Tensioning module for electromechanical wheel brake and electromechanical brake system

Abstract

The invention relates to a tensioning module for an electromechanical wheel brake and to an electromechanical brake system. The tensioning module is used to move a brake piston in an electromechanically operable wheel brake, preferably a brake piston in an electromechanically operable wheel brake of a motor vehicle.

Description

TECHNICAL FIELD

[0001] The present invention relates to a tensioning module for an electromechanical wheel brake and to an electromechanical brake device. The tensioning module is used to move a brake piston in an electromechanically operable wheel brake, preferably in an electromechanically operable wheel brake of a motor vehicle. BACKGROUND

[0002] Electromechanical wheel brakes ("EMB") are currently being developed for modern motor vehicles, which are also to be used as service brakes. These wheel brakes offer a number of advantages over conventional hydraulically actuated wheel brakes. For example, a complex hydraulic system is no longer required, and electromechanical wheel brakes also occupy significantly less space.

[0003] Electromechanical wheel brakes of this type typically have an electronic drive unit that interacts with a mechanism or a gear mechanism. A brake unit can then be arranged on the output side, and this brake unit can for example comprise a brake piston and a friction lining, which can be pressed onto a rotating friction partner by means of a translational movement. A deceleration can thereby be caused during operation.

[0004] To this end, the drive unit typically comprises at least one electric motor with a correspondingly high power density. A mechanical connection to the friction brake can then be established by means of at least a gear mechanism. In addition to factors such as efficiency and stiffness, the mechanical design, the installation space requirement and the transmission behavior in particular determine the possible applications of the wheel brake.

[0005] Various mechanisms are known for converting the rotational movement of an electric motor into the desired translational or linear movement. A known such mechanism is for example a ball screw drive (KGT). Ball screw drives offer the possibility of linear power transmission. However, known electromechanical brake devices with a ball screw drive as a rotation / translation converter have a relatively long overall design to make up for the relatively long distance, also taking into account wear compensation, which can be disadvantageous in terms of installation situation and space requirement.

[0006] It is true that the installation space for electromechanically actuated parking brake units is less important, so that the entire tensioning module can have a relatively large axial overall length.

[0007] However, if a tensioning module of this type (similar to an electric parking brake as described above) is to be used for example in an electromechanically actuable disc brake as a service brake, the greater extension in the axial direction would be disadvantageous instead. This can lead to challenges for such electromechanically actuable wheel brakes, in particular when they are to be integrated into a front axle of a motor vehicle.

[0008] The steering lock at the front axle in particular makes it desirable to have an axial overall length (an extension in the direction of the piston axis) that is as small as possible in order to be able to integrate an electromechanically actuatable disc brake into the installation space of a front axle of a motor vehicle of today. The axial overall length of an electromechanically actuatable wheel brake is therefore of particular importance.

[0009] On the other hand, the torque transmitted by the parking brake is smaller than the torque transmitted by the service brake. This can lead to the fact that anti-rotation protection means of the ball screw drive, such as between the piston and the brake lining, and / or seals, such as those known from parking brakes, cannot be easily transferred to the service brake. SUMMARY

[0010] It is therefore desirable to have a tensioning module, in particular for an electromechanically actuatable wheel brake, which at least mitigates the above-mentioned disadvantages or ideally has none of these. Here, the tensioning module should preferably be able to interact with a ball screw drive.

[0011] Furthermore, the electromechanically actuatable wheel brake should be able to be used as a service brake.

[0012] In addition, it is an object to reduce the axial overall length of the electromechanically actuatable wheel brake to the smallest possible size.

[0013] Here, it is also advantageous that the number of required components can be reduced. In addition, it is also desirable to achieve the greatest possible modularity in the construction and the individual components and to have a satisfactory mountability of the individual parts and components.

[0014] The inventors have set themselves this object.

[0015] This object is surprisingly simply achieved by a tensioning module, an electromechanical brake device, in particular for a motor vehicle, and a motor vehicle as claimed in one of the independent claims. Preferred embodiments and developments of the application can be gathered from the respective dependent claims.

