CN101870303B - Break/pendulum steering gear - Google Patents

Abstract

The invention relates to a bending and swinging steering device for construction machinery with a front vehicle and a rear vehicle. On the rear carriage, where the first and second stationary elements are connected to each other via a ball joint and a swivel/sliding bearing movable tangentially to the ball joint.

Description

Bending/Swing Steering

technical field

The invention relates to a bending/swing steering device and an engineering machine.

Background technique

Similar bending/swing steering devices are widely used in wheel loaders or in road rollers. In general, the knuckle/pivot steering has different advantages. A simple design of the axle with a knuckle/pivot steering is possible since the wheels themselves do not have to be steered. In this way, the chassis can be realized very compactly, since the steering angle of the wheels relative to the vehicle is not taken into account. A further advantage of a vehicle with a knuckle/pivot steering is that the trailing wheels follow exactly the path of the wheels driving out ahead, so that energy savings are possible in difficult terrain due to the low driving resistance.

A disadvantage of the conventional knuckle/pivot steering (as is known, for example, from DE 10158912 A1) is that it has a relatively complex construction, which is expensive to produce. Furthermore, the known knuckle/pivot steering requires a lot of space.

Contents of the invention

The object of the present invention is to provide an improved bending/swivel steering device and a construction machine with an improved bending/swivel steering device, whereby the disadvantages of hitherto known bending/swivel steering devices can be eliminated.

The solution according to the invention consists in the bending/pivot steering according to the invention and in the construction machine according to the invention.

The bending/swing steering device according to the invention has a first fastening element and a second fastening element, which are suitable for fastening on the front and rear vehicles, so that the front and rear vehicles can be bent/swinged together Steering gear connection. The bending/swivel steering device according to the invention is characterized in that the two fastening elements are connected via a ball joint and a swivel/sliding bearing movable tangentially to the ball joint, and the swivel/sliding bearing is accommodated with play on the sliding in the slot. The bending/pivot steering device according to the invention has the advantage that only two bearings, ball joint and swivel bearing, have to be provided. The steering device can thus be designed simply and inexpensively. Advantageously, the knuckle/pivot steering comprises only ball joints and swivel bearings and no other bearings for connecting the fastening elements. The ball joint achieves a defined base point through which both the steering axis and the pivot axis run. The pitching movement of the front vehicle relative to the rear vehicle has a fixed reference axis via the ball joint, which extends through the ball joint. In order to reduce the degree of freedom of the ball joint, a swivel bearing is additionally provided in the bending/pivot steering according to the invention, which is rotatable about the axis and is also displaceable tangentially to the ball joint. Displaceable here means that the rotary bearing can be displaced tangentially or substantially tangentially to the ball joint by means of a rolling or sliding movement. The pendulous pendulum steer according to the invention has a simple construction, is reliable and can be produced inexpensively. According to the invention, the swivel bearing is accommodated with play in a link oriented tangentially to the ball joint. The link, interacting with the swivel bearing, permits a pivoting movement of the front vehicle relative to the rear vehicle over the length of the link and blocks further pivoting movements. Excessive swivel angles are avoided in this way. According to the invention, a defined play is provided between the rotary bearing/sliding bearing and the link or one of the fastening elements. This ensures a reliable and wear-free guidance of the rotary bearing/sliding bearing in the link.

