Steering gear for an electromechanical steering system for a vehicle and electromechanical steering system for a vehicle

Abstract

Steering gear (120) for an electromechanical steering system (110) for a vehicle (100), wherein the steering gear (120) comprises an electric motor (230), a servo gearbox (240), and a bevel gear (250) for connecting a steering column (114) of the steering system (110) to a steering arm (116) of the steering system (110), characterized in that the bevel gear (250) is a mechanically driven ball screw drive with a ball nut (254) which engages with a segment shaft (122) of the steering gear (120) which can be connected to or is connected to the steering arm (116), wherein a spindle groove of a spindle (252) of the ball screw drive is continuous over the entire length of the spindle (252), wherein the spindle (252) is connected at one side to an output shaft of the servo gearbox (240), wherein the servo gearbox (240) is driven by the electric motor (230). is driven or driven, wherein the servo gear (240) is a planetary gear,wherein the planetary gear has planet gears (348) with identical number of teeth and geometry, wherein the planet gears (348) mesh with two independent ring gears (342, 344) with different numbers of teeth, wherein the planet gears (348) can be driven or are driven by the electric motor (230) via a carrier (346), wherein the ball nut (254) of the ball screw drive has a linear guide device designed to receive radial loads introduced by a toothing between the segment shaft (122) and the ball nut (254).

Description

[0001] The present invention relates to a steering gear for an electromechanical steering system for a vehicle and to an electromechanical steering system for a vehicle, in particular for a commercial vehicle.

[0002] A power steering system, as part of a commercial vehicle's steering system, is typically implemented as a hydraulic system. Hydraulic systems can be disadvantageous in terms of energy efficiency, as a high volume of fluid must be pumped through the steering system to provide steering force at all times. Furthermore, additional functions beyond the core steering function, such as driver assistance systems, can be complex to implement. Additionally, due to the separate installation locations of the steering pump and steering gear, lines are usually required between them, which must be installed, filled, and tested during vehicle assembly.

[0003] From DE 10 2010 053 581 A1, a power steering system for a commercial vehicle is known, comprising: an electric drive motor for generating a drive torque and a servo gearbox with a transmission, wherein the servo gearbox is provided for translating the drive torque, wherein the servo gearbox comprises at least two gear stages, wherein the gear stages are standard gearboxes that are coupled to each other in such a way that the servo gearbox has the transmission.

[0004] DE 10 2012 204 318 A1 discloses recirculating ball servo steering systems for vehicles for transmitting torque between an input element and a steering column lever, with two recirculating ball drives.

[0005] In DE 20 2004 021 588 U1, a commercial vehicle steering system with a steering gear (screw steering gear) is shown, which transmits steering movements initiated at the steering wheel to a steering column lever via a hydraulically assisted auxiliary power booster device, wherein an electromechanical auxiliary power booster device suitable for the majority of the vehicle operation is also provided.

[0006] DE 10 2014 117 647 A1 discloses a steering system for a motor vehicle, in particular a commercial vehicle, with a reduced, two-stage planetary gear system.

[0007] In DE 10 2015 006 084 A1 a gearbox for a drive arrangement of a working machine for driving the working machine with variably adjustable speed is described, with a first planetary gear set to which a first drive unit can be coupled, and with a second planetary gear set to which the working machine can be coupled.

[0008] DE 10 2005 005 425 A1 discloses a steering device for a motor vehicle, in particular for passenger cars, with a steering gear that converts a rotary movement of an input shaft into a sliding movement of a tie rod, and a superimposed gear with several shafts.

[0009] Furthermore, the gear law, profile shift and involute gearing are also known in the field of gear technology.

[0010] Against this background, the object of the present invention is to create an improved steering gear for an electromechanical steering system for a vehicle and an improved electromechanical steering system for a vehicle.

[0011] This problem is solved by a steering gear for an electromechanical steering system for a vehicle with the features of claim 1 and by an electromechanical steering system for a vehicle with the features of claim 7. Advantageous embodiments are set forth in the dependent claims.

[0012] According to embodiments, a servo gear unit, for example a planetary servo gear unit or an eccentric servo gear unit, can be provided for an electric power steering system with a recirculating ball gear, particularly for a power steering system of a commercial vehicle or a steering system of a commercial vehicle. In this case, for example, a recirculating ball steering gear with an electrically driven servo gear, in particular a planetary gear or planetary eccentric gear, can be arranged for an electric power steering system of a commercial vehicle. The power assistance can be enhanced, for example, by a planetary servo gear or a planetary eccentric servo gear driven by an electric motor.Such a servo gear unit, in particular a planetary servo gear or a planetary eccentric servo gear, can be connected to a spindle of a recirculating ball steering unit, which can transmit an increased electrically assisted torque to a segment shaft or output shaft of the servo steering gear.

