sequence of movements in particular of the deflecting members 23, 24, 25 and 26 in relation to the linear actuator 27 will be described below first by means of a position comparison of FIGS. 4a and 4b respectively.

The drive of the Einschwenkbewegung 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. As a result of the "lifting movement" of the thrust unit 27 or the retraction of the piston 29 into the cylinder 28, 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. By retracting the piston 29 into the cylinder 28 are thus on the connecting web 30 and the slide 21 and 22 in the direction c (in FIG A thus up) along the hinge pin shifted. At the outer edge, 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. 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 Einschwenkrichtung. In this case, only the respective transmitted by the corresponding deflecting member 23, 24, 25 or 26 horizontal component comes into play, 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 Anlenkbereichs 9, which thus represents a kind of forced operation. These can not follow the (also forcibly guided) vertical movement in the direction of arrow c. As a result, a vertical displacement (in the z-direction) of the slides 21 and 22 in the direction of arrow c to a horizontal (in the xy plane) Einschwenkung the pivot arm 10, wherein the outer arm 11 relative to the inner arm 12 in the direction of arrow d and the inner arm 12th pivots in the direction of arrow e relative to the articulation area 9 or relative to the machine frame. Conversely, results in a vertical displacement of the slide 21 and 22 in the direction of arrow c 'by an extension of the piston 29 from the cylinder unit 28 in the vertical downward direction in a horizontal swiveling out of the pivot arm 10, the outer arm 11 relative to the inner arm 12 in the direction of arrow d' and the Inner arm 12 with respect to the articulation region 9 or relative to the machine frame in the direction of arrow e 'swings.

The principal mode of operation of this force deflection is schematically further in the principle Figures 5a and 5b illustrated. These 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 α between the articulation region 9 and the inner arm 12 in the horizontal plane is indicated by α1 to α2. Now, 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.

To illustrate the principal mode of action of this deflection of a vertical movement in a horizontal movement even closer, is on the Figures 6a and 6b directed. The Figures 6a and 6b sketchy give the movement of the respective gear members from the FIGS. 5a and 5b again, being in the Figures 6a and 6b For the sake of clarity, a concrete representation of the pivoting movement has been dispensed with. In contrast to the pivoting mechanism according to the invention the outer arm 12 'is thus not pivoted in the xy plane, but only linearly displaced in the xy plane to the outside. The outer arm 12 'is thus guided linearly guided and not pivotally mounted in the horizontal plane. Due to this difference, the corresponding reference numerals are also each marked with a '. Starting from Fig. 6a It is clear that an adjustment of the slider 22 'in the direction of arrow c the position angle of the longitudinal axis of the deflecting member 25' relative to the horizontal plane (dashed line) reduced or approaches 0 °. The length of the deflecting member 25 'in the horizontal plane increases from L1' to L2 '. By this relative change in length of projected into the horizontal plane length of the deflecting member 25 '(or specifically the distance between the two articulated joints 125a' and 125b '), the positively driven inner arm 12' is displaced outwards. When the movement of the slider 22 'is reversed, the individual parts move into the in Fig. 6b indicated arrow directions.

The swivel gear of the invention goes over this in the Figures 6a and 6b shown basic structure now so far beyond that the inner arm 12 'is not linearly displaceably mounted in the horizontal plane, but pivotally, for example by the articulation of the inner arm 12 on the pivot joint 13. This is obtained in contrast to the linear forced guidance a swivel forced operation, which ultimately is used for swinging in and out of the support wheel located on the zero side. Transferred to the FIGS. 5a and 5b Thus, it follows that the vertical movement of the slider 22 along the hinge connection of the Image plane out to a relative change in length L1 L2 from Fig. 5a to Fig. 5b leads, as a result, the two legs 12 and 9 are moved toward each other (according to the specified angle α1 and α2.

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.

