Device for detecting a turning angle and heavy duty transport vehicle

0001The invention relates to a steering loss for detecting a steering angle between a leading first vehicle part and a trailing second vehicle part of a vehicle, according to the preamble of claim 1. The invention further relates to a heavy-duty transport vehicle according to the preamble of claim 12 with such a steering loss.

0002Such steering decrease for a heavy-duty transport vehicle from the <patcit id="pcit0001" dnum="DE840650B"><text>DE 840 650 B</text></patcit> known. In this document, a tiller steering for heavy vehicles with limited steering angle is described. The tiller arm is connected to a cam disc, which is rotated by the turning movement of the drawbar about an axis. This cam has in the region of allowable steering angle an approximately parabolic or hyperbolic curve. A pivoting of the cam is therefore in each case via a roller to a master cylinder which comprises in each case a cylinder tube and a piston rod is transmitted. The master cylinder is connected to the control cylinders so that displaced by the movement of the pistons of the envisaged for each wheel control piston and thus beyond the actual control rods, the wheel is wrapped.

0003A steering loss and a heavy-duty transport vehicle are also made of <patcit id="pcit0002" dnum="DE102006018388B4"><text>DE 10 2006 018 388 B4</text></patcit> known. This heavy-duty transport vehicle, the leading first vehicle part consists of a tractor, while the trailing second vehicle part consists of a semi-trailer. The steering loss or decrease steering comprises two master cylinders with which the steering movements and the turning angle of the tractor to be taken in relation to the trailer. The master cylinder there are arranged between a turntable of the tractor and the trailer, with their cylinder tubes pivotally mounted in an elevated area of ​​the semitrailer and their piston rods are hinged to the turntable.

0004A similar steering decrease or a heavy-duty transport vehicle having such a steering loss is from the <patcit id="pcit0003" dnum="DE202012010545U1"><text>DE 20 2012 010 545 U1</text></patcit> known the applicant. In this heavy-duty transport vehicle, there is a trailing second vehicle part consists of a multi-axle trailer having a steering axle and a plurality of rigid axles, while the leading first vehicle part consists of a supported on the trailer and over a gooseneck to a tractor of the transport vehicle telescopic carrier. At the rear end of the telescopic support a turntable is provided which is rigidly connected to the telescopic carrier and supported to a vehicle vertical axis mounted on the trailer. The steering device of the heavy-duty transport vehicle is designed as a fifth-wheel steering and includes serving as a master cylinder of the steering decrease hydraulic cylinder caused by the tractor and the support rotation of the turntable decreases during cornering with respect to trailer, and two slave cylinder axle steering of the steering axle of the trailer which are hydraulically connected to the master cylinder and provide a positive steering of the steering axle of the trailer, depending on the angle of rotation of the turntable and thus changes a steering angle of the telescopic carrier relative to the trailer.

0005In this type steering loss, in which the cylinder barrel of the master cylinder at the leading part of the vehicle and the piston rod is hinged to a relative to the leading vehicle part rotatable turntable of the trailing vehicle part, or vice versa, the relationship between the turning angle of the leading vehicle part and the steering angle of the trailing vehicle part , which is caused by the action of the slave cylinder on the steering axle, not be changed without additional hydraulic oil is fed into a hydraulic circuit between the master cylinder and the slave cylinder or discharged from the hydraulic circuit, which is relatively expensive. In addition, the maximum rotation angle between the leading and the trailing vehicle part by abutments must be limited so that the two master cylinder does not collide with each other in this type steering loss. In addition, the pivotable coupling of the cylinder tube and the piston rod of each master cylinder makes a complicated structure and a complicated steering kinematics required.

0006Proceeding from this, the invention aims to improve a steering loss and a heavy-duty transport vehicle of the type mentioned in that firstly a simple mechanical way a desired relationship between the turning angle of the leading first vehicle part and the steering angle of the trailing second vehicle part can be produced to impart, for example, the steering a desired aggressiveness that particular second, can be dispensed with a limitation of the steering angle of the trailing second vehicle part, and that particular third detecting the turning angle of the leading first vehicle part with respect to the trailing second vehicle part by means of the master cylinder can be simplified.

