Braking force generator for brake equipment, operating device for brake equipment

Abstract

To manufacture a planetary carrier at low costs.SOLUTION: A brake force generator 1 for brake equipment has: a drive shaft 3; an operation member slidably supported; and a gear device 6 acting between the drive shaft and the operation member so that the operation member slides when the drive shaft rotates, and the gear device has a planetary gear 7 having: a sun gear 11 connected to the drive shaft in a manner that it cannot rotate; a planetary carrier 8 rotatably supported; at least one planetary pinion 9A rotatably supported by the planetary carrier; and a driven engagement portion 22 belonging to the operation member. The driven engagement portion 22 is configured on a mantle wall 21 of an end region 14 of the planetary carrier facing in a direction opposite to the drive shaft.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present invention relates to a brake force generator for a brake installation, comprising: a drive shaft rotatably supported within a housing of the brake force generator; an electric motor having a rotor and at least one motor winding, the rotor being non-rotatably arranged on the drive shaft and rotatable by energizing the motor winding; an operating member slidably supported; and a gear device acting between the drive shaft and the operating member such that the operating member slides when the drive shaft rotates, the gear device having a sun gear non-rotatably connected to the drive shaft, a rotatably supported planetary carrier, at least one planetary pinion rotatably supported on the planetary carrier, and a driven meshing portion associated with the operating member.

[0002] Furthermore, the invention relates to an actuating device having a braking force generator of the type mentioned at the outset. [Background technology]

[0003] A hydraulic brake system of a motor vehicle typically includes at least one friction brake device. To operate the friction brake device, the brake system typically includes an operating device having a master brake cylinder in which at least one hydraulic piston is slidably supported. The master brake cylinder is then fluidically connected to a slave cylinder of the friction brake device. To operate the friction brake device, the hydraulic cylinder slides so that hydraulic fluid is transferred from the master brake cylinder into the slave cylinder.

[0004] Increasingly, automobile manufacturers are installing operating devices with brake force generators that allow for electric motor-driven sliding of hydraulic pistons and thus electric motor-driven actuation of friction brake devices. For example, operating devices of the applicant's i-Booster type have such a brake force generator. The brake force generator has a drive shaft rotatably supported in the brake force generator housing. The brake force generator further has an electric motor with a rotor and at least one, particularly polyphase, motor winding. The rotor is non-rotatably arranged on the drive shaft and can be rotated by appropriately energizing the motor winding, causing the drive shaft to rotate together with the rotor. The motor winding can be, for example, a stator winding fixed to the housing or a rotor winding that can rotate together with the rotor.

[0005] The braking force generator further includes a slidably supported operating member. A gear device is further provided that acts between the drive shaft and the operating member so that the operating member slides when the drive shaft rotates. That is, the gear device is configured to convert the rotational movement of the drive shaft into the translational movement of the operating member. To this end, the gear device typically includes a sun gear non-rotatably connected to the drive shaft, a rotatably supported planetary carrier, at least one planetary pinion rotatably supported on the planetary carrier, and a planetary gear having a driven mesh associated with the operating member. Summary of the Invention

[0006] The braking force generator of the present invention, which has the features of claim 1, is characterized in that the driven gear is configured on the outer wall of the end region of the planetary carrier facing away from the electric motor. In contrast, it is known in the prior art to assemble an additional gear with a driven gear to the end region of the planetary carrier, which in this case is configured in a rod-like manner. However, this results in relatively high manufacturing costs because the rod-like end region and the additional gear must be manufactured with as small component tolerances as possible. In contrast, the solution of the present invention is less costly because the planetary carrier itself has the driven gear, i.e., the gear output of the planetary gear, and therefore no additional gear is required. The planetary gear preferably has several planetary pinions rotatably mounted on the planetary carrier. It is particularly preferred that the planetary pinions are rotatably mounted on the planetary carrier, evenly distributed around the circumference of the planetary carrier. The drive shaft and the planetary carrier are preferably supported for rotation about the same axis of rotation. When the terms "axial" or "radial" are used within the scope of this disclosure, these terms refer to this axis of rotation unless expressly stated otherwise. The operating member is preferably supported for sliding in the axial direction, i.e., the operating member is slidable along the axis of rotation or along an axis extending parallel to and radially spaced from the axis of rotation.

