Operating device for a braking system

Abstract

The present invention relates to an electromechanical machine (21) arranged within a motor housing (20), the electromechanical machine (21) having a drive shaft (23) on which a rotor (22) of the electromechanical machine (21) is rotatably supported and being arranged non-rotatably relative thereto, and an actuator element (3) supported displaceably, the drive shaft (23) being connected to the actuator element (3) by a transmission (29) such that the actuator element (3) is displaceable by the electromechanical machine (21), the transmission (29) having an epicyclic gear mechanism (30) with a driven shaft (46), the drive shaft (46) being non-rotatably coupled to at least one sun gear (33, 38) of the epicyclic gear mechanism (30), at least one internal gear (32, 37) of the epicyclic gear mechanism (30), or at least one planet gear carrier (34, 39) of the epicyclic gear mechanism (30), and relates to an operating device (1) for a brake system (2). 【Solution means】 It is considered that the axis of rotation (24) of the drive shaft (23) is oriented perpendicular to the displacement axis (4) of the actuator element (3).

Description

Technical Field

[0001] The present invention relates to an electromechanical machine disposed within a motor housing, the electromechanical machine having a drive shaft on which a rotor of the electromechanical machine is rotatably supported and on which an actuator element is non-rotatably disposed relative to the drive shaft, the actuator element being displaceably supported, and a transmission device coupling the drive shaft to the actuator element such that the actuator element is displaceable by the electromechanical machine. The transmission device has a planetary gear mechanism including a driven shaft, and the drive shaft is non-rotatably coupled to at least one sun gear of the planetary gear mechanism, at least one internal gear of the planetary gear mechanism, or at least one planetary gear carrier of the planetary gear mechanism, and relates to an operating device for a brake system.

Background Art

[0002] Automotive hydraulic brake systems typically have multiple friction brake devices. The friction brake devices are operatively coupled to an operating device such that the friction brake devices can be operated by the operating device of the brake system. As the electrification of automobiles increases, the electrification of the operating devices of brake systems is also increasing. In this regard, it is known to provide an operating device for a brake system with an electromechanical machine arranged in a motor housing, where the rotor of the electromechanical machine is non-rotatably arranged on a drive shaft that is rotatably supported. To enable the operation of the friction brake devices by the operating device, the operating device further has an actuator element that is displaceably supported. The drive shaft is connected to the actuator element by a transmission such that the actuator element can be displaced by the electromechanical machine. That is, the transmission is formed to convert the rotation of the drive shaft into a translational movement of the actuator element. That is, the friction brake devices can be operated by the electromechanical machine. In this case, it is known to use an epicyclic gear mechanism with a driven shaft in the transmission. The driven shaft forms the output of the epicyclic gear mechanism, and as a result, the epicyclic gear mechanism can be connected by the driven shaft to a transmission element that is connected downstream of the epicyclic gear mechanism in terms of transmission technology. A high transmission ratio can be achieved by the epicyclic gear mechanism. Correspondingly, less noise generation in the operating device during operation is achieved by the epicyclic gear mechanism. Typically, the drive shaft is non-rotatably coupled to at least one sun gear of the epicyclic gear mechanism, at least one internal gear of the epicyclic gear mechanism, or at least one planet gear carrier of the epicyclic gear mechanism. At this time, the internal gear, the sun gear, or the planet gear carrier forms the input of the epicyclic gear mechanism. SUMMARY OF THE INVENTION

[0003] The operating device according to the present invention having the configuration of claim 1 has the advantage that the operating device can be realized favorably in terms of cost. For this reason, according to the present invention, it is considered that the rotational axis of the drive shaft is oriented perpendicular to the displacement axis of the actuator element. By orienting the rotational axis of the drive shaft relative to the displacement axis of the actuator element according to the present invention, a connection between the drive shaft and the actuator element that is simple in terms of transmission technology and mechanically robust can be achieved. Preferably, the planetary gear mechanism is at least partially arranged within the motor housing. For this reason, the motor housing, the electromechanical machine, and the planetary gear mechanism can be easily operable together. Preferably, the driven shaft projects from the motor housing. This simplifies the connection with the transmission elements connected downstream. Particularly advantageously, the planetary gear carrier of the planetary gear mechanism has the driven shaft, and as a result, the planetary gear carrier forms the output part of the planetary gear mechanism.