[0016] Thus, in a first aspect, the application comprises a tensioning module,

[0017] in particular for an electromechanical brake device for a motor vehicle,

[0018] The tensioning module comprises:

[0019] a ball screw drive,

[0020] a stop bearing washer, and

[0021] an axial bearing,

[0022] wherein the ball screw drive comprises a screw spindle and a nut, wherein a stop bearing washer is arranged at a radially extending axial end of the screw spindle,

[0023] and a rotation protection device is provided between the nut and a housing surrounding the tensioning module.

[0024] In another aspect, the present application also relates to an electromechanical brake device, preferably an electromechanically actuatable wheel brake, comprising such a tensioning module.

[0025] Finally, the present application also relates to a motor vehicle comprising at least one electromechanical brake device having at least one tensioning module as described above.

[0026] In the context of the present application, a motor vehicle is to be understood as meaning a vehicle having axles, wherein at least one of these axles can comprise steerable wheels and, furthermore, the drive to the wheels of at least one axle can be adapted in a wheel-specific manner.

[0027] The electromechanically actuatable wheel brake of the electromechanical brake device can be designed as an electromechanical disc brake, for example a caliper brake, in particular both for front axle applications and for rear axle applications in a motor vehicle.

[0028] It is also possible for the tensioning module according to the application to be used together with other wheel brakes, for example drum brakes. Combinations with parking brakes are also possible.

[0029] The electromechanical brake device can comprise an electric motor for driving the screw spindle, which preferably has a correspondingly designed gear mechanism. This can generate a drive torque, which is transmitted from the electric motor to the screw spindle via a suitable gear mechanism.

[0030] The configuration of the electromechanical brake device according to the application described hereinafter is shown by way of example only using an example of an electromechanical disc brake for setting a defined application force. A transfer to an electromechanical drum brake for setting a defined opening force or brake torque is possible without any problems for the person skilled in the art.

[0031] With regard to the brake device, the application direction, i.e. the axial direction along which the piston can be moved to generate a brake force, is referred to hereinafter as the piston side or on the piston side, while the opposite direction, and thus the release direction along which the drive unit can be positioned in the extension of the screw spindle, is also referred to as the drive side of the brake device or on the drive side.

[0032] Electromechanically actuatable disc brakes can be designed in such a way that the application force can be generated by means of an electric motor and a gear mechanism. In this context, the application force refers to the force with which the brake linings are pressed against the brake disc. Depending on the embodiment and the control concept, the actuation of the electromechanical disc brake can make it possible to set a certain, defined tensioning force or a certain, defined brake torque in accordance with the requested deceleration demand.

[0033] The tensioning module can comprise a housing of the disc brake housing general design style or a caliper housing, or can be integrated into such a caliper housing (for example, a floating caliper brake or a sliding caliper brake). The caliper housing can also be designed here as a multiple-piston unit or a multiple-piston caliper and can comprise more than one tensioning module (for example, two tensioning modules). In this way, the caliper housing can be designed as a double-piston sliding caliper, for example. The caliper housing can comprise corresponding holders for mounting the friction linings to implement the disc brake.

[0034] According to the application, a tensioning module of the type mentioned at the outset is provided, wherein the lead screw, the nut, the stop bearing washer and / or the axial bearing can be designed as separate components.

[0035] The tensioning module can further comprise a piston, which is configured in such a way that the piston can also be axially displaced by the axial movement of the nut, and wherein the stop bearing washer can be arranged on the side of the lead screw opposite the piston. This makes it possible to achieve a very compact design in the axial direction.

[0036] According to a preferred embodiment of the application, the lead screw can be mounted in the housing by means of an axial bearing. The axial bearing can be arranged in such a way that it can absorb axial forces that can arise in the clamping process and can transmit these axial forces to the housing. To this end, the lead screw can have a radially protruding, preferably annular, stop, which makes it possible to transmit the axial forces first to the stop bearing washer and from there to the axial bearing.

[0037] According to a preferred embodiment of the application, the lead screw can have a piston-side threaded portion and a drive-side drive portion, wherein the drive portion can have a smaller cross-sectional area than the threaded portion. In this way, an annular stop can be formed, which provides a piston-side stop surface for the stop bearing washer. The transition from the drive portion to the threaded portion thus represents the radial extension of the lead screw.

