Actuating device for brake system

Abstract

The invention relates to an actuating device (1) for a brake system (2), comprising an electric motor (21) arranged in a motor housing (20), a rotor (22) of the electric motor (21) being arranged in a rotationally fixed manner on a rotatably mounted drive shaft (23); the drive shaft (23) is coupled to the actuating element (3) by means of a transmission (29) such that the actuating element (3) can be moved by means of the electric motor (21), the transmission (29) having a planetary gear (30) with an output shaft (46), and the planetary gear (30) having an output shaft (46), the output shaft (46) being coupled to the drive shaft (23) by means of the planetary gear (30), and the output shaft (46) being coupled to the drive shaft (23) by means of the planetary gear (30). And wherein the drive shaft (23) is non-rotatably connected to at least one sun gear (33, 38), at least one ring gear (32, 37) or at least one planet carrier (34, 39) of the planetary gear (30). According to the invention, the axis of rotation (24) of the drive shaft (23) is oriented perpendicular to the axis of movement (4) of the actuating element (3).

Description

Technical Field

[0001] The present invention relates to an operating device for a braking system, the operating device having an electric motor arranged in a motor housing, wherein the rotor of the electric motor is arranged non-rotatably relative to a rotatably supported drive shaft; and the operating device also has a movably supported actuating element, wherein the drive shaft is coupled to the actuating element via a transmission device, so that the actuating element can be moved by the motor, wherein the transmission device has a planetary gear transmission mechanism with an output shaft, and wherein the drive shaft is non-rotatably connected to at least one sun gear of the planetary gear transmission mechanism, to at least one ring gear of the planetary gear transmission mechanism, or to at least one planetary gear carrier of the planetary gear transmission mechanism. Background Art

[0002] The hydraulic brake system of a motor vehicle usually has a plurality of friction brake devices. The friction brake device is effectively connected to the operating device of the brake system, so that the friction brake device can be operated by the operating device. As the degree of electrification of motor vehicles continues to increase, the operating device of the brake system is also increasingly electrified. In this regard, it is known to equip the operating device for the brake system with an electric motor arranged in a motor housing, wherein the rotor of the electric motor is arranged non-rotatably on a rotatably supported drive shaft. In order to achieve the operation of the friction brake device by the operating device, the operating device also has a movably supported actuating element. The drive shaft is coupled to the actuating element by a transmission device, so that the actuating element can be moved by the motor. Therefore, the transmission device is configured to convert the rotation of the drive shaft into a translational movement of the actuating element. Therefore, the friction brake device can be operated by the motor. It is known that a planetary gear transmission with an output shaft is used in the transmission device. The output shaft forms the output of the planetary gear transmission here, so that the planetary gear transmission can be coupled to a transmission element located downstream of the planetary gear transmission in terms of transmission technology through the output shaft. A high transmission ratio can be achieved by the planetary gear transmission. Accordingly, the planetary gear mechanism ensures that the actuating device generates little noise during operation. Typically, the drive shaft is connected to at least one sun gear of the planetary gear mechanism, to at least one ring gear of the planetary gear mechanism or to at least one planet carrier of the planetary gear mechanism in a rotationally fixed manner. The ring gear, the sun gear or the planet carrier then forms the input of the planetary gear mechanism. Summary of the invention

[0003] The operating device according to the invention having the features of claim 1 has the advantage that the operating device can be realized cost-effectively. According to the invention, for this purpose, it is provided that the rotation axis of the drive shaft is oriented perpendicularly to the displacement axis of the actuating element. By orienting the rotation axis of the drive shaft relative to the displacement axis of the actuating element in the manner according to the invention, a simple and mechanically stable coupling of the drive shaft to the actuating element can be achieved in terms of transmission technology. Preferably, the planetary gear mechanism is at least partially arranged in the motor housing. This makes it possible to easily carry the motor housing, the electric motor and the planetary gear mechanism together. The output shaft preferably extends from the motor housing. This simplifies the coupling with the transmission element located downstream. Particularly preferably, the planetary gear carrier of the planetary gear mechanism has an output shaft, so that the planetary gear carrier forms the output part of the planetary gear mechanism.