[0004] According to an advantageous embodiment, it is considered that the transmission device has a rack provided with a drive tooth part that is supported displaceably. By means of the rack, it is reliably possible to convert the rotation of the drive shaft into a translational movement of the actuator element. In addition, by using the rack, the manufacturing cost is reduced. In particular, the use of the rack enables the use of only a rolling-type transmission device, whereby a highly efficient transmission device is obtained. Preferably, the displacement axis of the rack is oriented parallel to the displacement axis of the actuator element. Preferably, the rack forms the actuator element. Alternatively, preferably, the rack is connected to the actuator element such that the actuator element is displaceable by the rack.

[0005] According to an advantageous embodiment, it is considered that the drive toothed portion of the rack meshes with the driven toothed portion of the driven shaft of the planetary gear mechanism. That is, the rack is transmission-technologically directly connected to the downstream side of the planetary gear mechanism. This embodiment of the operating device has the advantage that the operating device is formed compactly and thus formed with reduced structural space. According to an alternative embodiment, preferably, it is considered that at least one further transmission element, such as a gear, is arranged between the rack and the driven shaft.

[0006] According to an advantageous embodiment, it is considered that the transmission is at least partially arranged within the housing of the operating device and that the motor housing is fixed to the housing. By arranging the transmission within the housing, the transmission is protected by the housing from external influences. Preferably, the actuator element is also at least partially arranged within the housing. By fixing the motor housing to the housing, the operating device is formed mechanically robust as a whole. Preferably, the aforementioned rack is arranged within the housing. Preferably, the driven shaft of the planetary gear mechanism projects into the housing such that the driven toothed portion of the driven shaft is arranged within the housing. In particular, the motor housing is fixed to the transmission housing by at least one fixing means, such as a screw. Preferably, the motor housing is fixed to the housing flange of the housing. Thereby, on the one hand, a mechanically particularly robust fixing of the motor housing at the housing can be achieved, for example, by the aforementioned fixing means. 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. For this purpose, preferably, the motor housing flange of the motor housing abuts against the housing flange for sealing.

[0007] According to an advantageous embodiment, it is considered that the housing has at least one guide projection and the rack is supported radially by the guide projection with respect to the displacement axis of the rack. The stable guidance of the rack is achieved by the guide projection. Preferably, the side of the rack opposite to the drive tooth portion is supported radially by the guide projection. Preferably, the guide projection extends axially with respect to the displacement axis of the rack. Preferably, the housing has a plurality of guide projections, and the rack is supported by these guide projections. Thereby, particularly stable guidance of the rack is achieved.

[0008] According to an advantageous embodiment, it is considered that the driven shaft of the planetary gear mechanism has a first support portion and a second support portion arranged at a distance from the first support portion, and the housing supports these support portions of the driven shaft. By supporting both support portions, the position of the driven shaft can be determined particularly precisely. Preferably, the driven tooth portion of the driven shaft is arranged between both support portions. According to another embodiment, at least one of these support portions of the driven shaft is supported by the motor housing or by a support shield arranged in the motor housing.

[0009] Preferably, the housing is a tubular extrusion profile. Extrusion profiles are typically preferably manufacturable in terms of cost, and as a result, by forming the housing as an extrusion profile, the manufacturing cost for the operating device is further reduced. The element formed in a tubular shape has at least substantially closed side walls in the circumferential direction, in which case the side walls form or surround the axial through portion of the tubular element. Correspondingly, the tubular extrusion profile also has this type of side wall or housing wall, and this type of axial through portion, in which case the axial through portion forms the interior of the housing of the extrusion profile. However, the expression "tubular" does not imply a cross-section with a specific shape. Rather, the cross-section of the extrusion profile may have various shapes. However, preferably, the axial through portion has at least substantially a rectangular cross-section. The axially through portion formed in this way is particularly suitable for receiving and guiding the rack. Preferably, the extrusion profile is made of aluminum.