[0013] Advantageously, according to the embodiments, the installation space requirement can be reduced compared to a conventional two-stage planetary servo gearbox with the same gear ratio. Additionally, the number of meshing or engaging components can be reduced compared to a conventional two-stage planetary gearbox. In other words, a space-saving and low-maintenance steering gearbox can be provided for an electromechanical steering system of a vehicle, particularly a commercial vehicle. Product costs can thus be reduced by using fewer gears compared to a conventional two-stage planetary gearbox.

[0014] A steering gear for an electromechanical steering system for a vehicle comprises an electric motor, a servo gearbox, and an angle gearbox for connecting a steering column of the steering system to a steering arm of the steering system, wherein the angle gearbox is a mechanically driven ball screw drive with a ball nut that engages with a segment shaft of the steering gear that can be connected to or is connected to the steering arm, wherein a spindle of the ball screw drive is continuous, wherein the spindle is connected at one side to an output shaft of the servo gearbox, and wherein the servo gearbox can be driven or is driven by the electric motor.

[0015] The vehicle can be a motor vehicle for transporting people and, additionally or alternatively, goods, in particular a commercial vehicle, such as a truck or the like. Each of the transmissions can also be referred to as a transmission unit. The servo transmission can be coupled to the electric motor. When two components are connected or coupled, there can be a positive connection and, additionally or alternatively, a frictional connection between the components.

[0016] According to one embodiment, the servo gearbox can be a planetary gearbox. In this case, the planetary gearbox can have planet gears with identical numbers of teeth and geometry. The planet gears can mesh with two independent ring gears with different numbers of teeth. The planet gears can be driven by the electric motor via a carrier. The planet gears can be mounted on the carrier, and the carrier can be driven by the electric motor. Such an embodiment offers the advantage that an electromechanical drive for the steering system can be implemented in a particularly space-saving and reliable manner, without any imbalance.

[0017] Alternatively, the servo gearbox can be an eccentric planetary gearbox. In this case, the eccentric planetary gearbox can have a common planet gear. The planet gear can mesh with two ring gears. The difference in the number of teeth between the two ring gears can be greater than or equal to 1. The planet gear can be mounted eccentrically on a carrier that can be driven or is driven by the electric motor. This design offers the advantage that an electromechanical drive can be provided for the steering system, which is particularly space-saving, reliable, and robust.

[0018] In this design, a tip of the planetary gear can be shaped with a cut-off cross-section, depending on the engagement area. Such an embodiment offers the advantage that different engagement cross-sections can be taken into account to achieve reliable torque transmission.

[0019] The planet gear can also be adjustable on a carrier to set the backlash between the planet gear and at least one of the two ring gears. More precisely, a gear stage, preferably stage 2, can be adjusted to be virtually backlash-free via the eccentric. This design offers the advantage of achieving torque transmission with minimal wear and minimal losses.

[0020] According to one embodiment, tooth sections of at least one planetary gear and additionally or alternatively of the ring gears can be designed with a profile shift. Such an embodiment offers the advantage that proper and reliable engagement or meshing of the respective gears can be achieved.

[0021] Furthermore, the ball nut of the ball screw drive can have a linear guide designed to absorb radial loads introduced by a toothed connection between the segment shaft and the ball nut. Such an embodiment offers the advantage that, through this reinforcement and additional bearing mounting to reduce radial loads that can act on the ball mechanism during operation, reliable continuous operation of the steering gear can be ensured.

[0022] The linear guide device can be designed as a plain bearing, in particular as a multi-layer plain bearing or as a plastic plain bearing. Such an embodiment offers the advantage that conventional and readily available bearing devices can be used to achieve reliable load bearing.

[0023] Alternatively, the linear guide device can be designed as a rolling bearing, in particular as a needle roller bearing or as a combination of needle roller and rolling bearings. Such an embodiment offers the advantage that conventional and readily available bearing devices can be used to achieve reliable load bearing.