0007The object is achieved by a steering decrease with the features of claim 1 and a heavy-duty transport vehicle with the features of claim 11. Advantageous further developments are evident from the dependent claims.

0008The invention is based on the idea that in a simple mechanical way a desired relationship between the turning angle of the leading vehicle part and the steering angle of the trailing vehicle part can be produced by a suitable shaping of the outer periphery of the cam plate, the one itself by replacing the cam without additional supply of hydraulic oil can change in the hydraulic circuit. In addition, the cylinder tubes of the master cylinder can be rigidly connected to one of the two vehicle parts, covering not only the design of the master cylinder of the steering decrease more compact and easier, but also stops for limiting the angle of rotation between the two parts of the vehicle can be dispensed with, since a collision the master cylinder is no longer possible. The steering decrease invention is characterized in that when the travel of the piston rods of both master cylinder is the same, that is, when the piston rod of a master cylinder is moved exactly as far as the piston rod of the other master cylinder is extended, the lifting of the free ends of the piston rods can be from the outer periphery of the cam plate also prevented by the free ends of the piston rods of the master cylinder are connected to each other by at least one strap, which ensures a constant distance between the free ends of the two piston rods.

0009A very stable guidance of the free ends of the piston rods can be achieved according to one advantageous refinement of the invention, when they are connected to one another by two straps, of which one above and one is arranged below the cam. The brackets are advantageously formed so that they extend from both sides of the axis of rotation of the swivel joint at a lateral distance to the rotary joint over.

0010The relative movement between the cam and the piston rods of the two master cylinder is achieved by the fact that the cam disc is fixedly connected to one of the two vehicle components, while the master cylinder are rigidly connected to the other of the two vehicle parts.

0011The inventive heavy-duty transport vehicle comprises in addition to the steering decrease two slave cylinders which are connected hydraulically with a master cylinder and steer the lagging second vehicle part, depending on the areas covered by the master cylinders changes the steering angle.

0012The inventive measures also allow easy adjustment of the steering decrease in a varying number of steering axles at the trailing vehicle part by having larger diameters used in an increase in the number of steering axles either master cylinder or another cam and two more master cylinder are provided on the cam and the master cylinders to carry the larger oil demand calculation.

0013A preferred development of the invention provides that the free ends of the piston rods are each equipped with at least one on the outer periphery of the cam rolling roller in order to facilitate the movement of the free ends of the piston rods along the outer periphery of the cam.

0014In order to prevent an unintentional lifting of the free ends of the piston rods from the outer periphery of the cam disk, the piston rods of the master cylinder are preferably pressed under hydraulic pressure against the cam, so as to be corrected to the outer periphery of the cam plate when the steering of the distance between this and the cylinder tube of the respective master cylinder increases. If the distance of the outer periphery of the cam plate decreases from the cylinder tube of a master cylinder when driving, on the other hand, the piston rod of the cam plate is pressed against the hydraulic pressure in the cylinder barrel.

0015The leading first vehicle part and the trailing second vehicle part are rotatable to each other about a to the ground vertical axis of a rotating joint between the first and the second vehicle part relative, the axis of rotation in accordance with a further preferred embodiment of the invention by the cam extending therethrough. Establishing a desired, preferably non-proportional relation between the steering or turning characteristics of the trailing second vehicle part and the steering or turning characteristics of the leading first vehicle part, the curve geometry of the outer circumference of the cam disc can along those portions where the free ends of the piston rods or along rollers move, be selected accordingly. In this case, the relationship between the turning angle of the leading first vehicle part and the associated turning angle of the trailing second vehicle part to be controlled by along one of the turning angle of the leading first vehicle part corresponding portion of the outer periphery of the cam disc, the distance of the outer periphery of the cam plate from the rotational axis in the desired way is changed. Secondly, the aggressiveness of the steering can be controlled by one along the turning angle of the leading first vehicle part corresponding portion of the outer periphery of the cam disc whose slope, that is the first derivative of the distance is changed in a desired manner. In this way, the steering behavior of the trailing second vehicle part can be influenced in an ideal way.

0016In order to achieve that the steering movements of the steering axle of the trailing second vehicle part when turning to the left and when turning to the right are identical, the outer periphery of the cam suitably mirror symmetry to a vertical center plane of the one vehicle part by the rotational axis of the rotary joint, while the master cylinder expedient are mirror-symmetrical to a vertical center plane of the other vehicle part by the rotational axis of the rotary joint.