[0007] The planetary carrier is preferably made of plastic, which allows it to be produced at low cost. It is particularly preferred that the planetary carrier is produced as an injection-molded part, i.e., by injection molding, which allows even complex geometries, such as driven gears, to be produced technically easily.

[0008] In a preferred embodiment, the driven meshing portion directly meshes with the meshing portion of the operating member, or at least one other gear member of the gearing acts between the driven meshing portion and the operating member. If the driven meshing portion directly meshes with the meshing portion of the operating member, only a small number of parts are required to construct the gearing, thereby enabling the gearing to be configured in a way that saves design space. If another gear member is present, the driven meshing portion acts indirectly, i.e., indirectly, on the operating member. Preferably, the other gear member constitutes a second gear stage of the gearing, which exists in addition to the first gear stage constituted by a planetary gear. In this sense, the gearing is configured as a multi-stage. The multi-stage configuration of the gearing allows for particularly precise sliding of the operating member.

[0009] The driven gearing is preferably arranged on the outer wall of the mantle in the end region, which makes the driven gearing technically easy to access and thus allows the driven gearing to be easily brought into meshing engagement with a gearing of another gear member or with a gearing of an operating member.

[0010] In a preferred embodiment, the gear device is intended to have a second planetary gear, and a second sun gear of the second planetary gear is configured by a driven meshing portion. The provision of the second planetary gear provides a second gear stage, which allows the operating member to slide particularly accurately. Since the second sun gear of the second planetary gear is configured by a driven meshing portion, the planetary gear and the second planetary gear are arranged coaxially with each other. Accordingly, the provision of the second planetary gear does not increase, or only slightly increases, the radial length of the gear device. Accordingly, the provision of the second planetary gear provides a second gear stage in a manner that reduces design space.

[0011] The end region is preferably configured as a hollow shaft, and the driven gear is configured on the inner wall of the outer casing of the hollow shaft-like end region. Accordingly, the end region is configured as a spindle nut. This embodiment of the end region is particularly suitable for directly cooperating with the operating element. The operating element is preferably configured as a threaded spindle and is screwed into the hollow shaft-like end region. In this case, the operating element configured as a threaded spindle is advantageously equipped with an anti-rotation device, so that when the drive shaft and, therefore, the planetary carrier rotates, the operating element does not rotate but slides axially.

[0012] In a preferred embodiment, the planetary carrier is intended to be injected onto a metal support rod by injection molding, i.e., to obtain the planetary carrier, a support rod is prepared that is overmolded with plastic. Metal support rods have high stability, so that the planetary carrier is injected onto the support rod, thereby improving the stability of the planetary carrier.

[0013] The braking force generator preferably has a bearing for transmitting radial forces, and the support rod radially abuts against a first bearing ring of the bearing for supporting the planetary carrier. Due to the high stability of metal support rods, they are particularly suitable for supporting the planetary carrier. The end of the support rod facing away from the electric motor is preferably free of the planetary carrier, and this end of the support rod radially abuts against a first bearing ring of the bearing.

[0014] The actuating device of the present invention for a brake system has a master brake cylinder in which a hydraulic piston is slidably supported, and is characterized by the brake force generator of the present invention according to the features of claim 9, wherein the hydraulic piston is slidable by sliding of the actuating member. This also results in the advantages already mentioned. Other preferred features and combinations of features will become apparent from the above description and the claims. The hydraulic piston is preferably slidable axially, i.e., the hydraulic piston is slidable along the axis of rotation or along an axis extending parallel to and radially spaced from the axis of rotation. The actuating member preferably abuts indirectly against the hydraulic piston when it slides, i.e., there is at least one other slidable member between the actuating member and the hydraulic piston. Alternatively, the actuating member abuts directly against the hydraulic piston when it slides.