[0024] An electromechanical steering system for a vehicle comprises a steering column and a steering column lever, wherein the electromechanical steering system comprises an embodiment of the aforementioned steering gear, wherein the steering column and the steering column lever are connected to each other by means of the steering gear.

[0025] In conjunction with the electromechanical steering system, an embodiment of the aforementioned steering gear can be advantageously employed or used to apply a steering torque, representing a torque from a steering input at a steering wheel, and a support torque, representing a torque provided by the electric motor and the servo gearbox, to the segment shaft via the bevel gear. The electromechanical steering system can be referred to as an electromechanical power steering system or as a power steering system with an electromechanical drive.

[0026] Examples of the approach presented here are explained in more detail in the following description with reference to the figures. These show: Fig. 1 a schematic representation of a vehicle with an electromechanical steering system according to an exemplary embodiment; Fig. 2 a schematic representation of a steering gear according to an exemplary embodiment; Fig. 3 a schematic representation of the steering gear Fig. 2; Fig. 4 a schematic representation of a section of the steering gear made of Fig. 2 or Fig. 3; Fig. 5 a schematic representation of the steering gear Fig. 2, Fig. 3 or Fig. 4; Fig. 6 a schematic representation of the steering gear Fig. 2, Fig. 3, Fig. 4 or Fig. 5; Fig. 7 a schematic representation of a steering gear according to an exemplary embodiment; Fig. 8 a schematic representation of the steering gear Fig. 7; Fig. 9 a schematic representation of the steering gear Fig. 7 or Fig. 8; Fig. 10 a schematic representation of the steering gear made of Fig. 7, Fig. 8 or Fig. 9; and Fig. 11 a schematic representation of the steering gear made of Fig. 7, Fig. 8, Fig. 9 or Fig. 10.

[0027] Fig. Figure 1 shows a schematic representation of a vehicle 100 with an electromechanical steering system 110 according to an exemplary embodiment. The vehicle 100 is a motor vehicle, in particular a commercial vehicle, such as a truck or the like. The steering system 110 has a steering column 114 and a steering column lever 116. The steering column 114 is connected to a steering wheel 112. The steering wheel 112 can also be part of the steering system 110. The steering column lever 116 is coupled to steerable wheels, for example, an axle of the vehicle 100, via suitable devices. Furthermore, the steering system 110 has a steering gear 120. The steering gear 120 is designed as an electromechanical steering gear or with an electromechanical drive. The steering column 114 and the steering column lever 116 are connected to each other by means of the steering gear 120. Fig. Figure 1 also shows a segmented shaft 122 of the steering gear 120. The segmented shaft 122 is connected to the steering column lever 116. The steering gear 120 will be discussed in more detail with reference to the following figures.

[0028] Fig. Figure 2 shows a schematic representation of a steering gear 120 according to an exemplary embodiment. The steering gear 120 is shown here in an oblique view. The steering gear 120 corresponds to or is similar to the steering gear from Fig. 1. Thus, the steering gear 120 is intended for an electromechanical steering system for a vehicle. The steering gear 120 comprises an electric motor 230, a servo gearbox 240 or a servo gearbox unit 240, and a bevel gear 250. Furthermore, the steering gear 120 comprises the segment shaft 122 and an input shaft 221. The segment shaft 122 can be coupled to or is coupled to a steering column lever of the steering system. The segment shaft 122 serves to transmit pivoting motion via the steering column lever to a steering rod of the steering system, which, for example, moves the front wheels of the vehicle in a desired direction. The input shaft 221 can be coupled to or is coupled to a steering column of the steering system.

[0029] The bevel gear 250 is designed to connect the steering column of the steering system, coupled to the input shaft 221, with the steering arm of the steering system, which is coupled to the segment shaft 122. The bevel gear 250 is a mechanically driven ball screw drive. The bevel gear 250 has a spindle 252 and a ball nut 254, which is coupled to, or engages with, the segment shaft 122 via a toothed section 256. The spindle 252 is continuous. The spindle 252 extends between the input shaft 221 and the servo drive 240. The spindle 252 is connected to the input shaft 221 at one end via a torsion bar. At the opposite end, the spindle 252 is connected to the servo drive 240, more precisely to an output shaft of the servo drive 240. The servo drive 240 can be driven or is driven by the electric motor 230. The electric motor 230 is connected to the servo gearbox 240. According to the in Fig. In the embodiment shown in Figure 2, the servo gearbox 240 is designed as a planetary servo gearbox or planetary gearbox. The servo gearbox 240 is connected between the electric motor 230 and the bevel gearbox 250.

