Steering device of a vehicle

Abstract

The invention relates to a steering device (100, 101, 102) for a vehicle, in particular an industrial truck, having a rotatably mounted steering control element, a steering signal transmitter for acquiring the rotational position of the steering control element, and a braking device (30) for generating a rotary braking torque acting on the steering control element. The braking device (30) is in the form of a friction brake (31) generating a substantially permanently constant braking torque, and / or in the form of a speed-sensitive eddy current brake.

Description

[0001] Steering device of a vehicle

[0002] The invention relates to a steering device for steering at least one steerable wheel of a vehicle, in particular an industrial truck, in particular a tiller-guided industrial truck, with a rotatably mounted steering actuating element, a steering signal transmitter operatively connected to the steering actuating element and a steering control for detecting the rotational position of the steering actuating element and a braking device connected to the steering actuating element for generating a rotational braking torque acting on the steering actuating element.

[0003] It should be clear that the steering device can also be assigned a steering drive connected to the at least one steerable wheel of the vehicle, wherein the steering drive is controllable depending on the electrical output signal of the steering control and / or the steering signal transmitter. The steering signal transmitter can serve to directly or indirectly control the steering drive acting on the at least one steerable wheel.

[0004] Such steering systems are often referred to as electric steering or "steer-by-wire" steering systems and are well known. In particular, these steering systems lack a mechanical connection between the steering actuator, which can be moved by an operator, and the steerable wheel or a steering drive that generates the steering force at the steerable wheel. Rather, a change in the angle of the steering actuator is usually detected by the steering signal transmitter, and a corresponding electrical output signal is output. This signal is processed in an electric steering control or control device, and the steering drive is controlled accordingly. The steering drive is usually designed as an electric motor. The steering drive, also called a servomotor, is often connected to the steerable wheel via a suitable transmission.Alternatively, the steering drive can act on a vehicle joint, which allows the vehicle to perform a steering movement. Such a vehicle joint can be provided, for example, in articulated vehicles or tiller-guided industrial trucks.

[0005] Since in such steering systems the signal transmission between the steering actuating element and the associated steering drive is exclusively electrical, the actuating force of the steering actuating element is independent of the force exerted by the steering drive. In particular, the steering forces acting on the steerable wheel are not transmitted to the steering actuating element due to the lack of a mechanical connection. In order to simulate the operating characteristics of a mechanical steering system and to give the operator a feel for the steering forces actually present at the steerable wheel, it is known to have a device on the steering actuating element for braking the rotational force or for generating a resistance in order to exert a defined braking torque on the steering actuating element.

[0006] Such permanently uniform braking devices are typically designed as hydraulic brakes, also known as fluid brakes or water vortex brakes. The shaft to be braked—in this case, a steering shaft connected to the steering actuation element—is connected to a rotor disposed in a fluid. The mechanical work is converted at the rotor into kinetic energy of the fluid flow, which is ultimately dissipated primarily as heat through turbulence. It is therefore also referred to as brake fluid. Brake fluids of varying viscosity can be used to adjust the strength of the braking. For example, thick, high-viscosity fluids typically have a greater potential for slowing rotation than thin, low-viscosity fluids.However, it has been shown that when such industrial trucks are used in different areas of application, particularly in environments with different temperatures, the viscosity of the fluid and thus also the braking performance of the braking device can vary.

[0007] For example, in an industrial truck used in a cold storage facility, where temperatures are typically particularly low, the viscosity of the brake fluid may be relatively high due to the temperature, resulting in a relatively high resistance force acting on the steering actuator. If, for example, this industrial truck is then used to transport a pallet outside the cold storage facility, where ambient temperatures are significantly higher than those inside the cold storage facility, the viscosity of the brake fluid and the resistance force acting on the steering actuator decrease. As a result, an operator experiences temperature-dependent different resistance forces on the steering actuator and must regularly take these into account when operating the truck. This can significantly impair safe operation of the industrial truck.

[0008] The present invention is therefore based on the object of providing a steering device for a vehicle which improves at least one of the above-mentioned disadvantages and in particular enables improved driving safety of the vehicle compared to the prior art and a particularly compact braking device.

[0009] The invention solves the stated problem by a steering device having the features of the main claim. Advantageous embodiments and further developments of the invention are disclosed in the subclaims, the description, and the figures.