[0038] The application of the clamping force can take place by means of a nut and a screw spindle, which thus interact as a rotational-translational converter. On the basis of a drive torque of an electric motor, which can be transmitted to the screw spindle preferably via a suitably designed gear unit, the piston can be moved in an axially movable manner by means of the nut relative to the housing. In this way, for example in the case of a disc brake, the friction linings can be moved and pressed against a rotating element, for example a brake disc, in order to generate a predetermined braking torque.

[0039] The piston can be connected to the housing here by means of an elastic ring element, wherein the elastic ring element can be configured to be elastically deformable such that the housing and the piston can be displaced axially relative to one another. In this way, a gap or intermediate space generated between the housing and the piston can be sealed off from the ingress of particles or other substances.

[0040] The stop bearing washer can be disc-shaped or ring-shaped and have a through-hole, so that it can be inserted onto the screw spindle. This makes it possible to achieve cost-effective individual production and easy assembly.

[0041] For a fixed connection / torsionally rigid connection for co-rotation with the screw spindle, the stop bearing washer can have a toothing in the region of the through-hole. The toothing can be designed, for example, as an internal toothing in the stop bearing washer, wherein the screw spindle can then have a diametrically opposite configuration with an external toothing which fits exactly. Furthermore, the stop bearing washer can comprise a centring collar on the end face pointing towards the piston, which can facilitate assembly to the screw spindle in a form-fitting manner. Alternatively or additionally, a press-fit connection or an integral bond connection can also be provided, but it must be noted that the torque to be transmitted can be very great.

[0042] Finally, according to a particularly preferred embodiment of the application, the stop bearing washer can comprise a radially protruding shoulder. As a result, an end stop can be provided in particular advantageously, by means of which the end position of the actuator can be detected.

[0043] Such a tensioning module allows the integration of anti-rotation protection and tangential rotation stop into a single component or into a single assembly. This allows the number of components required to be reduced to a very advantageous extent.

[0044] The tensioning module according to the application can further comprise an anti-rotation protection, which is designed, for example, as a separate anti-rotation protection element. This makes it possible to achieve an easy-to-mount capability while having a high degree of modularity. The anti-rotation protection element can engage with the nut and the piston and provide an anti-rotation protection for the nut relative to the piston. According to a development of the application, it can also be provided that the anti-rotation protection element further engages with the housing. In this way, an anti-rotation protection can be provided for both the nut and the piston relative to the housing.

[0045] The anti-rotation protection element can have at least one of the following features. It can be designed as a disc-shaped or ring-shaped element with a continuous opening or through-hole, so that it can be plugged onto the nut and fixedly connected therewith for co-rotation. The fixed connection for co-rotation can also be provided via a toothing as described above or via, for example, a corresponding flat portion. Alternatively or additionally, a crimp connection or an integral bond connection can also be provided.

[0046] According to a particularly preferred embodiment of the application, the anti-rotation protection element can comprise a radially protruding attachment portion, which can engage into a recess or groove of the piston to form the anti-rotation protection device.

[0047] According to another equally particularly preferred embodiment of the application, the anti-rotation protection element can comprise a pin, which preferably protrudes axially from an end face on the side opposite the piston. To this end, the pin can be arranged on a radially protruding attachment portion and can provide a stop for a radially protruding shoulder of the stop bearing washer in a predetermined rotational position of the stop bearing washer.

[0048] The anti-rotation protection device according to the application can in this way implement at least two functions. Thus, an anti-rotation protection device of the nut relative to the piston and / or relative to the surrounding housing can be provided. A tangential rotation stop of the lead screw and the nut can also be provided.

[0049] The design of the proposed tensioning module can ensure reliable and safe operation of the tensioning module and of the electromechanically actuatable wheel brake equipped with the tensioning module.

[0050] Most advantageously, the rotational angle of the motor and the lead screw can here always be assigned a unique axial piston stroke, and thus reliable functioning and control of the piston stroke can be achieved by means of electronics and suitable software designed for this purpose.