In a preferred embodiment of the invention during travel, play is provided permanently between the rotary bearing/sliding bearing and one of the two fastening elements. An articulated machine has a front car and a rear car, which each have a center of gravity. The corresponding center of gravity is preferably selected such that a play is permanently maintained between the rotary bearing/sliding bearing and one of the two fixed elements during operation and at rest of the construction machine. This achieves that one of the rotary bearing/sliding bearing and the link or the fastening element is not damaged by alternating mechanical loads due to the changing position of the gap. Therefore, the reliability of the bending swing steering device is improved. Considering that the swivel bearing rests securely on one side permanently against one of the fastening elements, the pitch of the construction machine is reduced almost completely. The center of gravity of the front vehicle should preferably be chosen such that it (viewed in the horizontal direction) lies between the support line/support surface of the front axle and the knuckle pivot steering according to the invention. Accordingly, the center of gravity of the rear vehicle should preferably be chosen such that it (viewed in the horizontal direction) lies between the support line/support surface of the rear axle and the pendulous pivot steering according to the invention. It is thus achieved that the gap is permanently provided on one side and its position does not change. In construction machines such as vibratory rollers with two tires, the center of gravity is essentially determined by the construction of the vibratory roller, so that it can be structurally adjusted during operation as well as when stationary (as long as the vibratory roller is not lifted). The position of a gap between one of the elements or the position of a contact. On the other hand, in construction machines whose center of gravity changes during operation, for example in wheel loaders with blades, there are constant changes in the play or contact surface in the bending pivot joint, the load of these blades and The position determines the instantaneous center of gravity position of the vehicle in front, which has a negative effect on the swivel joint. Such unfavorable alternating loads do not occur according to the invention.

In a preferred embodiment it is also possible for the swivel bearing to be movably arranged directly on one of the fastening elements, so that it can slide or roll there. The arrangement of the chute can be dispensed with. This simplifies the design of the knuckle pivot steering. The swivel bearing is here advantageously arranged above the ball joint, since it can thus be ensured that pressure is transmitted via the swivel bearing such that the swivel bearing is pressed against the fastening element. Preferably, however, a safety device such as a safety link is provided which limits the freedom of movement of the swivel bearing in special operating states. During normal operation, however, no or only insignificant forces are transmitted via the safety link, since the safety pin arranged in the safety link is received without contact during normal operation.

The rotary bearing/sliding bearing is preferably rotatable about a substantially vertical axis. It is thus realized that the front vehicle phase can be turned or bent relative to the rear vehicle. The substantially vertical axis is advantageously the vertical axis of a vehicle which is arranged to receive the kink/swing steering arrangement of the invention.

Generally in this application the usual coordinate system for the vehicle is used for the kink/swing steering so that the longitudinal, transverse and vertical axes of the kink/swing steering correspond to the respective axes of the vehicle with the The kink/swing steering in it.

Preferably, the link is aligned transversely and horizontally to the longitudinal axis of the knuckle/pivot steering. The link is therefore preferably oriented in the direction of the transverse axis of the vehicle which is intended to accommodate the kink/pivot steering. The slightly curved shape of the link is advantageous here, since the relative movement of the swivel bearing takes place on a curved path in the link due to the fixed base point in the ball joint. Preferably, therefore, the link has a curved shape or a shape with a knuckle, which guides partly around the ball joint in the circumferential direction. The chute is oriented substantially in the direction of the transverse axis to allow rotational movement about the longitudinal axis. This offers the advantage that the pivoting movement up to the abutment of the link can be free. Due to this arrangement of the links, the axis of the swivel bearing also does not have to run exactly through the center of the ball joint, because the bending movement of the front vehicle relative to the rear vehicle, ie the bending movement of the first fastening element relative to the second fastening element It can also take place by a combination of a rotary movement of the rotary bearing and a tangential movement of the rotary bearing in the link.

Preferably the runner comprises a frame arranged on the first fastening element. The frame has the advantage that it provides a certain spring action, since the forces acting through the swivel bearing have to be guided by the frame into the first fastening element when the swivel bearing rests on the frame, so that the stiffness of the frame is determined by the spring action. It should be noted that the frame and the swivel bearing are preferably arranged in such a way that the swivel bearing rests against the frame in the normal rest position of the knuckle/pivot steering and in this way achieves a spring action.

The frame is advantageously U-shaped, so that the frame together with the first fastening element forms a link. It is only necessary that the U-shaped frame is fastened to the preferably plate-shaped first fastening element. A link is formed in a simple manner between the fastening element and the U-shaped frame. Advantageously the swivel bearing comprises an outer bearing ring guided in a sliding groove.