[0010] According to an advantageous embodiment, it is considered that the displacement axis of the actuator element is oriented perpendicular to the cross-section of the extrusion profile. The cross-section of the extrusion profile is a surface having a shape corresponding to the opening of the extrusion die used for the manufacture of the extrusion profile. As described above, the extrusion profile has an axial through portion due to its tubular configuration. If the displacement axis of the actuator element is oriented perpendicular to the cross-section of the extrusion profile, the extrusion profile correspondingly opens in the displacement direction of the actuator element. This simplifies the connection between the actuator element and other elements such as, for example, a brake master cylinder.

[0011] According to an advantageous embodiment, it is considered that the driven shaft has an axially penetrating portion and the drive shaft penetrates through the axially penetrating portion and protrudes. That is, the driven shaft is formed as a hollow shaft. Since the drive shaft penetrates through the axially penetrating portion and protrudes, for example, on the side of the driven shaft opposite to the rotor, the drive shaft can be supported. Such support of the drive shaft is mechanically particularly robust.

[0012] According to an advantageous embodiment, it is considered that the drive shaft has a first end portion protruding from the axially penetrating portion and a rotational speed sensor is arranged on the first end portion. The first end portion is easily accessible for measuring or detecting the rotational speed of the drive shaft, and as a result, it is advantageous to arrange the rotational speed sensor on the first end portion of the drive shaft. Preferably, the rotational speed sensor is press-fitted and mounted on the first end portion.

[0013] Preferably, the first end portion having the rotational speed sensor protrudes into the controller of the operating device. Preferably, the controller is formed to detect the rotational speed of the drive shaft depending on the sensor signal of the rotational speed sensor. Since the rotational speed sensor protrudes into the controller, the signal technical connection of the rotational speed sensor to the controller can be technically easily realized.

[0014] Preferably, the drive shaft is supported by the driven shaft. Thereby, the support of the portion of the drive shaft adjacent to the rotational speed sensor can be achieved. By supporting this portion, particularly precise detection of the rotational speed of the drive shaft becomes possible. Preferably, the operating device has a bearing bush acting between the drive shaft and the driven shaft. According to other embodiments, the first end portion is supported by the controller and / or the housing, and in this case, the support by the controller and / or the housing is provided alternatively or additionally to the aforementioned support by the driven shaft.

[0015] According to an advantageous embodiment, the planetary gear mechanism has at least a first planetary stage and a second planetary stage which is connected downstream of the first planetary stage in terms of transmission technology. In this case, the first planetary stage has a first internal gear, a first sun gear, and a first planetary gear carrier, and at least one first planetary gear is rotatably supported on the first planetary gear carrier. The second planetary stage has a second internal gear, a second sun gear, and a second planetary gear carrier, and at least one second planetary gear is rotatably supported on the second planetary gear carrier. It is considered that the second planetary gear carrier has a driven shaft. That is, the planetary gear mechanism is formed in multiple stages. Thereby, a planetary gear mechanism with a high transmission gear ratio can be realized. The transmission gear ratio of the 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 driven shaft.