[0004] According to a preferred embodiment, the transmission has a movably supported toothed rack with a drive toothing. The toothed rack can reliably convert the rotation of the drive shaft into a translational movement of the actuating element. In addition, the use of a toothed rack can also reduce manufacturing costs. In particular, the use of a toothed rack allows the use of a rolling-only transmission type in the transmission, thereby resulting in a highly efficient transmission. Preferably, the axis of movement of the toothed rack is oriented parallel to the axis of movement of the actuating element. Preferably, the toothed rack forms the actuating element. Alternatively, the toothed rack is preferably coupled to the actuating element, so that the actuating element can be moved by the toothed rack.

[0005] According to a preferred embodiment, it is provided that the drive toothing of the toothed rack meshes with the output toothing of the output shaft of the planetary gear. In terms of transmission technology, the toothed rack is then located directly downstream of the planetary gear. This design of the actuating device has the advantage that the actuating device is compact and thus space-saving. According to an alternative embodiment, it is preferably provided that at least one further transmission element, for example a gear, is arranged between the toothed rack and the output shaft.

[0006] According to a preferred embodiment, the transmission is at least partially arranged in a housing of the operating device, and the motor housing is fixed to the housing. By arranging the transmission in the housing, the housing protects the transmission from external influences. Preferably, the actuating element is also at least partially arranged in the housing. By fixing the motor housing to the housing, the operating device is mechanically stable as a whole. Preferably, the aforementioned rack is arranged in the housing. Preferably, the output shaft of the planetary gear mechanism extends into the housing, so that the output toothing of the output shaft is arranged in the housing. In particular, the motor housing is fixed to the transmission housing by at least one fixing element, such as a screw. Preferably, the motor housing is fixed to the housing flange of the housing. As a result, on the one hand, it can be achieved that the motor housing is fixed to the housing in a particularly mechanically stable manner, for example, by the fixing element mentioned above. In addition, by fixing the motor housing to the housing flange, a fluid seal acting between the motor housing and the housing can also be provided. Preferably, the motor housing flange of the motor housing is sealed against the housing flange for this purpose.

[0007] According to a preferred embodiment, it is provided that the housing has at least one guide projection and the toothed rack is supported radially on the guide projection relative to the displacement axis of the toothed rack. The guide projection enables a stable guidance of the toothed rack. Preferably, the side of the toothed rack facing away from the drive toothing is supported radially on the guide projection. Preferably, the guide projection extends in the axial direction relative to the displacement axis of the toothed rack. Preferably, the housing has a plurality of guide projections on which the toothed rack is supported. This enables a particularly reliable guidance of the toothed rack.

[0008] According to a preferred embodiment, the output shaft of the planetary gear mechanism has a first bearing location and a second bearing location arranged spaced apart from the first bearing location, and the housing carries the bearing location of the output shaft. By carrying these two bearing locations, the position of the output shaft can be defined particularly accurately. Preferably, the output toothing of the output shaft is arranged between the two bearing locations. According to another embodiment, at least one bearing location of the output shaft is supported by the motor housing or by a bearing cover arranged on the motor housing.

[0009] Preferably, the housing is a cylindrical extruded profile. Extruded profiles can usually be manufactured cost-effectively, so that the manufacturing costs of the operating device can be further reduced by constructing the housing as an extruded profile. The element of cylindrical construction has a peripheral wall that is at least substantially closed in the circumferential direction, wherein the peripheral wall forms or surrounds an axial penetration of the cylindrical element. Correspondingly, the cylindrical extruded profile also has such a peripheral wall or housing wall and such an axial penetration, wherein the axial penetration forms the interior of the housing of the extruded profile. However, the term "cylindrical" does not mean a cross-section with a specific shape. On the contrary, the cross-section of the extruded profile can have different shapes. However, the axial penetration preferably has a cross-section that is at least substantially rectangular. The axial penetration formed in this way is particularly suitable for accommodating and guiding the rack. The extruded profile is preferably made of aluminum.