In a preferred embodiment of the invention, the swivel bearing is accommodated with play in the link. The play offers the advantage that the swivel bearing can be easily accommodated in the link. Furthermore, the play offers the advantage that frictional losses are low when the swivel bearing moves in the link groove. In swivel bearings with an outer bearing ring, therefore, the outer diameter of the outer bearing ring is smaller than the width of the link groove, so that the outer bearing ring can roll in the link groove. This is achieved in such a way that sliding of the bearing ring in the link groove is not necessary during the pivoting movement, but rather allows rolling of the protective material. The outer diameter of the outer bearing ring is preferably only slightly smaller than the width of the link groove, ie for example the outer diameter preferably has at least 90%, preferably at least 95% or 97% of the width of the link groove. Overall the clearance is preferably between 0.1% and 20%, preferably between 1% and 10%, of the dimension of the chute. In this way, excessive play is avoided, which could lead to damage in special load situations of the knuckle/pivot steering, for example when the vehicle hits an obstacle. In addition, if the axis of the swivel bearing does not extend through the center of the ball joint, the outer bearing ring rolls in the link groove during the steering movement, so that the vehicle can be bent.

Advantageously, the swivel bearing comprises an inner bearing ring which is rigidly connected to the second fastening element via the pivot plate. Thus, in combination with the above-described configuration of the link on the first fastening element, a simple possibility for determining the degree of freedom of movement around the ball joint is obtained, while for the pitching movement of the front vehicle relative to the rear vehicle, the link The frame implements a certain spring characteristic. The swivel bearing is preferably designed as a deep-groove ball bearing, wherein other bearing forms with multiple raceways or rollers are also possible depending on the expected load.

In a preferred embodiment of the knuckle/pivot steering device, the swivel bearing includes a bearing block. The bearing block is preferably provided with at least one sliding surface which is suitable for slipping or sliding on a surface, for example the surface of one of the fastening elements. The support block can be arranged at the position of the bearing ring. A bearing pin is advantageously arranged in the bearing block. The bearing pin is connected to one of the two fixing elements and the bearing block is arranged such that it can slide, ie move, relative to the other fixing element. It is thus possible to form a displaceable swivel bearing and this design offers the advantage that the swivel bearing is very robust. Preferably, the bearing block consists of a sliding or damping material such as PTFE (polytetrafluoroethylene) or another wear-resistant material. The bearing block can be guided in the link in order to achieve a high degree of stability, and play in the link can be dispensed with when using the support block. An arrangement with gaps offers the advantage that frictional losses can be reduced. The bearing pin is rotatably accommodated in the bearing block or is rotatably connected to a component such as a pivot plate.

A further embodiment of the invention provides that the bearing block is arranged in a safety link, which is arranged on the fastening element, relative to which the rotary bearing can be displaced. In this way, it is also possible without a link, that the bending/pivot deflection remains intact even in special operating positions, for example when lifting a tandem roller. The safety link is preferably formed in such a way that the bearing pin is accommodated in the safety link with play. In this embodiment, the bearing pin is also referred to as a safety pin, since it is accommodated in the bearing block and the safety link and is fastened to the pivot plate. Other embodiments have separate support pins and safety pins, which are only rigidly connected to each other. Preferably, no contact of the pin with the safety link occurs in normal operating states. In addition, the safety link offers the advantage that a maximum swivel angle is determined, ie for limiting the swivel travel.

Advantageously, the joint comprises an at least partially spherical joint inner body, which is rigidly connected to the first fastening element. An only partially spherical shape of the joint inner body is generally sufficient for all movements of the ball joint that occur during operation. Only a limited movement possibility of the ball joint is necessary in the bending direction, ie in the steering direction, since the maximum possible bending deflection angle of the front vehicle relative to the rear vehicle is in any case limited by the shape of the individual components. This enables a compact and stable design of the ball joint.