[0010] According to the invention, the braking device is designed as a friction brake generating a permanently constant braking torque and / or as a speed-dependent eddy current brake. By designing the braking device as a friction brake generating a permanently constant braking torque, a permanently constant, in particular temperature-independent, braking torque or resistance against the movement of the steering actuating element can be achieved. As a result, the force required by an operator to steer the vehicle can remain permanently constant, thus enabling particularly safe operation of the vehicle. A friction brake can be understood in particular as an arrangement of two components in frictional contact with one another. One of these components can be connected to the steering actuating element in a rotationally fixed manner. It can be arranged, for example, on the shaft of a steering wheel. The other of the components is arranged stationary.The resistance force is generated by the frictional force of the aforementioned components, in particular a purely mechanical friction, which can be adjusted by the pressure exerted by the two components against each other – in this case, permanently constant, i.e., unchanged during operation. Therefore, the aforementioned components are also called resistance elements. The resistance moment is generated by the friction between the two braking elements. A resistance moment is thus generated as a reaction force to a movement of the steering actuating element and is always opposite to the actuating direction of the steering actuating element.

[0011] By designing the braking device as a speed-dependent eddy-current brake, a braking torque or resistance to the movement of the steering actuating element can also be achieved by utilizing the Lorentz force. In this design, for example, an electric motor can also be short-circuited, allowing the induced electrical voltage to be reduced. To achieve a sufficiently high speed of the steering shaft for this purpose, a transmission gear can be provided between the steering actuating element and the braking device.

[0012] In a further embodiment of the invention, the braking device can comprise a combination of a friction brake and an eddy-current brake. It should be clear that, in the braking device according to the invention, the resistance force is adjusted by the manufacturer during assembly, whereas, during subsequent operation of the vehicle, the resistance force of the braking device ideally remains unchanged. Thus, in a steering device according to the invention, the resistance moment of the braking element remains permanently constant throughout the operation of the vehicle.

[0013] Particularly preferably, the braking device is designed to be fluid-free. This means that the braking device contains no fluid at all. As a result, the braking device and its effective power are temperature-independent, so that the resistance force acting on the steering actuating element remains consistently high.

[0014] The braking device preferably comprises at least two discs rubbing against each other, in particular a stationary thrust disc and a rotating disc, also called a counter-rotating disc. The braking device can be designed in the manner of a disc brake. This allows the braking device to be particularly compact and particularly efficient in its operation.

[0015] Preferably, the discs are preloaded against each other with a permanently constant force. This allows the frictional force between the discs to be predefined. In particular, the frictional force can be permanently adjusted via the preload force. The preload force can be applied in various ways, for example, via a screw connection, using magnets, or using a spring element.

[0016] To generate the preload force, the braking device preferably has a device for generating a magnetic field. This device can in particular be integrated into the braking device. Particularly preferably, the braking device comprises at least one permanent magnet for generating the preload force. The permanent magnet can be designed, for example, as a conventional magnet, in particular as a neodymium magnet. The permanent magnet can generate a magnetic field by which a ferromagnetic disk, in particular a steel disk, is drawn towards the at least one magnet or can be pushed away from the at least one magnet. In particular, the disk can be preloaded by means of the magnet to generate friction with a disk moving relative to it. In this way, friction between the rotating, ferromagnetic counter-rotating disk and a stationary thrust disk can be permanently increased.Alternatively, a spring element can be provided to generate the preload force.

[0017] In one embodiment of the invention, the braking device comprises a stationary support plate. As the name suggests, the support plate can be designed as a plate or disc, in particular as a substantially round disc. The support plate can be secured to the vehicle, in particular to the vehicle chassis, via fastening means.

[0018] At least one permanent magnet can be arranged on the carrier plate. Preferably, two, six, eight or ten individual permanent magnets are arranged on the carrier plate. If more than one permanent magnet is arranged, the magnets are preferably arranged symmetrically on the carrier plate. If the carrier plate is designed as a substantially round disk, the permanent magnets are preferably arranged on the carrier plate so as to be evenly distributed over the circumference. An opening can be provided in the center of the carrier plate, through which opening a part of a shaft of the steering actuating element, in particular a steering shaft, can extend. A thrust washer can be provided on a side of the carrier plate facing the friction surface for braking the steering shaft.