[0030] The steering gear 120 has exemplary dimensions corresponding to an installation space of, for example, 160 millimeters by 210 millimeters by 160 millimeters.

[0031] Fig. Figure 3 shows a schematic representation of the steering gear 120. Fig. 2. In Fig. Figure 3 shows a partial sectional view of the steering gear 120. Also shown are a first ring gear 342, a second ring gear 344, a carrier 346, and one of several planet gears 348 from the servo gear 240. The servo gear 240, designed as a planetary gear or planetary servo gear, has several planet gears 348. The planet gears 348 have identical numbers of teeth and identical geometry. The first ring gear 342 and the second ring gear 344 are independent of each other. Furthermore, the first ring gear 342 and the second ring gear 344 have different numbers of teeth. The planet gears 348 mesh with the ring gears 342 and 344. The planet gears 348 are coupled to the electric motor 230 via the carrier 346 and can be driven or are driven by it.

[0032] The planetary servo gear unit or servo gear 240 according to the embodiment shown here comprises a conventional planetary gear train with two ring gears 342 and 344 with internal teeth or internal gears as central gear shafts and a carrier 346 or a carrier shaft which is driven by a torque of the electric motor 230. The carrier 346 comprises, for example, three planets or planet gears 348 arranged circumferentially. Each planet meshes with both ring gears 342 and 344 or outer gears. Resulting gear engagement forces are absorbed by planet bearings which are mounted on planet pins, whereby the forces are transmitted to the carrier 346 or planet carrier. The first ring gear 342 is attached to a housing of the steering gear 120 and therefore cannot rotate. The second ring gear 344 is directly connected to the spindle 252 by a shaft-hub connection or the like and represents the output shaft of the servo gearbox 240.

[0033] The number of teeth on the first ring gear 342 is slightly lower than that on the second ring gear 344, resulting in a positive fixed gear ratio of slightly more than 1.0. The fixed gear ratio is the characteristic ratio for planetary gear sets when the carrier shaft is stationary and one central shaft drives the other. For a given gear set configuration, this leads to a high ratio, which is determined by the Willis equation. For efficient gear contact, the gear teeth of the servo drive 240 can be designed as low-loss teeth, offering extended sliding or slippage for improved efficiency.

[0034] The first ring gear 342 can have a number of teeth z H1 of 53 H1 =53. The second ring gear 344 can have a number of teeth z H2 exhibiting 55 H2 =55. Each planetary gear 348 can have a number of teeth z P of 23 P=23. The torque of the electric motor 230 can, for example, be 20 newton meters. The efficiency η of the servo gearbox 240 can, for example, be 90.85 percent. A torque of, for example, 512 newton meters can be transmitted to the spindle 252 by the servo gearbox 240. The efficiency η of the bevel gearbox 250 can, for example, be 90 percent. A transmission ratio i BS The angle gear 250 can, for example, be 18, i BS =18. An overall translation ratio i GES It could, for example, be 495, i GES =495. The torque transmitted from the angle gear 150 to the segment shaft 122 can, for example, be 8197 Newton meters.

[0035] Fig. Figure 4 shows a schematic representation of a section of the steering gear 120. Fig. 2 or Fig. 3. In Fig. Figure 4 shows the steering gear 120 in a partial sectional view. The one in Fig. The section of the steering gear 120 shown in Figure 4 includes the electric motor 230, the servo gearbox 240 and a section of the spindle 252.

[0036] Fig. Figure 5 shows a schematic representation of the steering gear. Fig. 2, Fig. 3 or Fig. 4. In Fig. Figure 5 shows the steering gear 120 in a side view. In particular, the representation corresponds to the illustration in Fig. 5 of the illustration Fig. 2 except that the perspective differs.

[0037] Fig. Figure 6 shows a schematic representation of the steering gear. Fig. 2, Fig. 3, Fig. 4 or Fig. 5. In Fig. Figure 6 shows the steering gear 120 in a top view of the electric motor 230. In particular, the representation corresponds to Fig. 6 of the illustration Fig. 2 or Fig. 5 except that the perspective differs. Here, due to the nature of the illustration, the steering gear 120, the segment shaft 122, and the electric motor 230 are explicitly shown.