[0051] The electronics and software can be provided in a drive unit, which can be connected to the housing and can thus be assigned to the wheel brake. However, these functions can also be stored in, for example, a central vehicle controller. BRIEF DESCRIPTION OF DRAWINGS

[0052] Further details of the application result from the description of the exemplary embodiments shown and the claims appended thereto.

[0053] In the drawings:

[0054] Figure 1 A cross-sectional view of a tensioning module according to the application is shown according to a first embodiment of the application,

[0055] Figure 2 A cross-sectional view of a tensioning module according to the application is shown according to a first embodiment of the application, Figure 1External view of a tension module according to the invention,

[0056] Figure 3 An external view of a tension module according to the invention is shown, Figure 1 Oblique view of a stop bearing washer of a tension module according to the invention,

[0057] Figure 4 An external view of a tension module according to the invention is shown, Figure 1 External view of a tension module according to the invention (without stop bearing washer), Figure 2 and Figure 3 External view of a tension module according to the invention (without stop bearing washer),

[0058] Figure 5 Ball screw drive of a tension module according to the invention (without housing) and more visible anti-rotation protection according to the invention, Figure 4

[0059] Ball screw drive of a tension module according to the invention (without anti-rotation protection) according to the invention, Figure 6 Figure 5 Cross-sectional view of a tension module according to the invention according to another embodiment of the invention,

[0060] Figure 7 External view of a tension module according to the invention is shown,

[0061] Figure 8 Figure 7 Oblique view of a stop bearing washer of a tension module according to the invention,

[0062] Figure 9 External view of a tension module according to the invention is shown, Figure 7 Oblique view of a stop bearing washer of a tension module according to the invention,

[0063] Figure 10 External view of a tension module according to the invention (without stop bearing washer), Figure 8 and Figure 9 External view of a tension module according to the invention (without stop bearing washer),

[0064] Figure 11 Ball screw drive of a tension module according to the invention (without housing) and more visible anti-rotation protection according to the invention, and Figure 10

[0065] Ball screw drive of a tension module according to the invention (without anti-rotation protection) according to the invention. Figure 12 DETAILED DESCRIPTION Figure 10

[0066] ​​​​In the following detailed description of preferred embodiments, for clarity, the same reference numerals denote these embodiments or substantially the same parts of these embodiments. However, for better illustration of the invention, the preferred embodiments shown in the drawings are not always drawn to scale. For clarity, only those elements relevant to embodiments of the method according to the invention are shown herein.

[0067] Figure 1 and Figure 7 A cross-sectional view of a possible embodiment of the tensioning module 1 according to the present invention is shown. The tensioning module 1 is particularly suitable for electromechanical braking devices of motor vehicles and includes:

[0068] - Ball screw drive device

[0069] - Stop bearing washer 2, and

[0070] - Axial bearing 3.

[0071] The ball screw drive device includes a lead screw 4 and a nut 5, wherein a stop bearing washer 2 is arranged at the radially extending axial end of the lead screw 4.

[0072] Furthermore, an anti-rotation protection device is provided between the nut 5 and the housing 6 surrounding the tensioning module 1.

[0073] The housing 6 is designed for mounting and securing the tensioning module 1. Figure 2 In the plan view of the tensioning module 1 shown, various components (such as the surrounding housing 6) are not shown for clarity.

[0074] The present invention further includes an electromechanical braking device having the tensioning module 1 as described above, preferably an electromechanically actuated wheel brake. The electromechanically actuated wheel brake is preferably designed as a disc brake. The electromechanically actuated wheel brake preferably includes a motor for driving the lead screw 4.

[0075] Furthermore, the present invention also includes a motor vehicle comprising at least one electromechanical braking device having at least one tensioning module 1 as described above.

[0076] The rotary-translational converter of tensioning module 1 is designed as a ball screw drive, which has a nut 5, a screw 4, and balls running in corresponding grooves in the nut 5 and / or the screw 4. Figure 1 (Not shown in the view). In the tensioning module 1 shown, the lead screw 4, nut 5, stop bearing washer 2, and axial bearing 3 are designed as separate components, which makes it easy to manufacture these components from the correspondingly selected suitable materials.