[0019] The thrust washer can be mechanically connected to the carrier plate, so that the thrust washer is also fixed in place. The thrust washer can have a sliding surface against which the counter-rotating disc can run to generate friction. Preferably, at least one ferromagnetic counter-rotating disc is provided, which is connected in a rotationally fixed manner to the steering actuating element. For this purpose, the counter-rotating disc can, for example, have a key surface in the center with which the steering shaft engages, so that the counter-rotating disc and steering shaft are connected in a rotationally fixed manner. In principle, the materials can also be reversed, i.e., the thrust washer can be ferromagnetic and the counter-rotating disc can serve as a sliding pair.

[0020] The counter-rotating disk can be preloaded directly or indirectly against the carrier plate, i.e. in particular against the thrust washer connected to the carrier plate, by means of the at least one permanent magnet. The permanent magnet can be designed, for example, as a ring magnet. The magnetic field generated by the at least one magnet serves to preload or press the rotatable, ferromagnetic counter-rotating disk onto the stationary thrust washer, between which the friction takes place to brake the kinetic rotational energy. The at least one magnet can be inserted into a recess or receptacle provided on the carrier plate. For example, the magnet can be cylindrical and inserted into a bore provided on the carrier plate. In the case of a round carrier plate, the receptacle can be in the axial or radial direction, for example.

[0021] In a further development of the invention, it can be provided that a ferromagnetic counter-rotating disk is arranged on each side of the carrier plate, wherein both counter-rotating disks are prestressed in the direction of the carrier plate by means of the at least one magnet arranged in the carrier plate. In particular, a ferromagnetic disk can be arranged on each side of the planar extension of the carrier plate. Furthermore, both disks are preferably prestressed in the direction of the carrier plate by means of the at least one magnet arranged in the carrier plate. As a result, the braking power can be increased, in particular doubled. Furthermore, in particular on both axial sides of the carrier plate, in particular of the carrier plate designed essentially as a round disk, a thrust disk and a rotatable, ferromagnetic counter-rotating disk connected to the steering shaft can be arranged.Both counter-rotating discs can be preloaded toward the respective thrust washer by means of the same magnet(s), in particular attracted toward the carrier plate. It can be provided that, when at least two sliding discs are arranged, different, or a reduced, breakaway torque between static and sliding friction is enabled, so that the brake applies and decelerates relatively "smoothly." This can be achieved, in particular, by a time-delayed entrainment of the respective sliding disc by the steering shaft. For example, a first sliding disc is entrained immediately upon rotation of the steering shaft, and a second sliding disc only after the steering shaft has rotated beyond a predefined angle. The different entrainment can be achieved via mechanical entrainment means. It should be clear that the preload of the two sliding discs is preferably the same.

[0022] It was further determined that using the magnetic design, no screws or additional fasteners are required to generate the preload force and / or to hold the carrier plate, thrust washer, and counter-rotating washer together. All of the aforementioned components can be held together solely by the magnetic force of attraction.

[0023] Particularly preferably, the at least one thrust washer, with which the ferromagnetic counter-rotating disk is in frictional contact, is arranged between the carrier plate and the counter-rotating disk, in particular fixed to the carrier plate. For this purpose, the thrust washer can have a recess through which a pin or a fastening screw can extend for rotational fixation to the carrier plate. The pin can, for example, be a component of the carrier plate.

[0024] Preferably, the at least one permanent magnet is fixed to the carrier plate on both sides in a direction perpendicular to the surface extension of the carrier plate, in particular in the axial direction of the carrier plate. This means that the magnet is immobile relative to the carrier plate in the axial direction of the carrier plate, in which it preferably generates the magnetic field and attracts the ferromagnetic disc. This enables a particularly reliable, permanent brake.

[0025] As a design solution, the carrier plate can include at least two circumferential recesses, into each of which a permanent magnet can be radially inserted or inserted. The receptacle can, for example, be a radially arranged recess that has essentially the same shape as the magnet, for example, cylindrical or square. This allows the magnet to be held and fixed particularly securely in the receptacle of the carrier plate. Since the carrier plate is preferably arranged in a stationary manner, radial securing of the magnets in the receptacle is not necessarily required.

[0026] In a further embodiment of the invention, it is provided that the braking device comprises at least one stationary support plate on which at least one spring element is arranged, and at least one counter-rotating disc which is connected to the steering actuating element in a rotationally fixed manner and which is prestressed directly or indirectly against the support plate by means of the at least one spring element.