[0016] According to an advantageous embodiment, it is considered that the first planetary gear carrier is arranged in a supported and fixed manner, the internal gears are non-rotatably coupled to each other, the sun gears are non-rotatably coupled to each other, and the quotient of the number of teeth of the first internal gear and the number of teeth of the first sun gear is different from the quotient of the number of teeth of the second internal gear and the number of teeth of the second sun gear. Hereinafter, the quotient of the number of teeth of the first internal 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 internal gear and the number of teeth of the second sun gear is also referred to as the second quotient. By implementing the multi-stage planetary gear mechanism in this way, a particularly high transmission gear ratio can be achieved. The first planetary gear carrier is arranged in a supported and fixed manner. If a certain component is arranged in a supported and fixed manner, this component is fixed to the bearing directly or indirectly by a firm connection. The first planetary gear carrier is preferably fixed to the housing, the motor housing, the support shield, and / or the bearing portion for fixing the position of the bearing by a firm connection for the supported and fixed arrangement. As a result of arranging the first planetary gear carrier in a supported and fixed manner, the first planetary gear carrier does not rotate during the operation of the planetary gear mechanism. Since the first planetary gear carrier does not rotate, the first internal gear and the first sun gear rotate during the operation of the planetary gear mechanism. Since the second internal gear is non-rotatably coupled to the first internal gear, the second internal gear rotates together with the first internal gear during the operation of the planetary gear mechanism. This also applies to the second sun gear correspondingly. If the first quotient and the second quotient are the same, the second planetary gear carrier will not rotate during the operation of the planetary gear mechanism. However, since the first quotient is different from the second quotient, it is achieved that the second planetary gear carrier rotates during the operation of the planetary gear mechanism. At this time, the smaller the difference between the first quotient and the second quotient, the larger the transmission gear ratio of the planetary gear mechanism.

[0017] Next, the present invention will be described in more detail based on the drawings.

Brief Description of the Drawings

[0018]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Mode for Carrying Out the Invention

[0019] FIG. 1 is a cross-sectional view of an operating device 1 for an automobile brake system 2 not shown in detail. The operating device 1 has an actuator element 3 or a pressure element 3 that is displaceably supported and is formed as a pressure rod 3 in the present embodiment. The actuator element 3 is displaceable in a first direction 5 along a displacement axis 4 and in a second direction 6 opposite to the first direction 5. The displacement axis 4 corresponds to the longitudinal central axis of the actuator element 3.

[0020] The actuator element 3 is at least partially arranged within a housing 7 of the operating device 1. In the present embodiment, the housing 7 is a cylindrical extrusion profile 7. To this extent, the housing 7 has side walls 8 or housing walls 8 that are closed in the circumferential direction. The side walls 8 form or surround an axially penetrating portion 9 of the housing 7, and in this case, the axially penetrating portion 9 forms the housing interior 10 of the housing 7. In the present embodiment, the axially penetrating portion 9 has a rectangular cross-section. The actuator element 3 is arranged within the housing 7 or within the housing interior 10 such that the displacement axis 4 is directed perpendicular to the cross-section of the housing 7.

[0021] In the housing 7, the brake master cylinder 11 of the operating device 1 is fixedly arranged in the housing. In the present embodiment, the brake master cylinder 11 is arranged on the first end face 12 of the side wall 8. In the brake master cylinder 11, a first hydraulic piston 13 and a second hydraulic piston 14 are supported so as to be displaceable, that is, supported so as to be displaceable in the first direction 5 and the second direction 6. The brake master cylinder 11 has a plurality of hydraulic connection parts 15, 16. If the operating device 1 is installed in the brake system 2 as specified, the hydraulic connection parts 15, 16 are fluid-technologically connected to the slave cylinder of the friction brake device of the brake system 2. At this time, the friction brake device can be operated by the displacement of the hydraulic pistons 13 and 14 in the first direction 5. The actuator element 3 is connected to the hydraulic pistons 13 and 14 such that the hydraulic pistons 13 and 14 can be displaced in the first direction 5 by the actuator element 3. That is, the friction brake device can be operated by the displacement of the actuator element 3.

[0022] Furthermore, a housing plate 17 is fixedly arranged in the housing 7. In the present embodiment, the housing plate 17 is arranged on the second end face 18 of the side wall 8, which is opposite to the first end face 12. The housing plate 17 at least partially closes the axially penetrating portion 9.