[0015] Next, the present invention will be described in detail with reference to the drawings. [Brief explanation of the drawings]

[0016] [Figure 1] 1 is a first embodiment of a braking force generator of an operating device for brake equipment; [Figure 2] 1 is a second embodiment of a braking force generator. [Figure 3] 10 is a third embodiment of a braking force generator. [Figure 4] 10 is a fourth embodiment of a braking force generator. [Figure 5] 10 is a fifth embodiment of a braking force generator. [Figure 6] 10 is a sixth embodiment of a braking force generator. [Figure 7] 10 is a seventh embodiment of a braking force generator. [Figure 8] 10 is an eighth embodiment of a braking force generator. DETAILED DESCRIPTION OF THE INVENTION

[0017] FIG. 1 shows a first embodiment of a brake force generator 1 of an actuating device (not shown) of a hydraulic brake system. The hydraulic brake system includes a plurality of friction brake devices. The actuating device is configured to actuate the friction brake devices in order to generate a friction brake torque by the friction brake devices. For this purpose, the actuating device has a master brake cylinder in which at least one hydraulic piston is slidably supported. Typically, the master brake cylinder is a tandem master brake cylinder, whereby typically two hydraulic pistons are slidably supported in the master brake cylinder. In this case, the master brake cylinder is fluidically coupled to a slave cylinder of the friction brake device. When the hydraulic pistons slide into the actuating device, hydraulic fluid is transferred from the master brake cylinder into the slave cylinder, generating a friction brake torque.

[0018] The actuating device 1 is configured for electrically driving a hydraulic piston and thus for electrically driving a friction brake device. A principle of this kind is essentially known from actuating devices of the Applicant's iBooster type.

[0019] The operating device 1 has a housing 2 in which a drive shaft 3 is rotatably mounted. The drive shaft 3 is rotatably mounted about a rotation axis 5. The operating device 1 further has an electric motor 4, which is shown only diagrammatically. The electric motor 4 has a rotor and a multi-phase motor winding. The rotor is non-rotatably arranged on the drive shaft 3 and can be rotated by energizing the motor winding, whereby the drive shaft 3 rotates together with the rotor. The motor winding is, for example, a stator winding fixed to the housing and arranged distributed around the rotor.

[0020] The operating device 1 further has at least an operating member, not shown in FIG. 1, which is slidably supported in the axial direction, i.e. along the rotation axis 5 or along an axis extending parallel to and radially spaced from the rotation axis 5.

[0021] The operating device 1 further comprises a gearing 6 acting between the drive shaft 3 and the operating member such that the operating member slides axially when the drive shaft 3 rotates, the operating member being coupled to a hydraulic piston such that the hydraulic piston slides together with the operating member when the operating member slides in the operating direction.

[0022] The gear device 6 has a planetary gear 7. The planetary gear 7 has a sun gear 11 non-rotatably connected to the drive shaft 3. The planetary gear 7 further has a planetary carrier 8 rotatably supported about the rotation axis 5. The planetary gear 7 further has a plurality of planetary pinions rotatably supported on the planetary carrier 8, the meshing portions of which mesh with the meshing portions of the sun gear 11. In this example, a first planetary pinion 9A, a second planetary pinion 9B, and a third planetary pinion are present, but only the first planetary pinion 9A and the second planetary pinion 9B can be seen. The first planetary pinion 9A is rotatably supported on the planetary carrier 8 by a metal first planetary pinion shaft 10A. The second planetary pinion 9B is rotatably supported on the planetary carrier 8 by a metallic second planetary pinion shaft 10B. The third planetary pinion, not visible, is rotatably supported on the planetary carrier 8 by a metallic third planetary pinion shaft, not visible. When the design configuration of one of the planetary pinions or one of the planetary pinion shafts is described below, that design configuration also applies to the other planetary pinions or other planetary pinion shafts. Furthermore, the planetary gear 7 has a ring gear 12 fixed to the housing, and the meshing portions of the planetary pinions also mesh with the meshing portions of the ring gear 12.

[0023] The planetary carrier 8 is manufactured as an injection-molded part, i.e. by injection molding, from plastic and has a first end region 13 facing towards the electric motor 4 and a second end region 14 facing away from the electric motor 4.

[0024] The first end region 13 is configured as a hollow shaft section 13. In this sense, the end region 13 is cylindrical. The outer wall 15 of the hollow shaft section 13 has a number of radial through-holes corresponding to the number of planetary pinions. Each planetary pinion is assigned one radial through-hole and inserted into the radial through-holes. For example, the first planetary pinion 9A is inserted into the first radial through-hole 16A. The second planetary pinion 9B is inserted into the second radial through-hole 16B.