[0027] Preferably, a counter-rotating disc, a thrust disc, and a portion of the carrier plate are arranged on each side of the spring element, with both counter-rotating discs being preloaded toward the carrier plate by the at least one spring element. This allows for a particularly compact design of the braking device. The spring element can be designed as one or more conventional spiral springs or as a round disc spring. With the disc spring, the spring force can act from the center. The spring element preferably acts in both axial directions of the braking device or of the discs rubbing against each other.

[0028] Preferably, the spring element can be preloaded via a screw supported on the support plate. For example, a grub screw can be provided in the support plate, which rests directly or indirectly on the spring element with a free end and preloads the spring element to varying degrees depending on the screw-in depth.

[0029] In a further embodiment of the invention, the carrier plate is designed in two parts. This allows the at least one magnet or magnets to be advantageously held in the carrier plate when designing a two-sided friction brake (two friction pairs). Furthermore, particularly time- and cost-effective production is enabled. Furthermore, the size of the magnet receptacles can be adjusted particularly easily, allowing magnets of different strengths and thus different braking torques to be generated with the same carrier plate.

[0030] Preferably, the at least one permanent magnet is fixed to the carrier plate on one side in a direction perpendicular to a surface extension of the carrier plate, in particular in the axial direction of the carrier plate. The fixation can be achieved via a shoulder provided on the magnet. For this purpose, the magnet preferably has a protruding shoulder at a free end, in the case of a cylindrical design, in particular at an axial end, on which the magnet can be supported on the carrier plate and fixed at least in one axial direction.

[0031] Preferably, the carrier plate is designed as a two-part housing cover, which, when assembled, encloses the friction components, in particular the thrust washer and counter-rotating washer. This enables a particularly reliable and compact brake.

[0032] In one embodiment, the steering actuating element is designed as a tiller head of a tiller-guided industrial truck. In particular, a steering actuating element, typically designed as a tiller head, is arranged to rotate within at least a predefined angular range. The braking device also serves to decelerate the rotational movement generated by the operator and / or by a built-in return spring.

[0033] Two exemplary embodiments of the invention are explained in more detail below with reference to the figures. Like reference numerals denote like components. They show purely schematically:

[0034] Figure 1 - a first embodiment of a braking device of a steering device according to the invention in a perspective exploded view; Figure 2 - a second embodiment of a braking device of a steering device according to the invention in a perspective exploded view;

[0035] Figure 3 - the braking device according to Fig. 2 in an assembled state in a perspective view;

[0036] Figure 4 - the braking device according to Fig. 2 in a sectional view;

[0037] Figure 5 - a third embodiment of a braking device of a steering device according to the invention in a perspective exploded view; and

[0038] Figure 6 - the braking device according to Fig. 5 in an assembled state in a perspective view;

[0039] In Figure 1, reference numeral 100 shows part of a steering device according to the invention for a vehicle (not shown), in particular an industrial truck. For the sake of clarity, the steering device 100 is shown without a steering wheel, which is typically provided at the left end of a steering shaft 20 in Figure 1. The steering device 100 comprises a braking device 30, which is arranged at the right end of the steering shaft 20 in Figure 1, in particular at the free end of the steering shaft 20 there.

[0040] In the simple embodiment shown, the braking device 30 comprises a carrier plate 2, at least one magnet 4 which can be inserted therein - in the present case there are eight magnets 4 -, a thrust washer 1 and a counter-rotating washer 3.

[0041] The carrier plate 2 is fastened to the vehicle via fastening eyes 10, 11, so that the carrier plate 2 is arranged in a stationary manner. In a circumferential region, the carrier plate 2 in this case has eight receptacles 17, each with an opening 18, through which a magnet 4 can be inserted into the receptacle 17. In this case, the receptacle 17 is in particular each cylindrical in a size that corresponds approximately to the outer circumference of a magnet 4. Of course, the magnet and the receptacle can also have any other corresponding shape. On the bottom of the receptacle 17, an inwardly projecting shoulder can be provided, against which the magnet 4 can come to rest after it has been fully inserted into the receptacle 17. The magnet 4 is thus secured in at least one axial direction, in particular in the direction of the thrust washer 1.

[0042] Alternatively, a radially projecting shoulder can be formed on the magnet 4, with which the magnet 4 comes into axial contact with the carrier plate 2 after it has been fully inserted into the receptacle 17 and is thereby blocked from further movement in the insertion direction.