0017This causes the piston rod of a master cylinder retracted at each change of the steering angle of the leading first vehicle part by a defined amount, while the piston rod of the other master cylinder is extended by the same amount. In this way, the steering of the heavy-duty transport vehicle can be simplified, is connected by according to another preferred embodiment of the invention each of the two master cylinder hydraulic with one of the two slave cylinders and hydraulically separated from the other master cylinder and slave cylinder. Any minor difference amounts during retraction and extension of the piston rods of the two master cylinder can be compensated by the pressurized hydraulic fluid, so that the entry or exit way of the slave cylinder is always the same length.

0018Advantageously, the two master cylinders each having a vertical axis of rotation of the rotary joint central longitudinal axis, wherein they are expediently arranged on opposite sides of the rotation axis so that their longitudinal central axes are aligned. In this way, a maximum steering angle to be reached without the free ends of the two piston rods of the master cylinder must move over the same portion of the outer periphery of the cam.

0019To avoid jerky steering movements of the trailing second vehicle part provides an expedient development of the invention, that at least in the areas of the outer circumference of the cam disk on which to move the free ends of the piston rods along while driving, the distance between the outer periphery of the cam and the rotation axis of the rotary joint without steps or discontinuities gradually changed.

0020A further advantageous development of the invention provides that the cam surrounds the pivot, about an advantageous supporting a leading from the first vehicle portion and the trailing second vehicle part on each other Fahrzugteil.

0021The cylinder bore of the master cylinder can be rigidly connected with the leading first vehicle part, while rotating the cam together with the trailing second vehicle part to the axis of rotation of the rotary joint. This alternative is preferably used at a fifth-wheel steering, where the removed using the steering decrease turning angle of the leading first vehicle part for power steering is used by at least one steering axle of a slave member, such as in the transport vehicle of the aforementioned<patcit id="pcit0004" dnum="DE202012010545U1"><text>DE 20 2012 010 545 U1</text></patcit>,

0022In this case, the rotary joint preferably comprises between the two vehicle parts of a ball joint. On both sides of the ball joint are advantageously pivot joints provided, which enable a tilting movement of the leading first vehicle part in relation to the trailing second vehicle portion about a vehicle transverse axis.

0023However, the cylinder tubes of the master cylinder can be rigidly connected to the trailing second vehicle part, while the cam is rigidly connected to the leading first vehicle part, so that they are at steering movements of the leading first vehicle part together with this about the rotational axis of the rotary joint between the two vehicle parts rotate.

0024This alternative is preferably used when the leading vehicle first part of a tractor and the trailing second vehicle part is a semi-trailer with a tractor with respect to the rotatable gooseneck and at least one steered by the slave cylinders steering axle.