[0025] The planetary pinion shafts are supported in hollow shaft sections 13 on both sides of the planetary pinions. This will be explained in more detail below with respect to the first planetary pinion shaft 10A. The hollow shaft section 13 has a first bearing section 17 and a second bearing section 18. The first bearing section 17 has an axial through-hole 19. The second bearing section 18 has an axial recess 20 aligned with the axial through-hole 19. The first planetary pinion shaft 10A is supported both in the axial through-hole 19 and in the axial recess 20. The first planetary pinion shaft 10A is then fixedly connected to the planet carrier 8 in the region of the axial through-hole 19 and in the region of the axial recess 20, preferably by press fitting. To assemble the first planetary pinion 9A, the first planetary pinion 9A is first inserted into the radial through-hole 16A. The planetary pinion shaft 10A is then inserted through the axial through-hole 19 and through the central cutout of the first planetary pinion 9A and into the axial recess 20 until the front end of the planetary pinion shaft 10A, as seen in the insertion direction, abuts axially against the bottom surface of the axial recess 20. The planetary pinion shaft 10A is then dimensioned so that, when the planetary pinion shaft 10A is inserted, there is no planetary pinion shaft 10A in the rear region of the axial through-hole 19, as seen in the insertion direction. To axially fix the planetary pinion shaft 10A, this region of the axial through-hole 19 is formed by heat staking. In this example, the first bearing section 17 is located closer to the electric motor 4 than the second bearing section 18.

[0026] The second end region 14 of the planetary carrier 8 facing away from the electric motor 4 has an outer wall 21 on which the driven meshing portion 22, i.e., the gear output portion of the planetary gear 7, is formed. That is, the planetary carrier 8 made of plastic has the driven meshing portion 22. In the embodiment shown in FIG. 1 , the outer wall 21 is an outer wall 51 of the second end region 14 of the planetary carrier 8.

[0027] 1, the gear arrangement 6 has a further gear member 23, i.e., a gear wheel 23, whose meshing portion meshes with the driven meshing portion 22. Accordingly, at least one further gear member of the gear arrangement 6 acts between the driven meshing portion 22 and an operating member (not shown). If an operating member is shown, its meshing portion would mesh with that of, for example, the gear wheel 23. Alternatively, there could be at least one further gear member, such as, for example, a threaded nut, between the gear wheel 23 and the operating member. Furthermore, the operating member would be provided with an anti-rotation device to prevent rotation of the operating member.

[0028] 1, the planetary carrier 8 is injection molded onto a metal support rod 24 to increase the stability of the planetary carrier 8. The support rod 24 extends in this example through the second end region 14 of the planetary carrier 8. The end 25 of the support rod 24 facing away from the electric motor 4 is free of the planetary carrier 8, which is made of plastic.

[0029] The brake force generator 1 further includes a first bearing 26 for transmitting radial forces. The first bearing 26 is arranged between the planetary pinion, on the one hand, and the electric motor 4, on the other. The hollow shaft section 13 abuts a first bearing ring 27 of the first bearing 26 from the radial inside. A first end shield 28 fixed to the housing abuts a second bearing ring 29 of the first bearing 26 from the radial outside. A plurality of rolling elements 30 are arranged between the first bearing ring 27 and the second bearing ring 29. In this sense, the first bearing 26 of the embodiment shown in FIG. 1 is configured as a rolling bearing 26. Here, the first bearing ring 27 forms the inner bearing ring of the first bearing 26, and the second bearing ring 29 forms the outer bearing ring of the first bearing 26.

[0030] The braking force generator 1 further includes a second bearing 31 that transmits radial forces. The second bearing 31 is arranged between the first bearing 26 on the one hand and the electric motor 4 on the other hand. The drive shaft 3 abuts against a first bearing ring 32 of the second bearing 31 from the radially inner side. A second end shield 33 fixed to the housing abuts against a second bearing ring 34 of the second bearing 31 from the radially outer side. A plurality of rolling elements 40 are arranged between the first bearing ring 32 and the second bearing ring 34. In this sense, the second bearing 31 of the embodiment shown in FIG. 1 is also configured as a rolling bearing 31.