[0010] According to a preferred embodiment, it is provided that the movement axis of the actuating element is oriented perpendicularly to the cross section of the extruded profile. The shape of the cross section of the extruded profile corresponds to the opening of the extrusion tool used to produce the extruded profile. As mentioned above, the extruded profile has an axial penetration due to its cylindrical design. If the movement axis of the actuating element is oriented perpendicularly to the cross section of the extruded profile, the extruded profile is correspondingly open in the movement direction of the actuating element. This simplifies the coupling of the actuating element to another element, such as a master brake cylinder.

[0011] According to a preferred embodiment, the output shaft has an axial penetration and the drive shaft protrudes through the axial penetration. The output shaft is thus designed as a hollow shaft. Since the drive shaft protrudes through the axial penetration, the drive shaft can be supported, for example, on the side of the output shaft facing away from the rotor. Such a support of the drive shaft is particularly stable in terms of machinery.

[0012] According to a preferred embodiment, the drive shaft has a first end section protruding from the axial penetration, and the rotational speed sensor is arranged at the first end section. The first end section is easily accessible for measuring or detecting the rotational speed of the drive shaft, so it is preferred to arrange the rotational speed sensor at the first end section of the drive shaft. The rotational speed sensor is preferably pressed against the first end section.

[0013] Preferably, the first end section with the rotational speed sensor projects into the control unit of the actuating device. The control unit is preferably designed to determine the rotational speed of the drive shaft based on the sensor signal of the rotational speed sensor. Since the rotational speed sensor projects into the control unit, a signal connection of the rotational speed sensor to the control unit can be realized in a technically simple manner.

[0014] Preferably, the drive shaft is supported by the output shaft. This makes it possible to support a section of the drive shaft adjacent to the rotational speed sensor. By supporting this section, the rotational speed of the drive shaft can be detected particularly accurately. The actuating device preferably has a bearing bushing acting between the drive shaft and the output shaft. According to another embodiment, the first end section is supported by the control and / or by the housing, wherein the support by the control and / or by the housing is present as an alternative or in addition to the above-mentioned support by the output shaft.

[0015] According to a preferred embodiment, the planetary gear mechanism has at least one first planetary gear stage and a second planetary gear stage located downstream of the first planetary gear stage in terms of transmission technology, wherein the first planetary gear stage has a first ring gear, a first sun gear and a first planetary gear carrier, at least one first planetary gear is rotatably supported on the first planetary gear carrier, wherein the second planetary gear stage has a second ring gear, a second sun gear and a second planetary gear carrier, at least one second planetary gear is rotatably supported on the second planetary gear carrier, and wherein the second planetary gear carrier has an output shaft. Therefore, the planetary gear mechanism is a multi-stage structure. This allows a planetary gear mechanism with a high transmission ratio to be realized. The transmission ratio of a multi-stage planetary gear mechanism is the quotient of the rotational speed of the drive shaft of the planetary gear mechanism and the rotational speed of the output shaft.