[0023] The operating device 1 further has a drive unit 19. Next, with reference to FIG. 2, an embodiment of the drive unit 19 will be described in detail. For this purpose, FIG. 2 shows a cross-section of the operating device 1. The drive unit 19 has a motor housing 20, and an electromechanical machine 21 is arranged in the motor housing. The ring-shaped rotor 22 of the electromechanical machine 21 is arranged non-rotatably relative to the drive shaft 23, and in this case, the drive shaft 23 is rotatably supported about the axis of rotation 24. The axis of rotation 24 is oriented perpendicular to the displacement axis 4 of the actuator element 3. The ring-shaped stator 25 of the electromechanical machine 21 is arranged in the motor housing 20 in a housing-fixed manner and surrounds the rotor 22 radially with respect to the axis of rotation 24. The motor housing 20 is fixed to the housing 7. In the present embodiment, thereby, it is achieved that the motor housing flange 26 of the motor housing 20 is fixed to the housing flange 28 of the housing 7 by a plurality of fixing means 27.

[0024] The drive shaft 23 is connected to the actuator element 3 by a transmission 29 such that the actuator element 3 can be displaced by the electromechanical machine 21. Since the axis of rotation 24 is oriented perpendicular to the displacement axis 4, a technically simple connection between the drive shaft 23 and the actuator element 3 becomes possible. FIG. 3 is a cross-sectional view of the transmission 29.

[0025] The transmission device 29 has a planetary gear mechanism 30. FIG. 4 is a cross-sectional view of the planetary gear mechanism 30. FIG. 5 is a schematic view of the planetary gear mechanism 30. The planetary gear mechanism 30 is at least partially disposed within the motor housing 20. The planetary gear mechanism 30 has a first planetary stage 31. The first planetary stage 31 has a first internal 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 by the first planetary gear carrier. The planetary gear mechanism 30 further has a second planetary stage 36 that is connected downstream of the first planetary stage 31 in terms of transmission technology. The second planetary stage 36 is disposed on the side of the first planetary stage 31 opposite to the rotor 22. The second planetary stage 36 has a second internal 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 by the second planetary gear carrier.

[0026] The first planetary gear carrier 34 has a carrier portion 42 that carries the first planetary gear 40. The carrier portion 42 is disposed on the side of the first planetary gear 35 opposite to the second planetary stage 36. The carrier portion 42 is fixed to the position-fixing support portion 43 of the pivot bearing 44 by a strong coupling portion, and the function of the pivot bearing will be described in more detail later. The carrier portion 42, and thus the first planetary gear carrier 34, is supported and fixed by being fixed to the position-fixing support portion 43. Therefore, during the operation of the drive unit 19, the first planetary gear carrier 34 does not rotate.

[0027] The first internal gear 32 and the second internal gear 37 are coupled to each other so as not to be relatively rotatable. In the present embodiment, the first internal gear 32 and the second internal gear 37 are integrally formed with each other. The internal gears 32 and 37 are rotatable during the operation of the drive unit 19. However, as can be seen from a plurality of figures, no special pivot bearings for supporting these internal gears 32 and 37 are attached to the internal gears 32 and 37. Such a pivot bearing is not necessarily required. Rather, sufficient centering of the internal gears 32 and 37 is achieved by other components of the planetary gear mechanism 30 during the operation of the drive unit 19.

[0028] The first sun gear 33 and the second sun gear 38 are coupled to each other in a non-rotatable manner. In the present embodiment, the first sun gear 33 and the second sun gear 38 are integrally formed with each other. At this time, the sun gears 33 and 38 are disposed on the drive shaft 23 in a non-rotatable manner. Correspondingly, the sun gears 33 and 38 or the drive shaft 23 form an input portion of the planetary gear mechanism 30. According to another embodiment, instead of the sun gears 33 and 38, the internal gears 32 and 37 are coupled to the drive shaft 23 in a non-rotatable manner.

[0029] The second planetary gear carrier 39 has a carrier portion 45 that carries the second planetary gear 40. The carrier portion 45 is disposed on the side of the second planetary gear 40 opposite to the first planetary stage 31. The second planetary gear carrier 39 is rotatable during the operation of the drive unit 19. The second planetary gear carrier 39 has a driven shaft 46, and as a result, the second planetary gear carrier 39 forms an output portion of the planetary gear mechanism 30.