0025In the following the invention with reference to an embodiment shown in the drawing will be further explained.<dl id="dl0001"><dt>Fig. 1</dt><dd>shows a perspective view of an unloaded inventive heavy-duty transport vehicle using a tractor and a trailer, which is connected by a telescopic support with gooseneck with the tractor;</dd><dt>FIG. 2</dt><dd>shows a side view of the transport vehicle;</dd><dt>Fig. 3</dt><dd>shows a top view of the transport vehicle when driving through a curve;</dd><dt>Fig. 4</dt><dd>shows an enlarged side view of the follower and a part of the telescopic support;</dd><dt>Fig. 5</dt><dd>shows an enlarged side view of a fifth wheel between the trailer and the telescope support;</dd><dt>Fig. 6</dt><dd>shows a rear view of the bogie; </dd><dt>Fig. 7</dt><dd>shows a perspective view of the rotary head with a support plate, a footrest plate and an interposed steering decrease;</dd><dt>Fig. 8</dt><dd>shows a top view of the bogie;</dd><dt>Fig. 9</dt><dd>shows a perspective top view of the support plate and the steering decrease;</dd><dt>Fig. 10</dt><dd>shows a top view of the support plate and the steering decrease when driving straight ahead;</dd><dt>Fig. 11</dt><dd>shows a top view of the support plate and the steering decrease when driving through a left turn;</dd><dt>Fig. 12</dt><dd>shows a top view of the support plate and the steering decrease when driving through a right turn;</dd><dt>Fig. 13</dt><dd>shows an enlarged perspective view of a portion of a cam and a master cylinder of the steering decrease;</dd><dt>Fig. 14</dt><dd>is an enlarged top perspective view of the cam;</dd><dt>Fig. 15</dt><dd>shows an enlarged perspective view of one of the master cylinder of the steering decrease;</dd><dt>Fig. 16</dt><dd>shows another enlarged perspective view of the master cylinder; </dd><dt>Fig. 17</dt><dd>shows a perspective bottom view of the footrest plate and the steering decrease;</dd><dt>Fig. 18</dt><dd>shows another bottom perspective view of the footrest plate and the steering decrease;</dd><dt>Fig. 19</dt><dd>is an enlarged bottom perspective view of a portion of the footrest plate and the steering decrease;</dd><dt>Fig. 20</dt><dd>shows another enlarged perspective bottom view of a portion of the footrest plate and the steering loss.</dd></dl>The shown in the drawing heavy-duty transport vehicle 10 essentially consists of a tractor 12, one 12 arranged at a distance behind the tractor three-axle trailer 14, as well as a telescopic support 16, which has a load bearing surface 18 and at its front end by a swan-neck 20 with the tractor 12 is connected.

0026Instead of the telescopic support 16 the tractor is 12 but also directly by an elongate load, such as a rotor blade of a wind power plant, to be connected to the trailer 14th

0027As best seen in <figref idrefs="f0002">Fig. 3</figref> and <figref idrefs="f0003">4</figref> shown, the slave member 14, a chassis 22, on which the wheels of the three axes 24, 26, 28 are mounted on both sides of a longitudinal beam 30th In the rear axles 26 and 28 is rigid axles, the wheels are not steerable. At the front axle 24 is a steering axle whose wheels are steerable.

0028Above the central axis 26, the slave member 14 includes a turntable 30 on. The turntable 30 includes an immovable connected to the slave member 14 and supported on the upper side of the longitudinal member 30 planar support plate 34, a fixed to the rear of the telescopic support 16 and can be fixedly connected to the rear end of the load rectangular stool plate 36, and a between the support plate 34 and the footrest plate 36 disposed hinge 38. the hinge 38 allows the one hand a rotation of the rear end of the telescopic support 16 or the load with respect to the slave member 14 about an axis extending through the center of the fifth wheel 30, to the ground 40 vertical axis of rotation 42 (<figref idrefs="f0002">FIG. 2</figref>) And on the other hand, a limited tilting movement of the rear end of the telescopic carrier 16 and the load relative to the trailer 14 by a base 40 parallel to the lower transverse axis 44 (<figref idrefs="f0002">Fig. 3</figref>) That is perpendicular to the rotation axis 42 and to a central longitudinal axis 46 of the telescopic support 16 and the load.

0029Between the support plate 34 and the footrest plate 36 a steering loss is 48, with a steering angle of the telescopic support 16 or the elongated load with respect to the slave member 14, ie the angle of rotation of the two vehicle parts 14, 16 relative to each other about the rotation axis 42 during impaction the telescopic support 16, can be detected or removed in order to steer the steering axis 24 of the follower 14 in response to this steering angle with a desired steering response.

0030The formed as a ball joint swivel joint 38 includes a rigid with the support plate 34 and upwardly over the top thereof protruding joint socket 50 (<figref idrefs="f0005 f0006">Figures 9 to 12</figref>), And a rigidly connected with the footrest plate 36 down on the underside of the protruding rod end 52 (Figures 17 and 18). As best seen in<figref idrefs="f0005">Fig. 9</figref> shown, surrounds the socket 50 a recess 54 with a concentric to the vehicle vertical axis 42 concave spherical surface. The recess 54 serves for receiving the ball head 52, which is supported with a part-spherical surface 56 on the spherical surface of the recess 54th In order to prevent a tilting of the footrest plate 36 about the longitudinal central axis 46 of the telescopic carrier 16 or the load, the footrest plate 36 is in each case an additional pivot joint 58 is supported along the transverse axis 44 on both sides of the rotary joint 38 about on the supporting plate 34, wherein the two pivot joints 58 tilting movements allow about the transverse axis 44th