[0016] According to a preferred embodiment, the first planetary gear carrier is arranged in a fixed manner relative to the bearing, the ring gears are connected to each other in a non-rotatable manner, the sun gears are connected to each other in a non-rotatable manner, and the quotient of the number of teeth of the first ring gear and the number of teeth of the first sun gear is different from the quotient of the number of teeth of the second ring gear and the number of teeth of the second sun gear. In the following, the quotient of the number of teeth of the first ring gear and the number of teeth of the first sun gear is also referred to as the first quotient. The quotient of the number of teeth of the second ring gear and the number of teeth of the second sun gear is also referred to as the second quotient. By designing the multi-stage planetary gear transmission mechanism in this way, a particularly high transmission ratio can be achieved. The first planetary gear carrier is arranged in a fixed manner relative to the bearing. If the element is arranged in a fixed manner relative to the bearing, the element is directly or indirectly fixed to the bearing by a rigid connection. In order to achieve a fixed arrangement relative to the bearing, the first planetary gear carrier is preferably fixed to a non-rotating bearing component of the housing, motor housing, bearing cover and / or bearing by a rigid connection. It can be seen from the fixed arrangement of the first planetary gear carrier relative to the bearing that the first planetary gear carrier does not rotate during the operation of the planetary gear transmission mechanism. Because the first planetary gear carrier does not rotate, the first ring gear and the first sun gear rotate during the operation of the planetary gear mechanism. Because the second ring gear is non-rotatably connected to the first ring gear, the second ring gear rotates together with the first ring gear during the operation of the planetary gear mechanism. This applies to the second sun gear accordingly. If the first quotient and the second quotient are the same, the second planetary gear carrier does not rotate during the operation of the planetary gear mechanism. However, because the first quotient is different from the second quotient, the second planetary gear carrier rotates during the operation of the planetary gear mechanism. The smaller the difference between the first quotient and the second quotient, the higher the speed ratio of the planetary gear mechanism is. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The present invention is explained in more detail below with reference to the accompanying drawings. The accompanying drawings show:

[0018] Figure 1 is a cross-sectional view of an operating device for a brake system;

[0019] Figure 2 is another cross-sectional view of the control device;

[0020] Figure 3 is a cross-sectional view of a transmission device of a control device;

[0021] Figure 4 is a cross-sectional view of a planetary gear transmission mechanism of the transmission; and

[0022] Figure 5 It is a schematic diagram of a planetary gear transmission mechanism. DETAILED DESCRIPTION

[0023] Figure 1The present invention shows a longitudinal section through an actuating device 1 for a brake system 2 (not shown in detail) of a motor vehicle. The actuating device 1 has a movably mounted actuating element 3 or pressure element 3, which in the present case is designed as a push rod 3. The actuating element 3 can be moved along a displacement axis 4 in a first direction 5 and in a second direction 6 opposite to the first direction 5. The displacement axis 4 coincides with the longitudinal center axis of the actuating element 3.

[0024] The actuating element 3 is at least partially arranged in a housing 7 of the operating device 1. In the present case, the housing 7 is a cylindrical extruded profile 7. In this respect, the housing 7 has a circumferentially closed circumferential wall 8 or housing wall 8. The circumferential wall 8 forms or surrounds an axial penetration 9 of the housing 7, wherein the axial penetration 9 forms a housing interior 10 of the housing 7. In the present case, the axial penetration 9 has a rectangular cross section. The actuating element 3 is arranged in the housing 7, more precisely in the housing interior 10, so that the displacement axis 4 is oriented perpendicular to the cross section of the housing 7.

[0025] The master brake cylinder 11 of the actuating device 1 is arranged fixedly on the housing 7 relative to the housing. In the present case, the master brake cylinder 11 is arranged on the first end side 12 of the peripheral wall 8. A first hydraulic piston 13 and a second hydraulic piston 14 are supported in the master brake cylinder 11 so as to be movable, that is, movable in the first direction 5 and the second direction 6. The master brake cylinder 11 has a plurality of hydraulic couplings 15, 16. If the actuating device 1 is installed in the brake system 2 as specified, the hydraulic couplings 15, 16 are fluidically connected to the slave cylinders of the friction brake device of the brake system 2. The friction brake device can then be actuated by moving the hydraulic pistons 13 and 14 in the first direction 5. The actuating element 3 is coupled to the hydraulic pistons 13 and 14 so that the hydraulic pistons 13 and 14 can be moved in the first direction 5 by the actuating element 3. Thus, the friction brake device can be actuated by moving the actuating element 3.

[0026] The housing plate 17 is also arranged fixedly relative to the housing on the housing 7. In the present case, the housing plate 17 is arranged on a second end face 18 of the circumferential wall 8 facing away from the first end face 12. The housing plate 17 at least partially closes the axial penetration 9.