Advantageously, the joint comprises a bearing shell which is rigidly connected to the second fastening element. The bearing shell surrounds the joint from the outside and, in combination with the joint inner body, enables the movement possibilities of the ball joint about all axes of rotation.

The bearing shell is preferably connected to the second fastening element by means of a deflection plate, so that a bending movement of the bending/pivot steering device can be produced by a rotation of the deflection plate relative to the first fastening element about a substantially vertical axis. The substantially vertical axis in turn corresponds to the vertical axis of the vehicle which is intended to accommodate the kink/pivot steering. The deflection plate offers the advantage that it allows an extremely rigid connection of the bearing shell to the second fastening element. Thus, the pitching movement of the knuckle/pivot steering device can be reliably performed by the steering of the steering plate.

In order to carry out the steering movement of the knuckle/pivot steering, the steering plate is preferably connected to the first fastening element via a substantially horizontally acting steering drive. The expression “substantially horizontal” here refers to the plane formed by the longitudinal axis and the transverse axis of the vehicle which is intended to receive the kink/pivot steering. An oil pressure cylinder is preferably used as the steering drive, which is articulated on the one hand to the first fastening element and on the other hand to the steering plate or the second fastening element. Simple and reliable measures allow efficient steering in this way.

Advantageously, the swivel bearing and the ball joint of the knuckle/pivot steering are arranged one above the other in the vertical direction in the rest position. In this rest position is meant the position of the kink/swing steering without a steering angle and without kink of the kink/swing steering. The plane in which the swivel bearing and the ball joint are arranged one above the other in the vertical direction is preferably the plane formed by the vertical axis and the longitudinal axis. The link is advantageously designed in such a way that, depending on the position of the swivel bearing, an inherently stable straight-line travel is achieved. This can be achieved in that the steering movement leads to an energetically poor state, so that the kink/pivot steering automatically returns to straight-ahead driving. The swivel bearing and the ball joint are therefore preferably arranged such that the axis of rotation of the swivel bearing does not run through the center or base point of the ball joint. It can be achieved in this way that the steering movement necessarily leads to a pivoting movement and thus to an energetically poor state, so that the steering automatically returns to straight-ahead driving.

Advantageously the first fixing element comprises a first flange plate on which the slide groove is arranged or on which the bearing block slides, or the second fixing element comprises a second flange plate on which The second flange plate is rigidly connected with the swing plate or the turning plate. In this way, a particularly stable construction of the knuckle/pivot steering is achieved. The first and second flange plates are provided for connection with the front vehicle or the rear vehicle.

A construction machine, preferably a tandem roller mechanism, is another independent subject matter of the invention.

Description of drawings

A preferred exemplary embodiment of the invention is described below with the aid of the drawings. in:

Figure 1 shows a schematic cross-sectional view of a part of a bending/swing steering device according to the present invention;

FIG. 2 shows a complete schematic view of the bending/swing steering device according to the invention, shown in section in FIG. 1 and described as a partial view;

Figure 3 shows a schematic diagram of another bending/swing steering device according to the present invention;

Fig. 4 shows another schematic diagram of the bending/swing steering device of Fig. 3;

Figure 5 shows a schematic diagram of another variant of the bending/swing steering device of the present invention;

Figure 6 shows a schematic view of a construction machine according to the invention, including a bending/swing steering device according to the invention;

FIG. 7 shows an enlarged view of the bend/swing steering device of FIG. 6 .

Detailed ways

FIG. 1 shows a bending/pivot steering device 1 according to the invention in vertical section. The bending/swing steering device 1 comprises a first fastening element 2 and a second fastening element 3 . The first fastening element 2 and the second fastening element 3 are designed as flange plates which are provided for fastening respectively to the front and rear carriages of the construction machine with the bending/pivot steering device 1 .

The sectional view of FIG. 1 extends through the bending/swing steering device 1 in the plane of the longitudinal axis B and the vertical axis A of the bending/swivel steering device 1 . It is assumed that a coordinate system is fixedly connected to the first fastening device 2 and whose axes A, B and C correspond to the general axes of the vehicle, namely the vertical, longitudinal and transverse axes. The vertical axis is denoted below by A (see FIG. 1 ), the longitudinal axis by B and the horizontal axis by C.