[0043] On the side of the carrier plate 2 opposite the opening 18, the thrust washer 1 rests against the carrier plate 2. The thrust washer serves as protection for the carrier plate 2 and the magnets 4. The thrust washer has a fixing recess 12, which engages with a pin 16 formed on the carrier plate 2. As a result, the thrust washer 1 is arranged in a rotationally fixed manner relative to the carrier plate 2.

[0044] The counter-rotating disc 3, which is connected to the steering shaft 20 in a rotationally fixed manner and is thus rotatable, serves to brake the steering shaft 20. For this purpose, the counter-rotating disc 3 is connected to the steering shaft 20, particularly in section 21, in a rotationally fixed manner via a key surface 13. The counter-rotating disc 3 is designed as a ferromagnetic disc and is attracted in the direction of the carrier plate 2 by a magnetic field generated by the magnets 4. The resulting preload force presses the counter-rotating disc 3 against the thrust disc 1. This creates friction between the rotating counter-rotating disc 3 and the stationary thrust disc 1, which brakes the counter-rotating disc 3 and thus also the steering shaft connected to it.

[0045] In Figure 2, reference numeral 101 shows part of a steering device of a vehicle (not shown), in particular with a second embodiment of a braking device 30. For the sake of clarity, the steering device 101 is again shown without a steering wheel, which is provided at the left end of the steering shaft 20 in Figure 2. In Figures 2 to 6, the braking device 30 is designed as a double-acting friction brake. The structure of the braking device 30 is very similar to the structure described above for Figure 1, except for an additional arrangement of a further starting disk and counter-running disk on the second flat side of the carrier plate 2. Furthermore, the carrier plate 2 is designed in two parts in Figures 2 to 4.

[0046] Again, the braking device 30 in the double embodiment shown comprises a carrier plate 2, at least one magnet 4 insertable therein, now two thrust washers 1a, 1b and two counter-running washers 3a, 3b.

[0047] The carrier plate 2 is in turn fastened to the vehicle via fastening eyes 10, 11, so that the carrier plate 2 is arranged in a stationary manner. In a peripheral region, the carrier plate 2 in this case has eight receptacles 17, each with an opening 18, through which a magnet 4 can be inserted into the receptacle 17. In this case, the receptacle 17 is each cylindrical in a size approximately corresponding to the outer circumference of a magnet 4. The receptacle 17 and / or the magnet 4 in turn have suitable means for axial fixing, in particular a contact shoulder.

[0048] On each axial side of the carrier plate 2, a thrust washer 1a, 1b is connected to the carrier plate 2 in a rotationally fixed manner. The thrust washer 1a, 1b, in turn, serve as protection for the carrier plate 2 and for the magnets 4. In principle, the thrust washer 1a, 1b can be of identical design. In particular, the thrust washer 1a, 1b each have a fixing recess 12, which engages with a pin 16 formed on the carrier plate 2, so that movement of the thrust washer 1a, 1b in the circumferential direction is blocked.

[0049] In the braking device 30 according to this second embodiment, two counter-rotating discs 3a, 3b are each pulled against one of the thrust washers 1a, 1b by means of the magnets 3. The preload force or attraction of the two counter-rotating discs 3a, 3b is advantageously equal. The rotating counter-rotating discs 3a, 3b, which are connected to the steering shaft 20 via the key surfaces 13 and 21, thus exert a double braking torque on the steering shaft 20.

[0050] The carrier plate 2 is in this case constructed in two parts, in particular with a first carrier plate 2a and a second carrier plate 2b. This enables, on the one hand, particularly simple mounting of the at least one magnet 4 on the carrier plate 2 and, on the other hand, fixation of the at least one magnet 4 in both axial directions of the carrier plate 2. For example, the opening 18 of the receptacle 17 can face the magnet 4 arranged between the two carrier plate halves 2a, 2b. The at least one magnet 4 can thus be inserted into both carrier plate halves 2a, 2b. Both carrier plate halves 2a, 2b have a shoulder on the bottom of the receptacle 17, in particular an inwardly projecting shoulder, against which the magnet 4 comes into contact after it has been fully inserted. The carrier plate halves 2a, 2b are then connected to one another to form the carrier plate 2, so that the magnets are integrated into the carrier plate.This enables a particularly compact and safe friction brake.