[0030] Next, the functional mode of the planetary gear mechanism 30 will be described in detail. The internal gears 32 and 37 and the sun gears 33 and 38 are formed such that the quotient of the number of teeth of the first internal 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 internal gear 37 and the number of teeth of the second sun gear 38. For this reason, in the combination of the support and fixation arrangement of the first planetary gear carrier 34, the non-rotatable coupling of the internal gears 32 and 37, and the non-rotatable coupling of the sun gears 33 and 38, the planetary gear mechanism 30 has a high transmission gear ratio. At this time, the transmission gear ratio of the planetary gear mechanism 30 corresponds to the difference between the above-described two quotients. The smaller the difference between these quotients, the larger the transmission gear ratio of the planetary gear mechanism 30.

[0031] Next, a specific example of the transmission gear ratio of the planetary gear mechanism 30 will be given. In this specific example, the first internal gear 32 has 44 teeth, the first sun gear 33 has 10 teeth, the second internal gear 37 has 39 teeth, and the second sun gear 38 has 9 teeth.

[0032] The first sun gear 33 is disposed on the drive shaft 23 so as not to be relatively rotatable, and is driven via the first internal gear 32. As a result, the first transmission stage 31 has a transmission gear ratio of 4.4. That is, the first internal gear 32 rotates at a gear ratio of 4.4.

[0033] In the second planetary stage 37, the driven operation is performed via the second planetary gear carrier 39.

[0034] When the second sun gear 38 is driven, with respect to the transmission gear ratio of the second planetary stage 36, Transmission gear ratio = 1 + 39 / 9 = 5.33 is applied.

[0035] However, when the second internal gear 37 is driven, with respect to the transmission gear ratio of the second planetary stage 36, Transmission gear ratio = 1 + 9 / 39 = 1.23 is applied.

[0036] Since the planetary gear mechanism 30 is formed within the second planetary stage 36, both the second internal gear 37 and the second sun gear 38 are driven. Therefore, the following relationship is applied to the transmission gear ratio of the planetary gear mechanism 30.

[0037]

Number

[0038] That is, when the driven shaft 46 rotates exactly one full rotation, the number of full rotations of the drive shaft 23 is approximately 352 rotations. If the plurality of quotients are not different from each other, it is considered that the second planetary gear carrier 39 does not rotate during the operation of the drive unit 19.

[0039] As is apparent from FIG. 2, the driven shaft 46 protrudes from the motor housing 20. In addition, the driven shaft 46 passes through the first through portion 77 of the side wall 8 and protrudes into the housing interior 10. Further, the driven shaft 46 passes through the second through portion 78 of the side wall 8 and protrudes from the housing 7. The driven shaft 46 has a first support portion 47 and a second support portion 48 that is spaced apart from the first support portion 47. The support portions 47 and 48 are supported by the housing 7. For this reason, in the present embodiment, the housing 7 carries a first pivot bearing 49 that acts between the housing 7 and the first support portion 47 and a second pivot bearing 50 that acts between the housing 7 and the second support portion 48. Between the support portions 47 and 48, the driven shaft 46 has a driven tooth portion 51.

[0040] The operating device 1 further has a rack 52 that is supported so as to be displaceable. The rack 52 is displaceable in a first direction 5 and a second direction 6. The rack 52 is also disposed within the housing 7 or the housing interior 10. In the present embodiment, the rack 52 is disposed such that the longitudinal central axis of the rack 52 corresponds to the longitudinal central axis of the actuator element 3. The rack 52 is connected to the actuator element 3 such that the actuator element 3 is displaceable by the rack 52.

[0041] The rack 52 has a drive tooth portion 53. The drive tooth portion 53 meshes with the driven tooth portion 51 of the driven shaft 46 such that the rack 52 is displaceable by the driven shaft 46. That is, the rack 52 is directly operatively coupled to the driven shaft 46. According to a further embodiment, at least one additional transmission element, such as a gear, is disposed between the rack 52 and the driven shaft 46.