In a preferred embodiment the bending/swing steering device 1 comprises a ball joint and a swivel bearing. The swivel bearing has an inner bearing ring 5 and an outer bearing ring 6 . The balls of the rotary bearing are arranged between the bearing rings 5 and 6 . The inner bearing ring 5 is connected to the pivot plate 8 via a bearing receptacle 7 . The pivot plate 8 is in turn rigidly connected to the flange plate of the second fastening element 3 . The inner bearing ring 5 is welded to the bearing receptacle 7 , which in turn is welded to the pivot plate 8 . The pivot plate is in turn welded to the second fastening element 3 , so that a rigid connection is formed between the inner bearing ring 5 and the second fastening element 3 . The fastening of the inner bearing ring 5 to the bearing receptacle 7 and the bearing receptacle 7 to the pivot plate 8 can optionally be achieved by means of a press fit.

On the side of the first fastening element 2 , the swivel bearing passes through a U-shaped frame 10 which is welded to the flange plate of the first fastening element 2 . The U-shaped frame 10 together with the flange plate of the first fastening element 2 thus forms a link for the outer bearing ring 6 of the swivel bearing. The U-shaped frame is not exactly straight, but has slight bends or bends, so that the runner formed thereby constitutes an approximate partial circular trajectory along the circumference around the ball joint (explained later) described above in FIG. 1 . The inner width of the sliding channel formed by the U-shaped frame 10 and the first fixing element 2 is approximately 2% larger than the diameter of the outer bearing ring 6, so that the outer bearing ring 6 can either rest on the U-shaped frame 10 or can be fixed in operation. The element 2 rolls on, depending on whether the swivel bearing is pressed against the outer bearing ring 6 against the U-shaped frame 10 or against the first fixed element 2 . The function of the swivel bearing and the link will be explained later in relation to the rest of the knuckle/pivot steering.

Furthermore, the bending/pivot steering device 1 has a ball joint which is connected on the one hand to the first fastening element 2 via a receiving piece 15 and on the other hand to the second fastening element 3 via a deflection plate 16 . The deflection plate 16 is welded to the flange plate of the second fastening element 3 and also serves as a receptacle for the bearing half shell 17 . To fix the bearing half shell 17 and to protect the ball joint, the bearing half shell 17 and the ball joint are embedded at least from above in a housing 18 which is fixed in the deflection plate 16 by means of pins. The cylindrical head of the receiving block 15 protrudes into the housing 18 . A joint inner body 19 , which has a cylindrical bore on the inside and whose outer side forms part of the surface of the ball joint, rests on the receiving piece 15 . The joint inner body 19 is fixed axially on the receiving block 15 by means of a clamping ring 20 . The described structure forms a ball joint between the first fastening element 2 and the second fastening element 3 .

During operation, the ball joint with the bearing shell 17 and the joint inner body 19 permits a rotation of the deflection plate 16 and thus the second fastening element 3 relative to the first fastening element 2 in all directions of rotation, starting from the rest position depicted in FIG. 1 . sports. The limited movability of the ball joint due to the flattened ball of the joint inner body 19 is sufficient, since the ball joint only has to perform limited movements about different axes during operation in the construction machine. It is to be noted that the receiving block 15 is connected to the first fixing element 2 by pins (not depicted in FIG. 1 ).