[0051] It can also be provided that the opening 18 of the receptacle 17 is not aligned in the axial direction, but on the circumferential wall of the carrier plate 2. In this case, the at least one magnet 4 is pushed into the carrier plate 2 from radially outside. As a result, the at least one magnet 4 is particularly securely secured in the axial direction of the carrier plate 2. Since the carrier plate 2 does not rotate, securing in the radial direction is possible, but not absolutely necessary. It can also be provided that the opening 18 of the receptacle 17 is arranged on an inner circumferential side, so that the at least one magnet 4 is pushed into the carrier plate 2 from radially inside.Furthermore, it is possible for the two carrier plate halves 2a, 2b each to have a half receptacle 17, into which the at least one magnet 4 is completely received when the carrier plate halves 2a, 2b are joined together, so that complete integration of the magnet 4 into the carrier plate 2 is possible. A third embodiment of a steering device according to the invention with a braking device 30 is shown in Figures 5 and 6 with the reference numeral 102. In this case, it is provided that the braking device 30 - similar to the embodiment shown in Figures 2 to 4 - has two thrust washers 1a, 1b and two counter-rotating washers 3a, 3b. However, the preload force is not realized via magnets but via a spring element 32. The spring element 32 can - as shown - be designed as a spiral spring or, alternatively, as a round disc spring.Here, a counter-rotating disk 3a, 3b, a thrust disk 1a, 1b, and a part of the carrier plate 2a, 2b, also called half of a carrier plate, are arranged on each side of the spring element 32, wherein both counter-rotating disks 3a, 3b are preloaded in the direction of the carrier plate 2a, 2b by means of the at least one spring element 32. In particular, the two counter-rotating disks 3a, 3b are pressed axially away from each other, each against the thrust disk 1a, 1b, which is non-rotatably connected to one half of a carrier plate 2a, 2b.

[0052] The two halves of the support plate 2a, 2b are designed as a cover and serve as the housing of the braking device 30. The support plate 2a, 2b is in turn arranged in a fixed position and is secured to the vehicle, in particular via lateral eyelets. Additional fixation of the two support plates 2a, 2b to each other can be provided, so that the support plates 2a, 2b can lie against each other - as shown in Figure 6 - and thus each form a "half."

[0053] It can be provided that, in the embodiment shown in Figures 5 and 6, at least one adjusting screw (not shown here) is provided on one or both of the support plates 2a, 2b, by means of which adjusting screw the respective thrust washer 1a, 1b can be driven forward in the direction of the spring element 32. The adjusting screw can, for example, be designed as a grub screw, which rests with a free end on the thrust washer 1a, 1b and engages with the support plates 2a, 2b via a thread. This allows an individual friction force to be set between the thrust washer 1a, 1b and counter-rotating washer 3a, 3b, and thus an individual, permanently effective braking power. It should be clear that the scope of protection of the present invention is not limited to the described embodiments.In particular, the number and arrangement of the magnets, the number and design of the spring element, and the structure of the support plate can be modified without altering the core of the invention. Furthermore, the static and rotating parts can be reversed in their mounting arrangement, i.e., static parts become rotating parts and vice versa.

[0054] Reference list:

[0055] 1, la, lb thrust washer

[0056] 2, 2a, 2b carrier plate

[0057] 3, 3a, 3b Counter-rotating disc

[0058] 4 Magnet

[0059] 10 fastening eyelets

[0060] 11 Mounting eyelet

[0061] 12 Fixing recess

[0062] 13 key surface

[0063] 14 Contact surface, friction surface

[0064] 15 Counter surface, friction surface

[0065] 16 pin

[0066] 17 recesses

[0067] 18 Opening

[0068] 20 Steering shaft

[0069] 21 key surface

[0070] 30 Braking device

[0071] 31 Friction brake

[0072] 32 spring element

[0073] 100 steering device

[0074] 101 Steering device

[0075] 102 Steering device

Claims

Patent claims:

1. Steering device (100, 101, 102) for a vehicle, in particular an industrial truck, with a rotatably mounted steering actuating element, a steering signal transmitter for detecting the rotational position of the steering actuating element and a braking device (30) for generating a rotational braking torque acting on the steering actuating element, characterized in that the braking device (30) is designed as a friction brake (31) generating a braking torque of essentially the same design over the long term and / or as a speed-dependent eddy current brake.