0031The steering decrease 48 includes a vertical distance laid on top of the support plate 34 mounted and the support plate 34 parallel cam 60, which rotates together with the slave member 14 about the rotational axis 42nd Further, the steering approval includes 46 two hydraulic master cylinder 62 which rotate together with the rear of the telescopic support 16 or the elongated load to the rotation axis 42 and each having a cylinder tube 64 and includes a piston rod 66th

0032As in <figref idrefs="f0007">Fig. 14</figref> shown, the cam plate made from sheet steel or made from a lightweight but rigid plastic material 60 of two parts 68 which are mirror-symmetrical to a plane passing through the rotation axis 42 vertical longitudinal center plane 70 of the slave member 14 is composed. The cam plate 60 has an opening 72 for the joint socket 50 so that they can be fastened around the latter at a distance above the support plate 34th The cam 60 has a further about its periphery and rotating the surface of the support plate 34 vertical outer peripheral surface 74th

0033On the peripheral surface 74 rolls on two rollers 76, each of which is attached to a parallel to the rotation axis 42 axis 78 to rotate freely at the free end of one of the two piston rods 66 of the master cylinder 62nd When the rear end of the telescopic carrier 16 and the rear end of the elongated load when driving with respect to the slave member 14 rotates about the rotational axis 42, the two rollers move 76 on the outer peripheral surface 74 of the cam plate 60 along.

0034The outer circumferential surface 74 has along the path of movement of the rollers 76 no discontinuities in order to ensure smooth steering movements. The

0035Curve geometry of the outer periphery or the peripheral surface 74 of the cam plate 60 is formed with respect to the rotation axis 42 so that the piston rod 66 is retracted by one of the master cylinder 62 and the piston rod 66 of the other master cylinder 62 is extended by the same amount when the slave member 14 another turn and the telescopic supports 16 or the load with respect to the axis of rotation 42nd This is achieved by the fact that starting from a rotational position (<figref idrefs="f0005">FIGS. 9 and 10</figref>), In which the longitudinal center axis 70 of the follower 14 in plan view, with the longitudinal center axis 46 of the telescopic support 16 and the load is aligned in both directions of rotation, the distance between the roller 76 and the rotation axis 42 decreases for one of the two master cylinder 62 and the other master cylinder 62 increases by the same amount.

0036With the adapted to the number of steering axles 24 of the trailer 14 curve geometry of the outer periphery or the peripheral surface 74 of the cam 60 allows the control of the vehicle 10 influence in an ideal manner. On the one hand between the rotational position in<figref idrefs="f0005">FIGS. 9 and 10</figref> on the one hand and the two rotary positions in <figref idrefs="f0006">Fig. 11</figref> and 12 on the other hand, where the telescopic supports 16 and the load is taken with different directions of rotation and a steering angle of 45 degrees with respect to the trailer 14, the distance between the roller 76 and the rotation axis 42 are changed by a desired amount. On the other hand, the slope of the outer circumference or the peripheral surface 74 of the cam plate 60, that is the first derivative of the distance may be changed in a desired manner. The degree of change in the distance of the peripheral surface 74 from the axis of rotation 42 between the rotational position in<figref idrefs="f0005">FIGS. 9 and 10</figref> on the one hand and the two rotary positions in <figref idrefs="f0006">Fig. 11</figref> or 12 the other hand, determines the relationship between the turning angle of the telescopic support 16 or the load in relation to the trailer 14 on the one hand and the steering angle of the steering axis 24 of the trailer 14 on the other. In other words, 62 can be changed between two rotational positions of the steering angle of the steering axle 24 of the trailer 14 between these rotational positions by a desired amount by a predetermined change in the distance or the movement path of the piston rods 66 of the master cylinder. The slope of the outer circumference or the peripheral surface 74 of the cam 60, however, determines the aggressiveness of the steering of the steering axle 24 of the trailer 14. In other words, the speed of the forward stroke steering of the trailer 14 can be changed by a predetermined change of the slope.