In order to initiate a steering movement, ie a bending movement of the bending/pivoting steering device 1 about a vertical axis A which passes vertically through the ball joint from bottom to top, the steering plate 16 is connected to a hydraulic steering drive 21 . Only the two end flanges of the steering drive 21 are depicted in FIG. 1 , which connect the steering drive 21 to the steering plate 16 via pins 22 and ball joint bodies 23 . When the steering drive 21 is actuated, the deflection plate 16 is rotated about the vertical axis A, so that the second fastening element 3 is rotated about the vertical axis A relative to the first fastening element 2 . For the unproblematic kinematics of the bending/swing steering device 1, the driving point of the steering drive 21 is at the same height as the center of the joint, so that when the second fastening element 3 pivots around the longitudinal axis B, the steering Plate 16 can also rotate about joint body 23 . For this purpose, it is advantageous if the point of action of the steering drive 21 on the steering plate 16 lies in the plane of the transverse axis C and the longitudinal axis B of the ball joint.

The function of the bending/pivot steering device 1 is briefly described below as described in FIG. 1 . The steering movement can be carried out by the knuckle/pivot steering 1 by actuating the steering drive 21 . Due to the ball joint fixed on the first fixing element 2, all movements of the second fixing element 3 relative to the first fixing element 2 are rotational movements about the joint center of the ball joint. During the steering movement, the outer bearing ring 6 of the swivel bearing is forced to make a rotational movement around the vertical axis A. Since the point of rotation of the swivel bearing is not on the vertical axis A, the outer bearing ring 6 rolls on the U-shaped frame 10 , so that an oscillating movement, ie a swivel movement about the longitudinal axis B, additionally takes place. This behavior stabilizes straight-line travel when driving, since the center position of the swivel bearing is energetically most favorable due to the pivoting movement, so that the construction machine automatically returns to straight-line travel after a steering movement on a straight basis. The second fastening element can be pivoted about the longitudinal axis B in the event of an uneven driving surface which would necessitate pivoting of the vehicle in front relative to the vehicle behind. In addition, the bearing ring 6 rolls on the U-shaped frame 10 again.

In the normal operating state, the swivel bearing outer bearing ring 6 bears against the U-shaped frame 10 and not against the first fastening element 2 . The reason for this is that, in the usual construction of a construction machine, a moment with a compressive force on the top and a tensile force on the bottom must be transmitted between the first fastening element 2 and the second fastening element 3 in the bending/pivot steering device 1 . Tensile forces must therefore be transmitted via the pivot plate 8 so that the outer bearing ring 6 bears against the U-shaped frame 10 . In contrast, the pressure acting on the ball joint is transmitted via the deflection plate 16 . Only in special operating states, for example when driving over an obstacle or when the construction machine is raised by means of a crane, can the load in the bending/pivot steering device 1 be changed, so that the outer bearing ring 6 then rests against the first fastening element 2 on. For the pivoting movement, it makes no difference whether the outer bearing ring 6 rests on the U-shaped frame 10 or on the first fastening element 2 , since it can roll on both components respectively. A pivoting movement is therefore also possible in the above-mentioned special operating states. Since the pivoting movement about the longitudinal axis B is carried out and the suspension point of the steering drive 21 on the steering plate 16 is likewise located on the longitudinal axis B, the pivoting movement does not cause a load on the steering drive 21 .

The bending/pivot steering device 1 of FIG. 1 is again fully described in FIG. 2 , wherein the same reference numerals designate the same parts as in FIG. 1 . In contrast to FIG. 1 , however, the steering drive 21 is completely depicted in FIG. 2 . The steering drive 21 is supported on the connecting flange 25 on the first fastening element 2 . Also shown in FIG. 2 is a pin 28 , via which pin receiving block 15 is fastened to first fastening element 2 . In the installed state, the first fastening device 2 serves as a first flange plate to which the rear vehicle is fastened. The front carriage of the construction machine is fastened to a second fastening element 3 serving as a second flange plate.

Due to its construction, the described preferred embodiment of the bending/swing steering device 1 according to the invention is especially suitable for tandem rollers, which have large rollers (wheel tires) on the front and rear carriages respectively. )s frame. The bending/swing steering device 1 according to the invention has a simple construction and allows stable straight-line driving and also a certain driving comfort, because the frame 10 acts as a spring when a load is generated about the transverse axis C, and the swivel bearing supports on that frame. Due to the favorable position of the center of gravity, tandem rollers are particularly well suited for the bending/pivoting steering device 1 according to the invention, since relatively high loads almost always act in one direction and the presence of play does not become disadvantageous.