[0031] The braking force generator 1 further includes a third bearing 35 that transmits radial forces. The end 25 of the support rod 24 abuts against a first bearing ring 36 of the third bearing 35 from the radially inner side. The first end shield 28 abuts against a second bearing ring 37 of the third bearing 35 from the radially outer side. A plurality of rolling elements 38 are arranged between the first bearing ring 36 and the second bearing ring 37. In this sense, the third bearing 36 of the embodiment shown in FIG. 1 is also configured as a rolling bearing 36.

[0032] FIG. 2 shows a braking force generator 1 according to a second embodiment. The braking force generator 1 shown in FIG. 2 differs from the braking force generator 1 shown in FIG. 1, particularly in terms of the configuration of the first bearing 26. In the embodiment shown in FIG. 2, the hollow shaft section 13 abuts against the first bearing ring 27 of the first bearing 26 from the radial outside. The second end shield 33 abuts against the second bearing ring 29 of the first bearing 26 from the radial inside. That is, the second end shield 33 abuts against the second bearing ring 34 of the second bearing 31 from the radial outside on the one hand and against the second bearing ring 29 of the first bearing 26 from the radial inside on the other hand. For this purpose, the free end section 39 of the second end shield 33 has a stepped shape in the area of ​​the bearings 26 and 31. In the embodiment shown in FIG. 2, the first bearing ring 27 forms the outer bearing ring of the first bearing 26 and the second bearing ring 29 forms the inner bearing ring of the first bearing 26 .

[0033] FIG. 3 shows a braking force generator 1 according to a third embodiment. The braking force generator 1 shown in FIG. 3 differs from the braking force generator 1 shown in FIG. 2, particularly in terms of the configuration of the second end region 14 of the planetary carrier 8. In the embodiment shown in FIG. 3, the gearing 6 has a second planetary gear 41. The second sun gear 42 of the second planetary gear 41 is formed by the driven meshing portion 22 of the outer wall 21 of the second end region 14 of the planetary carrier 8. The second planetary gear 41 has a rotatably supported second planetary carrier 43. The second planetary carrier 43 is also preferably made of plastic, preferably by injection molding. Three planetary pinions are rotatably supported on the second planetary carrier 43, of which only the fourth planetary pinion 44A and the fifth planetary pinion 44B are visible in FIG. 3. In the embodiment shown in Fig. 3, the second planetary carrier 43 abuts against the first bearing ring 36 of the third bearing 35 from the radially inner side. A separate end shield 45 fixed to the housing abuts against the second bearing ring 37 of the third bearing 35 from the radially outer side. If an operating member is shown, a meshing portion of the operating member would mesh with, for example, a driven meshing portion of the second planetary carrier 43. Alternatively, there would be at least one other gear member between the driven meshing portion of the second planetary carrier and the operating member. Furthermore, the operating member would be equipped with an anti-rotation device to prevent rotation of the operating member.

[0034] FIG. 4 shows a braking force generator 1 according to a fourth embodiment. The braking force generator 1 shown in FIG. 4 differs from the braking force generator 1 shown in FIG. 3, particularly in terms of the configuration of the support for the drive shaft 3 and the support for the planetary carrier 8. In the embodiment shown in FIG. 4, the second bearing 31 is omitted. Instead, both the planetary carrier 8 and the drive shaft 3 are rotatably supported by the first bearing 26. The first bearing ring 27 forms the outer bearing ring of the first bearing 26. The hollow shaft section 13 abuts the first bearing ring 27 from the radial outside. The second bearing ring 29 forms the inner bearing ring of the first bearing 26. Nevertheless, to enable the second end shield 33 to abut the second bearing ring 29 from the radial outside, the second bearing ring 29 has a second axial protrusion 45 that protrudes axially from the first bearing 26 in the direction of the electric motor 4. The second end shield 33 abuts radially outwardly against the second axial projection 45. The drive shaft 3 abuts radially inwardly against the second bearing ring 29 by means of a needle roller assembly 46. Alternatively, the drive shaft 3 abuts radially inwardly against a third bearing ring, which further forms the inner bearing ring of the first bearing 26, whereby the second bearing ring 29 forms the middle bearing ring of the first bearing 26. In that case, it is advantageous to arrange a plurality of rolling elements or sliding media between the second bearing ring 29 and the third bearing ring.