[0042] The housing 7 has a plurality of guide protrusions 54 protruding into the interior 10 of the housing. The guide protrusions 54 are arranged on the side of the rack 52 opposite to the driven shaft 46. In the present embodiment, the guide protrusions 54 are formed in a vertically long shape and extend in the axial direction with respect to the displacement axis of the rack 52. During the operation of the drive unit 19, the driven shaft 46 pushes the rack 52 in the direction of the guide protrusions 54. As a result, the surface 55 of the rack 52 on the side opposite to the drive tooth portion 53 contacts the guide protrusions 54 in the radial direction with respect to the displacement axis of the rack 52. The rack 52 is supported by the guide protrusions 54, that is, supported in the radial direction with respect to the displacement axis of the rack 52. Correspondingly, the rack 52 is guided by the guide protrusions 54 during the operation of the drive unit 19.

[0043] The driven shaft 46 has an axially penetrating portion 56 and is formed as a hollow shaft 46 to that extent. The drive shaft 23 penetrates and protrudes through the axially penetrating portion 56. In this case, a first end portion 57 protrudes from the axially penetrating portion 56. A rotation speed sensor 58 is arranged on the first end portion 57. In the present embodiment, the rotation speed sensor 58 is attached by being pressed onto the first end portion 57. The first end portion 57 carrying the rotation speed sensor 58 protrudes into the controller 59 of the operating device 1. The controller 59 is formed to detect the rotation speed of the drive shaft 23 depending on the sensor signal of the rotation speed sensor 58 and to control the electromechanical device 21 depending on the detected rotation speed. Since the first end portion 57 protrudes into the controller 59 together with the rotation speed sensor 58, the sensor signal of the rotation speed sensor 58 can be technically easily supplied to the controller 59.

[0044] The drive shaft 23 has a first support portion 60 bordering on the first end portion 57. The first support portion 60 is supported by the driven shaft 46. The operating device 1 has a bearing bush 61 acting between the sleeve-shaped support portion of the driven shaft 46 and the first support portion 60 of the drive shaft 23.

[0045] The drive shaft 23 further has a second support portion 62. The second support portion 62 is disposed between the first planetary gear carrier 34 and the rotor 22. The second support portion 62 is supported by a support shield 63 that is fixedly disposed to the housing with respect to the motor housing 20. The support shield 63 carries the pivot bearing 44 described above. As described above, the first planetary gear carrier 34 is supported and fixed by being fixed to the support portion 43 that fixes the position of the pivot bearing 44. According to another embodiment, the planetary gear carrier 34 is supported and fixed, for example, by being fixed to the support shield 63.

[0046] The drive shaft 23 further has a third support portion 64. The third support portion 64 is disposed on the side of the rotor 22 opposite to the first planetary gear carrier 34. The third support portion 64 is supported by the bottom portion 65 of the motor housing 20. For this reason, in the present embodiment, the bottom portion 65 carries a pivot bearing 66 that acts between the bottom portion 65 and the third support portion 64.

[0047] The operating device 1 further has an operating element 67 that is displaceably supported within the axial through portion 68 of the rack 52. The first end portion 69 of the operating element 67 can be connected or is connected to the brake pedal of the brake system 2 by an input rod 70, and as a result, at this time, the operating element 67 can be displaced by the operation of the brake pedal. The second end portion 71 of the operating element 67 is connected to the actuator element 3 such that the actuator element 3 can be displaced by the operating element 67. That is, the brake friction device can also be operated by the operation of the brake pedal.

[0048] As is clear from FIGS. 1 and 2, the operating element 66 has a radial protrusion 72 that engages with the radial hole 74 of the rack 52 for the formation of the twist prevention portion 73. In the present embodiment, the radial hole 74 is formed as a radial through portion 74.