Further exemplary embodiments of the bending/pivot steering device according to the invention are described below. The same reference numerals are used here for identical or similar parts as in FIGS. 1 and 2 . Not all visible parts have been marked with corresponding reference symbols in the individual figures. This is for overview only.

FIG. 3 schematically depicts a knuckle/pivot steering device 1 , wherein the swivel bearing has a different embodiment than in the exemplary embodiment of FIGS. 1 and 2 . The remaining components correspond to the embodiments described above and are not described again here. It is to be noted that the kink/swing steering device 1 of FIG. 3 operates substantially in the same manner as the kink/swing steering device of FIGS. 1 and 2 .

In the swivel bearing of the embodiment in FIG. 3 , a bearing block 31 is provided, which is mounted rotatably on a bearing pin 32 . The bearing block 31 is accommodated with a 5% play in the slideway with the frame 10 and can slide in the slideway. The bearing block 31 consists of a plastic material which exhibits low wear when sliding on the first fastening element 2 . The support pin is fixed on the swing plate 8 . The embodiment depicted in FIG. 3 is particularly inexpensive to manufacture and simple to install. In addition, a certain damping can also be achieved by means of the bearing block 31 in order to improve driving comfort.

FIG. 4 shows the embodiment of FIG. 3 in another perspective in the form of a schematic sketch. It is clearly visible in FIG. 4 how the bearing blocks 31 are accommodated in the slideway with the frame 10 . A certain damping is also achieved by the support blocks 31 when the support blocks 31 abut against the side arms of the frame 10 during the pivoting movement of the bending/swing steering device 1 .

Another knuckle/pivot steering device 1 is schematically depicted in FIG. 5 . The bending/pivot steering device 1 of FIG. 5 differs from the previously described embodiments primarily in that the swivel bearing is arranged not below the ball joint but above it. This achieves that, during normal operation, tensile forces are transmitted via the ball joint and compressive forces are transmitted via the swivel bearing. Also discard the chute. Instead, the bearing block 31 slides freely on the first fixing element 2 . In order to ensure that the bending/pivot steering device 1 of FIG. 5 remains intact even in special operating states, the bearing pin 32 is additionally secured with a fastening plate 33 . The fastening plate 33 includes safety slots 34 in which the bearing pins 32 are guided. A defined movement clearance space for the bending/pivot steering device 1 can be achieved by means of the safety link 34 , for example to avoid excessive pivoting movements.

The present invention is not limited to the above-described embodiments, but rather the scope of the present invention is defined by the claims.

FIG. 6 shows a construction machine according to the invention, including a pendulum and pivot steering device according to the invention. This is a tandem roller. A tandem roller has a front carriage with a front tire Bv, which lies on the ground along a front support line. The vertical axis ASv of the center of gravity Sv of the front vehicle (seen in the horizontal direction) is at a distance Xv from the vertical axis Sv of the front support line Pv. Due to the arrangement of the center of gravity Sv of the vehicle in front, a front moment Mv in the direction of the indicated arrow occurs about the front support line Pv.

The tandem roller also has a rear carriage with a rear tire Bh which rests on the ground along a rear support line Ph. The vertical axis ASh of the center of gravity of the rear vehicle (seen in the horizontal direction) is at a distance Xh from the vertical axis Ah of the rear support line Ph. Due to the arrangement of the center of gravity Sh of the trailing vehicle, a rear moment Mh in the direction of the arrow shown is generated with respect to the rear support line Ph.

The positions of the centers of gravity Sv and Sh remain almost unchanged when the tandem roller is running and when it is stationary. The front vehicle and the rear vehicle are connected to each other by means of the bending and pivoting device 1 according to the invention.