[0035] FIG. 5 shows a braking force generator 1 according to a fifth embodiment. The braking force generator 1 shown in FIG. 5 differs from the braking force generator 1 shown in FIG. 4, particularly in terms of the configuration of the first bearing 26. In the embodiment shown in FIG. 5, the second bearing ring 29 forms the outer bearing ring of the first bearing 26. A second end shield 33 abuts against the second bearing ring 29 from the radially outer side. The first bearing ring 27 forms the inner bearing ring of the first bearing 26. Nevertheless, to enable the hollow shaft section 13 to abut against the first bearing ring 27 from the radially outer side, the first bearing ring 27 has a first axial protrusion 47 that protrudes axially from the first bearing 26 in the direction of the planetary pinion 9. The hollow shaft section 13 abuts against the first axial protrusion 47 from the radially outer side. The drive shaft 3 abuts against the first bearing ring 27 from the radially inner side by means of a needle roller assembly 46. Alternatively, the drive shaft 3 abuts radially from the inside against a third bearing ring, which further forms the inner bearing ring of the first bearing 26, whereby the first bearing ring 27 forms the middle bearing ring of the first bearing 26. In that case, it is advantageous to arrange a plurality of rolling bodies or sliding media between the first bearing ring 27 and the third bearing ring.

[0036] Figure 6 shows a braking force generator 1 based on a sixth embodiment. The braking force generator 1 shown in Figure 6 differs from the braking force generator 1 shown in Figure 5 in that a plurality of balls 48 are provided between the drive shaft 3 and the first bearing ring 27 instead of a needle roller assembly 46 as a rolling element. Here, the drive shaft 3 has a circumferential groove 49. The first bearing ring 27 has a circumferential groove 50 that faces the circumferential groove 49 in the radial direction. The balls 48 engage with both the circumferential groove 49 and the circumferential groove 50 in the radial direction.

[0037] FIG. 7 shows a braking force generator 1 according to a seventh embodiment. The embodiment shown in FIG. 7 differs from the embodiment shown in FIG. 1 in particular with regard to the configuration of the second end region 14 of the planetary carrier 8. In the embodiment shown in FIG. 7, the second end region 14 is configured as a hollow shaft. The driven gear 22 is configured on the inner wall 52 of the outer casing of the hollow shaft-like end region 14. FIG. 7 also shows an operating element 53. In this example, the operating element 53 is a threaded spindle 54 that is screwed into the driven gear 22. The threaded spindle 54 is equipped with an anti-rotation device (not shown), so that when the planetary carrier 8 rotates, the threaded spindle 54 does not rotate together with the planetary carrier 8 but slides axially.

[0038] FIG. 8 shows a braking force generator 1 according to an eighth embodiment. In the embodiment shown in FIG. 8, the second end region 14 is also hollow-shaft shaped, and the driven gear 22 is configured on the inner wall of the outer casing of the hollow-shaft shaped end region 14. A threaded spindle 55 is screwed onto the driven gear 22. Alternatively, the planetary carrier 8 is injection-molded onto the threaded spindle 55. The operating member 53 is formed by a threaded nut 56 screwed onto the threaded spindle 55. The threaded nut 56 is provided with an anti-rotation device (not shown), so that when the planetary carrier 8 rotates, the threaded nut 56 does not rotate together with the planetary carrier 8 but slides axially. [Explanation of symbols]

[0039] 1 Braking force generator 2. Housing 3 drive shaft 4 electric motors 6 Gearing 7 Planetary Gear 8 Planetary Carrier 9A Planetary Pinion 11 Sun gear 14 End area 21 Mantle Wall 22 driven meshing portion 24 Support rod 35 bearings 36 First bearing ring 41 Second planetary gear 42 Second sun gear 51 Mantle outer wall 52 Inner wall of mantle 53 Operating member