[0038] Fig. Figure 7 shows a schematic representation of a steering gear 120 according to an exemplary embodiment. The steering gear 120 is shown here in an oblique view. The steering gear 120 in Fig. 7 corresponds to the steering gear from Fig. 2 except that the servo gearbox 240 is designed as an eccentric gearbox, eccentric planetary gearbox or planetary eccentric gearbox.

[0039] The steering gear 120 has exemplary dimensions corresponding to an installation space of, for example, 180 millimeters by 235 millimeters by 180 millimeters.

[0040] Fig. Figure 8 shows a schematic representation of the steering gear 120. Fig. 7. In Fig. Figure 8 shows the steering gear 120 in a partial sectional view. The illustration in Fig. 8 resembles the representation from Fig. 3. The servo gearbox 240 also includes a first ring gear 342, a second ring gear 344, and a common planet gear 348, or a pair of planet gears. The common planet gear 348 meshes with both ring gears 342 and 344. The difference in the number of teeth between the two ring gears 342 and 344 is greater than or equal to 1. The common planet gear 348 is mounted eccentrically on a carrier that can be driven or is driven by the electric motor 230.

[0041] The servo gearbox 240, designed as a planetary eccentric servo gearbox unit or eccentric gearbox, comprises a conventional planetary gear train with two ring gears 342 and 344 or internal gears as central gear shafts and a carrier or carrier shaft driven by a torque from the electric motor 230. The carrier is directly connected to a rotor shaft of the electric machine or electric motor 230 and has a planet gear 348 that meshes with both ring gears 342 and 344. The resulting gear engagement forces are absorbed by planetary bearings mounted on a planetary pin, with the forces being transmitted to the carrier or planet carrier. The first ring gear 342 is attached to a housing of the steering gear 120 and therefore cannot rotate. The second ring gear 344 is directly connected to the spindle 252 by a shaft-hub connection and constitutes an output shaft of the servo gearbox 240.

[0042] According to one embodiment, the connection between the planetary pin and the carrier or carrier shaft is adjustable. During assembly, an eccentric connection can thus be adjusted to eliminate backlash in the gear mesh between the planetary gear 348 and one of the two ring gears 342 and 344. Backlash-free gear mesh allows changes in the direction of rotation of the servo drive 240 or the steering gear 120 without interrupting the torque.

[0043] The number of teeth on the first ring gear 342 is slightly lower than that on the second ring gear 344, resulting in a positive stationary gear ratio of slightly more than 1.0. The stationary gear ratio is the characteristic ratio for planetary gear sets when the carrier shaft is fixed and one central shaft drives the other. For a given gear set configuration, this leads to a high ratio, which is determined by the Willis equation. The number of teeth on the common planet gear 348 is chosen such that the difference in the number of teeth on the internal gears is approximately 7 or 8.

[0044] The first ring gear 342 can have a number of teeth z H1 of 28 H1 =28. The second ring gear 344 can have a number of teeth z H2 of 29 H2 =29. The common planetary gear 348 can have a number of teeth z P exhibiting 21 P=21. The torque of the electric motor 230 can, for example, be 20 Newton meters. The efficiency η of the servo gearbox 240 can, for example, be 92.85 percent. A torque of, for example, 534 Newton meters can be transmitted to the spindle 252 by the servo gearbox 240. The efficiency η of the bevel gearbox 250 can, for example, be 90 percent. A transmission ratio i BS The angle gear 250 can, for example, be 18, i BS =18. An overall translation ratio i GES It could be, for example, 522, i GES =522. A torque transmitted from the angle gear 150 to the segment shaft 122 can, for example, be 8699 Newton meters.

[0045] The tooth geometry of the planet gear 348 is identical for both gear engagements with the two ring gears 342 and 344, which simplifies the manufacturing of the planet gear 348. The gear engagement with the fixed, first ring gear 342 is located in the upper region of the teeth of the planet gear 348, and the gear engagement with the second ring gear 344, which is connected to the spindle 252 or spindle shaft, is located in the lower region of the teeth of the planet gear 348. To prevent interference, the tooth tips of the planet gear 348 in the area of ​​engagement with the second ring gear 344, which is connected to the spindle 252 and has a higher number of teeth, are turned to a smaller diameter. For efficient gear contact, the gear teeth can be designed as low-loss teeth, offering extended sliding or slippage for improved efficiency.

[0046] Fig. Figure 9 shows a schematic representation of the steering gear 120. Fig. 7 or Fig. 8. In Fig. Figure 9 shows the steering gear 120 in a partial sectional view. The illustration in Fig. 9 resembles the representation from Fig. 4. The one in Fig. The section of steering gear 120 shown in Figure 9 includes the electric motor 230, the servo gearbox 240 and a section of the spindle 252.