FIG. 7 shows an enlarged view of the knuckle swing steerer from FIG. 6 . Figure 7 is almost identical to Figure 1. Only the gap Sp is depicted more clearly in FIG. 7 . Due to the arrangement shown in FIG. 6 of the centers of gravity Sv and Sh, a gap Sp is permanently provided between the first fastening element 2 and the outer bearing ring 6 of the swivel bearing. In other words, a contact Kt is formed permanently on the other side between the outer bearing ring 6 and the U-shaped frame 10 . According to the invention, there is no change in the position of the gap Sp or the contact Kt from the side shown in FIG. Change. Alternating mechanical loading of the rotary bearing, the U-shaped frame 10 and the first fastening element is thus avoided in order to increase the service life of the components.

Claims (15)

1. bend pendulum steering gear (1); Be used to have the construction machinery and equipment of front truck and back car; This bending pendulum steering gear comprises first retaining element (2) and second retaining element (3); Be used for fixing on the front truck of construction machinery and equipment and back car, it is characterized in that: first retaining element (2) and second retaining element (3) are connected to each other through the ball-joint and the swivel bearing/plain bearing that can on the tangential of ball-joint, move, and swivel bearing/plain bearing has the gap and is contained in the chute (Sp).

2. by the described bending pendulum steering gear of claim 1 (1), it is characterized in that: gap (Sp) is arranged between one of swivel bearing/plain bearing and two retaining elements (2,3) enduringly.

3. by claim 1 or 2 described bending pendulum steering gears (1), it is characterized in that: swivel bearing can be around the axis rotation of perpendicular.

4. by claim 1 or 2 described bending pendulum steering gears (1), it is characterized in that: swivel bearing leads in being tangential to the directed chute of ball-joint, and this chute is directed along the horizontal and on even keel of the longitudinal axis (B) of bending pendulum steering gear (1).

5. by claim 1 or 2 described bending pendulum steering gears (1), it is characterized in that: swivel bearing comprises outer collar bearing/slip slit, leads in chute or slide from the teeth outwards in this outer collar bearing/slip slit.

6. by claim 1 or 2 described bending pendulum steering gears (1), it is characterized in that: swivel bearing comprises anchor plate.

7. by the described bending pendulum steering gear of claim 6 (1), it is characterized in that: anchor plate is gone up at one of retaining element (2,3) and is slided.

8. by claim 1 or 2 described bending pendulum steering gears (1), it is characterized in that: ball-joint comprises part ball-shaped movable joint endosome (19) at least, and this movable joint endosome and first retaining element (2) are rigidly connected.

9. by claim 1 or 2 described bending pendulum steering gears (1), it is characterized in that: ball-joint comprises supporting shell (17), and this supporting shell and second retaining element (3) are rigidly connected.

10. by the described bending pendulum steering gear of claim 9 (1); It is characterized in that: supporting shell (17) is connected with second retaining element (3) by means of deflecting plate (16), makes to bend motion with respect to first retaining element (2) around the energy of rotation of the axis (A) of perpendicular through deflecting plate (16).

11. by the described bending pendulum steering gear of claim 10 (1), it is characterized in that: deflecting plate (16) is connected with first retaining element (2) through the steer-drive (21) of substantial horizontal effect.

12. by claim 1 or 2 described bending pendulum steering gears (1), it is characterized in that: swivel bearing/plain bearing and ball-joint self are provided with in dead position in vertical direction stackedly.

13., it is characterized in that by claim 1 or 2 described bending pendulum steering gears (1):

First retaining element (2) comprises first flanged plate, slides on this first flanged plate at the anchor plate that chute or swivel bearing are set on first this flanged plate; And/or

Second retaining element (3) comprises second flanged plate, and this second flanged plate and oscillating deck (8) and/or deflecting plate (16) are rigidly connected.

14. construction machinery and equipment comprises front truck and back car, said front truck and back car are by means of being connected to each other by each described bending pendulum steering gear (1) of claim 1 to 13.

15. by the described construction machinery and equipment of claim 14, it is characterized in that: said construction machinery and equipment is a tandem roller.

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