[0027] The operating device 1 also has a drive unit 19. Figure 2 The design of the drive unit 19 is explained in more detail. Figure 2In this regard, a cross section of the actuating device 1 is shown. The drive unit 19 has a motor housing 20 in which an electric motor 21 is arranged. An annular rotor 22 of the electric motor 21 is arranged on a drive shaft 23 in a rotationally fixed manner, wherein the drive shaft 23 is supported rotatably about an axis of rotation. The axis of rotation 24 is oriented perpendicular to the displacement axis 4 of the actuating element 3. An annular stator 25 of the electric motor 21 is arranged fixedly on the motor housing 20 relative to the housing and radially surrounds the rotor 22 relative to the axis of rotation 24. The motor housing 20 is fixed to the housing 7. In the present case, this is achieved by fixing a motor housing flange 26 of the motor housing 20 to a housing flange 28 of the housing 7 by means of a plurality of fixing elements 27.

[0028] The drive shaft 23 is coupled to the actuating element 3 via a transmission 29, so that the actuating element 3 can be moved by the motor 21. Since the rotation axis 24 is oriented perpendicularly to the displacement axis 4, a simple coupling of the drive shaft 23 to the actuating element 3 is possible in terms of transmission technology. Figure 3 A sectional view of a transmission 29 is shown.

[0029] The transmission 29 has a planetary gear 30 . Figure 4 A sectional view of a planetary gear mechanism 30 is shown. Figure 5 2 shows a schematic diagram of a planetary gear mechanism 30. The planetary gear mechanism 30 is at least partially arranged in the motor housing 20. The planetary gear mechanism 30 has a first planetary gear stage 31. The first planetary gear stage 31 has a first ring gear 32, a first sun gear 33 and a first planetary gear carrier 34, and a plurality of first planetary gears 35 are rotatably supported on the first planetary gear carrier. The planetary gear mechanism 30 also has a second planetary gear stage 36, which is located downstream of the first planetary gear stage 31 in terms of transmission technology. The second planetary gear stage 36 is arranged on the side of the first planetary gear stage 31 facing away from the rotor 22. The second planetary gear stage 36 has a second ring gear 37, a second sun gear 38 and a second planetary gear carrier 39, and a plurality of second planetary gears 40 are rotatably supported on the second planetary gear carrier.

[0030] The first planetary gear carrier 34 has a carrier section 42 that supports the first planetary gears 40. The carrier section 42 is arranged on the side of the first planetary gears 35 that faces away from the second planetary gear stage 36. The carrier section 42 is fixed to a non-rotating bearing part 43 of a rotary bearing 44 by a rigid connection, the function of which will be explained in more detail below. Due to the fixation to the non-rotating bearing part 43, the carrier section 42 and thus the first planetary gear carrier 34 are arranged in a fixed manner relative to the bearing. Therefore, during operation of the drive unit 19, the first planetary gear carrier 34 does not rotate.

[0031] The first ring gear 32 and the second ring gear 37 are connected to each other in a non-rotatable manner. In the present case, the first ring gear 32 and the second ring gear 37 are manufactured integrally with each other. The ring gears 32 and 37 can rotate during the operation of the drive unit 19. As can be seen from the figure, the ring gears 32 and 37 are not assigned a separate rotary bearing for supporting the ring gears 32 and 37. Such a rotary bearing is not absolutely necessary. On the contrary, during the operation of the drive unit 19, the ring gears 32 and 37 are fully centered by the remaining elements of the planetary gear mechanism 30.

[0032] The first sun gear 33 and the second sun gear 38 are connected to each other in a non-rotatable manner. In the present case, the first sun gear 33 and the second sun gear 38 are manufactured integrally with each other. Here, the sun gears 33 and 38 are arranged on the drive shaft 23 in a non-rotatable manner. The sun gears 33 and 38, more precisely the drive shaft 23, respectively form the input of the planetary gear mechanism 30. According to another embodiment, it is not the sun gears 33 and 38 but the ring gears 32 and 37 that are connected to the drive shaft 23 in a non-rotatable manner.