Explanation of Reference Numerals

[0049] 1 Operating device 2 Brake system 3 Actuator element 4 Displacement axis of the actuator element 7 Housing of the operating device or extrusion profile 17 Housing plate (fixing means) 20 Motor housing 21 Electromechanical device 22 Rotor 23 Drive shaft 24 Axis of rotation of the drive shaft 29 Transmission 30 Planetary gear mechanism 31 First planetary stage 32 First internal gear 33 First sun gear 34 First planetary gear carrier 35 First planetary gear 36 Second planetary stage 37 Second internal gear 38 Second sun gear 39 Second planetary gear carrier 40 Second planetary gear 46 Driven shaft 47 First support part of the driven shaft 48 Second support part of the driven shaft 51 Driven tooth part of the driven shaft 52 Rack 53 Driving tooth part of the rack 54 Guide projection of the housing 56 Axial through-hole of the driven shaft 57 First end part of the drive shaft 58 Rotational speed sensor 59 Controller

Claims

1. An electromechanical device (21) disposed within a motor housing (20), the rotor (22) of the electromechanical device (21) being non-rotatably disposed on a drive shaft (23) rotatably supported, and an actuator element (3) supported displaceably, the drive shaft (23) being connected to the actuator element (3) by a transmission (29) such that the actuator element (3) is displaceable by the electromechanical device (21). The transmission (29) has a planetary gear mechanism (30) with a driven shaft (46). The driven shaft (46) is non-rotatably coupled to at least one sun gear (33, 38) of the planetary gear mechanism (30), at least one internal gear (32, 37) of the planetary gear mechanism (30), or at least one planetary gear carrier (34, 39) of the planetary gear mechanism (30). In an operating device for a brake system, the rotational axis (24) of the drive shaft (23) is oriented perpendicular to the displacement axis (4) of the actuator element (3).

2. The operating device according to claim 1, characterized in that the transmission (29) has a rack (52) provided with a drive tooth portion (53) and is supported displaceably.

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

4. The operating device according to any one of claims 1 to 3, characterized in that the transmission (29) is at least partially disposed within the housing (7) of the operating device (1), and the motor housing (20) is fixed to the housing (7), in particular by at least one fixing means (17).

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

6. The driven shaft (46) of the planetary gear mechanism (30) has a first support portion (47) and a second support portion (48) arranged at an interval from the first support portion (47), and the housing (7) supports the support portions (47, 48) of the driven shaft (46). The operating device according to any one of claims 4 and 5, characterized in that.

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

8. The operating device according to claim 7, characterized in that the displacement axis (4) of the actuator element (3) is oriented perpendicular to the cross section of the extrusion profile (7).

9. The operating device according to any one of claims 1 to 8, characterized in that the driven shaft (46) has an axially penetrating portion (56), and the drive shaft (23) penetrates through the axially penetrating portion (56) and protrudes.

10. The operating device according to claim 9, characterized in that the drive shaft (23) has a first end portion (57) protruding from the axially penetrating portion (56), and a rotational speed sensor (58) is arranged on the first end portion (57).

11. The operating device according to claim 10, characterized in that the first end portion (57) having the rotational speed sensor (58) protrudes into the controller (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 driven shaft (46).

13. The planetary gear mechanism (30) has at least a first planetary stage (31) and a second planetary stage (36) connected downstream of the first planetary stage (31) in terms of transmission technology. The first planetary stage (31) has a first internal gear (32), a first sun gear (33), and a first planetary gear carrier (34). At least one first planetary gear (35) is rotatably supported by the first planetary gear carrier. The second planetary stage (36) has a second internal gear (37), a second sun gear (38), and a second planetary gear carrier (39). At least one second planetary gear (40) is rotatably supported by the second planetary gear carrier. The second planetary gear carrier (39) has the driven shaft (46). The operating device according to any one of claims 1 to 12, characterized in that.

14. The first planetary gear carrier (34) is fixedly supported and arranged. The internal gears (32, 37) are coupled to be non-rotatable relative to each other. The sun gears (33, 38) are coupled to be non-rotatable relative to each other. The quotient of the number of teeth of the first internal 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 internal gear (33) and the number of teeth of the second sun gear (38). The operating device according to claim 13, characterized in that.

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