Claims

1. A brake force generator for a brake installation, comprising: a drive shaft (3) rotatably supported within a housing (2) of a brake force generator (1); an electric motor (4) having a rotor and at least one motor winding, the rotor being non-rotatably disposed on the drive shaft (3) and rotatable by energizing the motor winding; an operating member (53) slidably supported; and a gear device (6) acting between the drive shaft (3) and the operating member (53) such that the operating member (53) slides when the drive shaft (3) rotates, the gear device (6) including a planetary gear (7), The planetary gear (7) is a sun gear (11) non-rotatably connected to the drive shaft (3); a rotatably supported planetary carrier (8) including a first end region (13) and a second end region (14) formed integrally with the first end region (13), the first end region (13) being arranged between the electric motor (4) and the second end region (14), the planetary carrier (8) being a hollow tube formed by an outer wall (15) enclosing an interior space in which the sun gear (11) is arranged, the outer wall (15) including at least one notch passing through the outer wall (21) in a radial direction from the interior space to an outer region radially outside the outer wall (15); A ring gear (12); a planetary pinion shaft and a planetary pinion corresponding to each of the at least one notch; The planetary pinions are rotatably mounted in the respective notches of the hollow tubes of the planetary carrier (8) so as to satisfy the following (a) to (d): (a) the centers of the respective planetary pinions are radially disposed within the radial region of the mantle wall (15); (b) each said planetary pinion extends radially through said respective notch from said interior space to a radially outer side of said planetary pinion; (c) each planetary pinion is rotatable relative to the outer wall (15) by rotating about its respective planetary pinion shaft, the planetary pinion shaft extending axially from a first axial position within the thickness of the outer wall (15), through the axial position of each notch, to a second axial position within the thickness of the outer wall (15); (d) the outer side of each planetary pinion is arranged to interact with the external teeth of the sun gear (11) in the internal space and with the internal teeth of the ring gear (12) in the external space, thereby causing rotation of the planetary carrier (8); and, A braking force generator (1), wherein a radial edge of the second end region (14) of the planetary carrier (8) is formed as a driven meshing (22) associated with the operating member (53) so that rotation of the planetary carrier (8) causes the driven meshing (22) to generate an axial translational movement of the operating member (53).

2. 2. A braking force generator according to claim 1, characterized in that the planetary carrier (8) is made of plastic.

3. 3. A braking force generator according to claim 1 or 2, characterized in that the planetary carrier (8) is produced as an injection-molded part.

4. 4. The braking force generator according to claim 1, wherein the driven meshing portion (22) directly meshes with a meshing portion of the operating member (53), or at least one other gear member of the gear device (6) acts between the driven meshing portion (22) and the operating member (53).

5. 5. A braking force generator according to claim 1, wherein the driven tooth (22) is arranged on an outer mantle wall (51) of the second end region (14).

6. 6. The braking force generator according to claim 5, wherein the gear device (6) has a second planetary gear (41), and a second sun gear (42) of the second planetary gear (41) is constituted by the driven meshing portion (22).

7. 5. The brake force generator according to claim 1, wherein the second end region (14) is configured as a hollow shaft, and the driven meshing portion (22) is configured on an inner wall (52) of the hollow shaft-shaped second end region (14).

8. 8. A braking force generator according to any one of claims 2 to 7, characterized in that the planetary carrier (8) is injected onto a metal support rod (24) by injection moulding.

9. 9. A brake force generator according to claim 8, further comprising a bearing (35) for transmitting radial forces, the support rod (24) abutting in the radial direction against a first bearing ring (36) of the bearing (35) for supporting the planetary carrier (8).

10. 10. An operating device for a brake system, comprising: a master brake cylinder in which a hydraulic piston is slidably supported; and a brake force generator (1) according to any one of claims 1 to 9, wherein the hydraulic piston is slidable by sliding of the operating member (53).

11. A braking force generator as described in claim 1, wherein at least one gear member of the gear device (6) acts between the driven meshing portion (22) and the operating member (53).

12. A brake force generator as described in claim 9, wherein the bearing (35) includes the first bearing ring (36), a second bearing ring (37) radially outside the first bearing ring (36), and a plurality of rolling elements (38) that are at the same axial position as each other and are all radially surrounded by the first and second bearing rings (36, 37).

13. A bearing (26) is provided at an axial position between the axial position of the electric motor (4) and the axial position of each of the planetary pinions, 2. The brake force generator according to claim 1, wherein the bearing (26) includes, at one axial position, a first bearing ring (27) against which the radially outer side of the first end region (13) of the planetary carrier (8) abuts on its radially inner side, a second bearing ring (29) located radially outside the first bearing ring (27), and a plurality of rolling elements (30) radially surrounded by the first and second bearing rings (27, 29).

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