[0033] The second planetary gear carrier 39 has a carrier section 45 that supports the second planetary gears 40. The carrier section 45 is arranged on the side of the second planetary gears 40 that faces away from the first planetary gear stage 31. The second planetary gear carrier 39 can rotate during operation of the drive unit 19. The second planetary gear carrier 39 has an output shaft 46, so that the second planetary gear carrier 39 forms the output of the planetary gear mechanism 30.

[0034] The working principle of the planetary gear mechanism 30 is explained in more detail below. The ring gears 32 and 37 and the sun gears 33 and 38 are configured so that the quotient of the number of teeth of the first ring gear 32 and the number of teeth of the first sun gear 33 is different from the quotient of the number of teeth of the second ring gear 37 and the number of teeth of the second sun gear 38. Combined with the fixed arrangement of the first planetary gear carrier 34 relative to the bearing, the non-rotatable connection of the ring gears 32 and 37, and the non-rotatable connection of the sun gears 33 and 38, this enables the planetary gear mechanism 30 to have a high speed ratio. The speed ratio of the planetary gear mechanism 30 corresponds to the difference between the aforementioned two quotients. The smaller the difference between the quotients, the greater the speed ratio of the planetary gear mechanism 30.

[0035] The speed ratio of the planetary gear transmission mechanism 30 is explained below by taking a specific example in which the number of teeth of the first ring gear 32 is 44, the number of teeth of the first sun gear 33 is 10, the number of teeth of the second ring gear 37 is 39, and the number of teeth of the second sun gear 38 is 9.

[0036] The first sun gear 33 is arranged on the drive shaft 23 in a rotationally fixed manner and outputs via the first ring gear 32 , so that the first transmission stage 31 has a transmission stage ratio of 4.4. Therefore, the first ring gear 32 rotates at the transmission ratio of 4.4.

[0037] In the second planetary gear stage 37 , the output occurs via the second planetary gear carrier 39 .

[0038] If the second sun gear 38 is driven, the gear ratio for the second planetary gear stage 36 is:

[0039] Transmission level speed ratio = 1 + 39 / 9 = 5.33

[0040] However, if the second ring gear 37 is driven, the gear ratio for the second planetary gear stage 36 is:

[0041] Transmission level speed ratio = 1 + 9 / 39 = 1.23

[0042] Since both the second ring gear 37 and the second sun gear 38 in the second planetary gear stage 36 are driven due to the design of the planetary gear 30, the following relationship holds true for the transmission ratio of the planetary gear 30:

[0043]

[0044] Therefore, the drive shaft 23 rotates 352 times when the output shaft 46 rotates once. If the quotients do not differ from each other, the second planetary carrier 39 does not rotate during the operation of the drive unit 19.

[0045] from Figure 2 It can be seen that the output shaft 46 protrudes from the motor housing 20. In addition, the output shaft 46 protrudes into the housing interior 10 through a first penetration 77 of the peripheral wall 8. In addition, the output shaft 46 protrudes from the housing 7 through a second penetration 78 of the peripheral wall 8. The output shaft 46 has a first bearing point 47 and a second bearing point 48 arranged at a distance from the first bearing point 47. The bearing points 47 and 48 are supported by the housing 7. For this purpose, the housing 7 in the present case supports a first rotary bearing 49 acting between the housing 7 and the first bearing point 47 and a second rotary bearing 50 acting between the housing 7 and the second bearing point 48. The output shaft 46 has an output toothing 51 between the bearing points 47 and 48.

[0046] The operating device 1 also has a movably mounted toothed rack 52. The toothed rack 52 can be moved in a first direction 5 and a second direction 6. The toothed rack 52 is also arranged in the housing 7, more precisely in the housing interior 10. In the present case, the toothed rack 52 is arranged such that the longitudinal center axis of the toothed rack 52 coincides with the longitudinal center axis of the actuating element 3. The toothed rack 52 is coupled to the actuating element 3 so that the actuating element 3 can be moved by the toothed rack 52.