2. Steering device (100, 101, 102) according to claim 1, characterized in that the braking device (30) is designed to be fluid-free.

3. Steering device (100, 101, 102) according to one of claims 1 or 2, characterized in that the braking device (30) comprises at least one rotatable brake disc (3, 3a, 3b).

4. Steering device (100, 101, 102) according to one of the preceding claims, characterized in that the braking device (30) comprises at least two discs (1, 1a, 1b, 3, 3a, 3b) rubbing against one another, in particular a stationary thrust disc (1, 1a, 1b) and a rotatable counter-rotating disc (3, 3a, 3b).

5. Steering device (100, 101, 102) according to one of claims 3 or 4, characterized in that the at least one disc (1, 1a, 1b, 3, 3a, 3b) is prestressed with a force that remains substantially constant.

6. Steering device (100, 101, 102) according to one of claims 3 to 5, characterized in that for generating the pretensioning force, the braking device (30) comprises at least one permanent magnet (4) or a spring element (32).

7. Steering device (100, 101) according to one of the preceding claims, characterized in that the braking device (30) comprises at least one stationary carrier plate (2, 2a, 2b) on which at least one permanent magnet (4) is arranged, and at least one ferromagnetic counter-rotating disc (3, 3a, 3b) which is connected in a rotationally fixed manner to the steering actuating element and which is prestressed directly or indirectly against the carrier plate (2, 2a, 2b) by means of the at least one permanent magnet (4).

8. Steering device (100, 101) according to claim 7, characterized in that a ferromagnetic counter-rotating disc (3, 3a, 3b) is arranged on each side of the carrier plate (2, 2a, 2b), and both counter-rotating discs (3, 3a, 3b) are prestressed in the direction of the carrier plate (2, 2a, 2b) by means of the at least one magnet (4) arranged on the carrier plate (2, 2a, 2b).

9. Steering device (100, 101) according to one of claims 7 or 8, characterized in that the at least one permanent magnet (4) is fixed to the carrier plate (2, 2a, 2b) on one side or both sides in a direction perpendicular to a surface extension of the carrier plate (2, 2a, 2b), in particular in the axial direction of a carrier plate (2, 2a, 2b) designed essentially as a disk.

10. Steering device (100, 101) according to one of claims 7 to 9, characterized in that the carrier plate (2, 2a, 2b) comprises at least one recess (17) into which a permanent magnet (4) is inserted, in particular can be inserted radially.

11. Steering device (102) according to one of claims 1 to 6, characterized in that the braking device (30) has at least one stationary arranged support plate (2, 2a, 2b), on which at least one spring element is arranged, and at least one counter-rotating disc (3, 3a, 3b) which is connected to the steering actuating element in a rotationally fixed manner and which is prestressed directly or indirectly against the support plate (2, 2a, 2b) by means of the at least one spring element.

12. Steering device (102) according to claim 11, characterized in that a counter-rotating disc (3, 3a, 3b), a thrust washer (1, 1a, 1b) and a part of the carrier plate (2, 2a, 2b) are arranged on both sides of the spring element, and both counter-rotating discs (3, 3a, 3b) are prestressed in the direction of the carrier plate (2, 2a, 2b) by means of the at least one spring element.

13. Steering device (102) according to one of claims 11 or 12, characterized in that the spring element can be pretensioned via a screw supported on the carrier plate (2, 2a, 2b).

14. Steering device (100, 101, 102) according to one of claims 7 to 13, characterized in that a thrust washer (1, 1a, 1b) is arranged between the carrier plate (2, 2a, 2b) and the counter-rotating disk (3, 3a, 3b), in particular fixed to the carrier plate (2, 2a, 2b).

15. Steering device (100, 101, 102) according to one of claims 7 to 14, characterized in that the carrier plate (2, 2a, 2b) is formed in two parts, in particular comprising a first carrier plate (2a) and a second carrier plate (2b).

16. Steering device (100, 101, 102) according to one of the preceding claims, characterized in that the carrier plate (2, 2a, 2b) is designed as a two-part housing cover which, in an assembled state, surrounds the friction components, in particular the thrust washer (1, 1a, 1b) and counter-rotating washer (3, 3a, 3b).

17. Steering device (100, 101, 102) according to one of the preceding claims, characterized in that the steering actuating element is designed as a tiller head of a tiller-guided industrial truck.

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