[0047] Fig. Figure 10 shows a schematic representation of the steering gear 120. Fig. 7, Fig. 8 or Fig. 9. In Fig. Figure 10 shows the steering gear 120 in a side view. The illustration in Fig. 10 resembles the representation from Fig. 5. In particular, the representation corresponds to Fig. 10 of the representation from Fig. 7 except that the perspective differs.

[0048] Fig. Figure 11 shows a schematic representation of the steering gear 120. Fig. 7, Fig. 8, Fig. 9 or Fig. 10. In Fig. Figure 11 shows the steering gear 120 in a top view of the electric motor 230. The illustration in Fig. 11 resembles the representation from Fig. 6. In particular, the representation in Fig. 11 of the representation from Fig. 7 or Fig. 10, with the exception that the perspective differs. Due to the nature of the illustration, the steering gear 120, the segment shaft 122, and the electric motor 230 are explicitly shown.

[0049] With reference to the figures described above, it should be noted that according to an embodiment of the steering gear 120, tooth areas of the at least one planet gear 348 and / or the ring gears 342 and 344 may also be shaped with a profile shift. REFERENCE MARK LIST 100 vehicles 110 Steering system 112 Steering wheel 114 Steering column 116 Steering column lever 120 Steering gear 122 Segment shaft 221 Input shaft 230 electric motor 240 servo gearboxes 250 angle gears 252 Spindle 254 ball nut 256 tooth section 342 first ring gear 344 second ring gear 346 carriers 348 planetary gear

Claims

[1] Steering gear (120) for an electromechanical steering system (110) for a vehicle (100), wherein the steering gear (120) comprises an electric motor (230), a servo gear (240) and an angle gear (250) for connecting a steering column (114) of the steering system (110) to a steering column lever (116) of the steering system (110), characterized bythat the angle gear (250) is a mechanically driven ball screw drive with a ball nut (254) which engages with a segment shaft (122) of the steering gear (120) which can be connected to or is connected to the steering column lever (116), wherein a spindle groove of a spindle (252) of the ball screw drive is continuous over the entire length of the spindle (252), wherein the spindle (252) is connected at one side to an output shaft of the servo gear (240), wherein the servo gear (240) can be driven or is driven by the electric motor (230), wherein the servo gear (240) is a planetary gear drive, wherein the planetary gear drive has planet gears (348) with identical number of teeth and geometry, wherein the planet gears (348) mesh with two independent ring gears (342, 344) with different numbers of teeth, wherein the planet gears (348) are driven by the electric motor via a carrier (346). (230) are powered or driven,wherein the ball nut (254) of the ball screw drive has a linear guide device designed to receive radial loads introduced by a toothing between the segment shaft (122) and the ball nut (254). [2] Steering gear (120) according to claim 1, characterized by , that the servo gear (240) is an eccentric planetary gear, wherein the eccentric planetary gear has a common planet gear (348), wherein the planet gear (348) meshes with two ring gears (342, 344), wherein a difference in the number of teeth between the two ring gears (342, 344) is greater than or equal to 1, wherein the planet gear (348) is mounted eccentrically on a carrier which can be driven or is driven by the electric motor (230). [3] Steering gear (120) according to claim 2, characterized by, that the planet gear (348) is adjustable on a carrier in order to adjust a gear backlash of a gear engagement between the planet gear (348) and at least one of the two ring gears (342, 344). [4] Steering gear (120) according to any one of the preceding claims, characterized by , that tooth areas of at least one planet gear (348) and / or the ring gears (342, 344) are shaped with a profile shift. [5] Steering gear (120) according to any one of the preceding claims, characterized by that the linear guide device is designed as a sliding bearing, in particular as a multi-layer sliding bearing or as a plastic sliding bearing. [6] Steering gear (120) according to any one of claims 1 to 4, characterized by that the linear guide device is designed as a rolling bearing, in particular as a needle bearing or as a combination of needle bearing and rolling bearing. [7] Electromechanical steering system (110) for a vehicle (100), wherein the steering system (110) comprises a steering column (114) and a steering column lever (116), characterized by a steering gear (120) according to one of the preceding claims, wherein the steering column (114) and the steering arm (116) are connected to each other by means of the steering gear (120).

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