[0047] The rack 52 has a drive toothing 53. The drive toothing 53 meshes with the output toothing 51 of the output shaft 46, so that the rack 52 can be moved by the output shaft 46. The rack 52 is thus directly operatively connected to the output shaft 46. According to another embodiment, at least one further transmission element, such as a gear, is arranged between the rack 52 and the output shaft 46.

[0048] The housing 7 has a plurality of guide projections 54 that extend into the housing interior 10. The guide projections 54 are arranged on the side of the toothed rack 52 that faces away from the output shaft 46. In the present case, the guide projections 54 are configured to have a certain length and extend in the axial direction relative to the axis of movement of the toothed rack 52. During the operation of the drive unit 19, the output shaft 46 presses the toothed rack 52 in the direction of the guide projections 54, so that the surface 55 of the toothed rack 52 that faces away from the drive tooth 53 rests radially on the guide projections 54 relative to the axis of movement of the toothed rack 52. As a result, the toothed rack 52 is radially supported on the guide projections 54 relative to the axis of movement of the toothed rack 52. Accordingly, during the operation of the drive unit 19, the toothed rack 52 is guided by the guide projections 54.

[0049] The output shaft 46 has an axial penetration 56 and is therefore configured as a hollow shaft 46. The drive shaft 23 extends through the axial penetration 56, wherein a first end section 57 extends from the axial penetration 56. A rotational speed sensor 58 is arranged at the first end section 57. In the present case, the rotational speed sensor 58 is pressed against the first end section 57. The first end section 57 carrying the rotational speed sensor 58 extends into a controller 59 of the operating device 1. The controller 59 is configured to determine the rotational speed of the drive shaft 23 based on the sensor signal of the rotational speed sensor 58 and to control the electric motor 21 based on the determined rotational speed. Since the first end section 57 extends into the controller 59 with the rotational speed sensor 58, the sensor signal of the rotational speed sensor 58 can be provided to the controller 59 in a technically simple manner.

[0050] The drive shaft 23 has a first bearing point 60 adjacent to the first end section 57. The first bearing point 60 is supported by the output shaft 46. The actuating device 1 has a bearing bushing 61 which acts between a sleeve-shaped bearing section of the output shaft 46 and the first bearing point 60 of the drive shaft 23.

[0051] The drive shaft 23 also has a second bearing location 62. The second bearing location 62 is arranged between the first planetary gear carrier 34 and the rotor 22. The second bearing location 62 is carried by a bearing cover 63, which is arranged on the motor housing 20 in a fixed manner relative to the housing. The bearing cover 63 carries the aforementioned rotary bearing 44. As described above, the first planetary gear carrier 34 is arranged in a fixed manner relative to the bearing by being fixed to the non-rotating bearing part 43 of the rotary bearing 44. According to another embodiment, the planetary gear carrier 34 is arranged in a fixed manner relative to the bearing, for example by being fixed to the bearing cover 63.

[0052] The drive shaft 23 also has a third bearing point 64. The third bearing point 64 is arranged on the side of the rotor 22 facing away from the first planetary carrier 34. The third bearing point 64 is supported by the bottom 65 of the motor housing 20. In the present case, the bottom 65 carries a rotary bearing 66 for this purpose, which acts between the bottom 65 and the third bearing point 64.

[0053] The operating device 1 further comprises an operating element 67, which is movably supported in an axial penetration 68 of the rack 52. A first end 69 of the operating element 67 can be coupled to or with a brake pedal of the brake system 2 via an input rod 70, so that the operating element 67 can be moved by operating the brake pedal. A second end 71 of the operating element 67 is coupled to the actuating element 3, so that the actuating element 3 can be moved by the operating element 67. Therefore, the friction brake device can also be actuated by operating the brake pedal.

[0054] from Figure 1 and Figure 2 It can be seen that the actuating element 67 has a radial projection 72 which engages in a radial recess 74 of the toothed rack 52 to form a rotational lock 73 . In the present case, the radial recess 74 is designed as a radial penetration 74 .