0037The two master cylinder 62 are part of a hydraulic dual-circuit steering device (not shown) of the slave member 14, which includes in addition to the master cylinders 62 two slave cylinder (not shown), each circuit includes a master cylinder 62 and a slave cylinder. The two slave cylinders each engage on opposite sides of the steering axis 24, each slave cylinder (not shown) through lines is connected to a master cylinder of the 62nd On the other hand the two circuits of the steering device are not connected.

0038As best seen in <figref idrefs="f0005 f0006">Figures 9 to 12</figref> shown, the two master cylinder 62 are arranged on opposite sides of the rotary joint 38 and the cam 60, with their longitudinal central axes are aligned with each other and intersect the axis of rotation 42nd The piston rods 66 are directed toward the cam 60 back.

0039In order to prevent a lifting of the rollers 76 from the outer peripheral surface 70, the master cylinder 62 are biased in the respective circuit with a hydraulic pressure of about 30 bar, so that the piston rods 66, the rollers 76 pressing against the peripheral surface 74th In addition, the rollers 76 of the two master cylinder 62 by means of two O-shaped brackets 80, 82 connected to each other to ensure a constant distance between the rollers 76 and the free ends of the two piston rods 66 of the master cylinder 62nd The one 80 of the two brackets 80, 82 is arranged above the cam plate 60 and hinged to the upper ends of the rollers 76, while the other strap 82 is disposed below the cam plate 60 and is hinged to the lower ends of the rollers 76th The hydraulic preload of the two hydraulic circuits and the strap 80 ensures that the rollers 76 are tracked to the outer periphery of the cam 60 while driving and not stand out from the circumferential surface 74, and that the movement of the piston rods 66 of the master cylinder 62 is always exactly the same is.

0040The two mirror-symmetrical to the rotation axis 42 bracket 80, 82 each enclose a generally rectangular opening with rounded corners, the rotary joint through which extends 38 along the rotation axis 42 passes.

0041As best seen in <figref idrefs="f0009">Figures 17 and 18</figref> shown, the cylinder tubes 64 of the master cylinder 62 are held by means of swivel joints 58 so at the bottom of the footrest plate 36 to rotate with the footrest plate 36, but 36 allow tilting of the footrest plate to the transverse axis 44 of the aligned longitudinal central axes master cylinder 62 coincides. For holders of the cylinder tubes 64 of the master cylinder 62, the cylinder tubes 64 are each provided with a support 84 which is movable relative to the mounting plate 34, on the part of the forces acting on the footrest plate 36 load on the support plate 34 is transmitted and on the footrest plate 36 pivotally supported.

0042The holder 84 surrounding the respective cylinder tube 64 and is rigidly connected thereto. The bracket 84 has on its the supporting plate 34 underside facing a slide plate 86 having a the top of the support plate 34 parallel planar sliding surface, which slides in steering to the axis of rotation 42 around on the support plate 34, as best seen by comparing<figref idrefs="f0006">FIGS. 11 and 12</figref> is visible. As best seen in<figref idrefs="f0007">Fig. 13</figref>. <figref idrefs="f0008">15 and 16</figref> shown, the bracket 84 on its stool of plate 36 facing top on a saddle 88 with the transverse axis 44 coaxial convex part-cylindrical surface 90th As best seen in<figref idrefs="f0009">FIGS. 17 and 18</figref> shown, engages the seat 88 in a recess 92 in the underside of the footrest plate 36, where it is within the recess 92 against a complementary concave part-cylindrical surface (not visible) of the footrest plate 36 abuts and along with this the swivel joint 58 forms, the rocking motion a the telescopic support 16 allows the trailer 14 with respect to the transverse axis 44th The saddle 88 is connected by means of supports 94 rigidly connected to the slide plate 86th

0043To reduce weight, the cam 60 and the slide plate 86 are provided with holes 96 and 98th The holes 98 of the slide plate 86 are also filled with grease to lubricate the sliding movement of the brackets 82 on the supporting plate 34th

0044With the steering decrease 46 previously described a simple adaptation to a varying number of steering axles of the trailer 14 is possible by each master cylinder 62, a master cylinder 62 used in an increase in the number of steering axles instead of a larger diameter, or between the footrest plate 36 and the support plate 34 another cam and two more master cylinder are provided to take account of the greater demand for oil for steering the other steering axles.