Claims (17)

1. A road construction machine (1) for processing roadways,

   - with an automotive travelling mechanism with a steerable front axle of said travelling mechanism comprising at least one support wheel (2, 3) and two rear support wheels (4, 5);

   - with a working device (6) which is mounted in or on the machine frame and is approximately flush with said machine frame on one side, namely its so-called zero side (7);

   - with a pivot unit (8) comprising an articulation area (9) formed by the machine frame and a pivot arm (10) which carries the rear support wheel (5) on the zero side (7) at its one end and is pivotally articulated at its other end to the articulation area (9) of the machine frame, the pivot unit (8) being implemented in such a manner that it can be pivoted between an "outwardly pivoted position", in which the rear wheel (5), which is on the zero side (7), is pivoted outwardly to an outer end position (5a) parallel to the longitudinal direction of the machine frame, and an "inwardly pivoted position", in which the rear support wheel (5), which is on the zero side (7), is inwardly pivoted to an inward end position (5b) parallel to the longitudinal direction of the machine frame, and

   - with a pivot gear which controls the adjustment of the pivot unit (8) between the "outwardly pivoted position" and the "inwardly pivoted position" about a pivot axis (17)
   characterized in that
   the pivot gear is a spatial gear with a thrust member (21, 22) which is adjustable in the vertical direction, and that it comprises a deflection device which is implemented in such a manner that it deflects the vertical movement of the thrust member (21, 22) to a horizontal inwardly and outwardly pivoting movement of the pivot arm (10).
2. The road construction machine (1) according to claim 1,
   characterized in that
   the spatial gear is a coupling gear.
3. The road construction machine (1) according to any one of the preceding claims,
   characterized in that
   the thrust member (21, 22) comprises a slide (22) which is guided along a vertically extending thrust axis and the deflection device is arranged between the slide (22) and the pivot arm (10).
4. The road construction machine (1) according to claim 3,
   characterized in that
   the deflection device comprises a rigid deflection member (23, 24) which is articulated to the slide (22) via a first link joint and is articulated to the pivot unit (8) via a second link joint, the longitudinal axis between the two link joints being disposed at an angle (β) of 0 to less than 90° relative to the horizontal pivot plane of the pivot arm (10).
5. The road construction machine (1) according to any one of the preceding claims,
   characterized in that
   the thrust axis of the thrust member (22) and the pivot axis (17) of the pivot arm (10) are arranged coaxially.
6. The road construction machine (1) according to any one of the preceding claims,
   characterized in that
   the deflection device comprises a further deflection member (25, 26) which is articulated to the thrust member (22), the one deflection member (26) being articulated with its free end to the articulation area (9) on the side of the machine frame and the other deflection member (25) being articulated with its free end to the pivot arm (10).
7. The road construction machine (1) according to claim 6,
   characterized in that
   the two deflection members (25, 26) are structurally identical.
8. The road construction machine (1) according to any one of the preceding claims,
   characterized in that
   the pivot arm (10) is arranged with several members, especially two members, comprising an inside arm (12) and an outside arm (11), the inside arm (12) being horizontally pivotable relative to the articulation area (9) on the side of the machine frame and the outside arm (11) being horizontally pivotable relative to the inside arm (12), respectively.
9. The road construction machine (1) according to claim 8,
   characterized in that
   the spatial gear comprises a further deflection device which deflects the vertical movement of the thrust member into a horizontal pivoting of the outside arm (11) relative to the inside arm (12).
10. The road construction machine (1) according to claim 9,
    characterized in that
    the further deflection device also comprises a slide (21), the thrust axis of which extends coaxially to the pivot axis (18) between the inside arm (12) and the outside arm (11).
11. The road construction machine (1) according to claim 10,
    characterized in that
    the thrust axes of the slides (21, 22) and the pivot axes (17, 18) of the pivot device extend parallel with respect to each other.
12. The road construction machine (1) according to any one of claims 10 or 11,
    characterized in that
    both slides (21, 22) are functionally coupled with each other.
13. The road construction machine (1) according to claim 12,
    characterized in that
    a connecting bridge (30) is provided for functional coupling between the two slides (21, 22).
14. The road construction machine (1) according to any one of claims 10 to 13,
    characterized in that
    the slides (21, 22) are triggered by a joint thrust drive.
15. The road construction machine (1) according to claim 14,
    characterized in that
    the thrust drive (27) is mounted on the inside arm (12).
16. The road construction machine (1) according to claim 15,
    characterized in that
    the inside arm (12) is implemented as L-shaped, the shorter limb (31) of the L-shaped inside arm (12) being articulated to the articulation area (9) on the side of the machine frame and the longer limb (32) being articulated to the outside arm (11).
17. The road construction machine (1) according to any one of the preceding claims,
    characterized in that
    the link joints of the deflection device comprise ball joints (123a, 123b, 124a, 124b, 125a, 125b, 126a, 126b), especially the link joints of at least one gear member (23, 24, 25, 26) being ball joints (123a, 123b, 124a, 124b, 125a, 125b, 126a, 126b) and the at least one deflection member (23, 24, 25, 26) preferably comprising the respective ball sockets.

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