Claims

1. An operating device for a brake system, the operating device having an electric motor (21) arranged in a motor housing (20), wherein: The rotor (22) of the electric motor (21) is non-rotatably arranged on a rotatably supported drive shaft (23), and the operating device also has a movably supported actuating element (3), wherein the drive shaft (23) is coupled to the actuating element (3) via a transmission device (29), so that the actuating element (3) can be moved by the electric motor (21), wherein the transmission device (29) has a planetary gear transmission (30) with an output shaft (46), and wherein the drive shaft (23) is non-rotatably connected to at least one sun gear (33, 38) of the planetary gear transmission (30), to at least one ring gear (32, 37) of the planetary gear transmission (30), or to at least one planetary gear carrier (34, 39) of the planetary gear transmission (30), characterized in that the rotation axis (24) of the drive shaft (23) is oriented perpendicular to the movement axis (4) of the actuating element (3).

2. The operating device according to claim 1, characterized in that The transmission (29) has a movably mounted toothed rack (52) which has a drive toothing (53).

3. The operating device according to claim 2, characterized in that The driving tooth portion (53) of the rack (52) meshes with the output tooth portion (51) of the output shaft (46) of the planetary gear transmission mechanism (30).

4. An operating device according to any one of the preceding claims, characterized in that The transmission device (29) is at least partially arranged in a housing (7) of the operating device (1), and the motor housing (20) is fastened to the housing (7), in particular via at least one fastening element (17).

5. The operating device according to claim 4, characterized in that The housing (7) has at least one guide projection (54), and the toothed rack (52) is radially supported on the guide projection (54).

6. The operating device according to any one of claims 4 and 5, characterized in that The output shaft (46) of the planetary gear mechanism (30) has a first bearing point (47) and a second bearing point (48) arranged spaced apart from the first bearing point (47), and the housing (7) carries the bearing points (47, 48) of the output shaft (46).

7. The operating device according to any one of claims 4 to 6, characterized in that The housing (7) is a cylindrical extruded profile (7).

8. The operating device according to claim 7, characterized in that The movement axis (4) of the actuating element (3) is oriented perpendicularly to the cross section of the extruded profile (7).

9. An operating device according to any one of the preceding claims, characterized in that The output shaft (46) has an axial penetration portion (56), and the drive shaft (23) protrudes through the axial penetration portion (56).

10. The operating device according to claim 9, characterized in that The drive shaft (23) has a first end section (57) which projects from the axial passage (56), and a rotational speed sensor (58) is arranged at the first end section (57).

11. The operating device according to claim 10, characterized in that The first end section (57) with the rotational speed sensor (58) projects into a control unit (59) of the operating device (1).

12. The operating device according to any one of claims 9 to 11, characterized in that The drive shaft (23) is supported by the output shaft (46).

13. An operating device according to any one of the preceding claims, characterized in that The planetary gear transmission (30) has at least one first planetary gear stage (31) and a second planetary gear stage (36) which is located downstream of the first planetary gear stage (31) in terms of transmission technology, wherein the first planetary gear stage (31) has a first ring gear (32), a first sun gear (33) and a first planetary gear carrier (34), at least one first planetary gear (35) is rotatably supported on the first planetary gear carrier, wherein the second planetary gear stage (36) has a second ring gear (37), a second sun gear (38) and a second planetary gear carrier (39), at least one second planetary gear (40) is rotatably supported on the second planetary gear carrier, and wherein the second planetary gear carrier (39) has the output shaft (46).

14. The operating device according to claim 13, characterized in that The first planetary gear carrier (34) is arranged in a fixed manner relative to the bearing, and the ring gears (32, 37) are non-rotatably connected to each other, so that the sun gears (33, 38) are non-rotatably connected to each other, and the quotient of the number of teeth of the first ring gear (32) and the number of teeth of the first sun gear (33) is different from the quotient of the number of teeth of the second ring gear (33) and the number of teeth of the second sun gear (38).

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