[0077] In the illustrated embodiment, the tensioning module 1 further includes a piston 7. The piston 7 is arranged linearly or axially relative to the housing 6. The tensioning module 1 may include a drive unit (not shown in more detail) with a motor and gear mechanism to generate drive torque so that the lead screw 4 can withstand torque during operation.

[0078] Based on the drive torque of the drive unit, piston 7 can move axially relative to housing 6 along its axis of rotation. Nut 5 is configured to transmit a force component to piston 7 by means of axial movement. In this way, piston 7 can press friction linings (not shown) against brake disc (not shown) to generate a predetermined braking torque or predetermined applied force for the wheel brake.

[0079] In the configuration shown, piston 7 is connected to housing 6 via elastic ring element 8 (not fully shown), wherein elastic ring element 8 is elastically deformable, allowing housing 6 and piston 7 to be axially displaced relative to each other.

[0080] Tensioning module 1 includes an anti-rotation protection device, which includes an anti-rotation protection element 9. Figure 1 The advantageous configuration and arrangement of the anti-rotation protection element 9 are shown in the figure. The following will combine... Figure 5 Further discussion on anti-rotation protection element 9.

[0081] The tensioning module 1 further includes an axial retaining ring 10 mounted in the piston 7. The retaining ring 10 is used to actively move the piston 7 in the release direction by means of the nut 5. Figure 1 Pull from the middle to the right.

[0082] Tensioning module 1 further includes a stop bearing washer 2 and an axial bearing 3. Figure 3 A perspective view of the stop bearing washer 2 in an advantageous embodiment of the present invention is shown.

[0083] The lead screw 4 is supported in the housing 6 by an axial bearing 3. The axial bearing 3 is arranged such that it can absorb axial forces that may be generated during clamping and can transmit these axial forces to the housing 6. The axial bearing 3 can be designed, for example, as a single-row or double-row cylindrical roller bearing, such as... Figure 1 As shown.

[0084] The spindle 4 has a radial annular stop 44 which extends in an annular manner for the stop bearing washer 2, which makes it possible for axial forces which occur during application to be transmitted firstly to the stop bearing washer 2 and from there to the axial bearing 3. The spindle 4 comprises a piston-side threaded portion 42 and a drive-side drive portion 43, wherein the drive portion 43 has a smaller cross-sectional area or a smaller diameter than the threaded portion 42. In this way, the annular stop 44 is formed, which provides a piston-side stop surface for the stop bearing washer 2 or the radial extension.

[0085] As shown in the embodiment, Figure 1 The outer diameter of the axial bearing 3 can correspond approximately to the outer diameter of the stop bearing washer 2, as shown in the embodiment. This makes it possible, in particular, to axially support the tangential outer region of the stop bearing washer 2, whereby a particularly high stability can be achieved.

[0086] The stop bearing washer 2 is in the form of a disc or ring with a through-hole 41, through which the spindle 4, in particular the drive portion 43, is guided. The stop bearing washer 2 is designed to be able to be inserted directly onto the spindle 4 in the axial direction. In order to achieve a fixed connection for co-rotation with the spindle 4, a toothing 48 is provided in the region of the through-hole. The corresponding portion of the spindle 4 has a matching design with a corresponding counter-toothed structure.

[0087] In the embodiment shown, this counter-toothed structure is an outer toothing 51 of the spindle 4, which interacts with the inner toothing of the stop bearing washer 2 and establishes a form-locked connection. Alternatively or additionally, a crimp connection or an integral bond connection is also possible. In this way, the drive torque can be reliably transmitted between the spindle 4 and the stop bearing washer 2.

[0088] Figure 3 The toothing 48 of the stop bearing washer 2 as an inner toothing is shown. In the embodiment shown, the toothing 48 is configured with 12 teeth 49 or 12 point-like portions. This makes it possible to insert axially on the spindle 4 in a particularly advantageous manner, which is configured in the embodiment with a hexagonal outer toothing in the corresponding portion of the spindle 4. Since the inner toothing is designed with 12 teeth, the axial insertion provides more adjustment possibilities compared to an inner toothing which is designed with only 6 teeth, which is considered to be advantageous for assembly.

[0089] The stop bearing washer 2 further comprises a centring collar 50 on the end face pointing towards the piston for mounting in an accurately fitting manner.

[0090] Furthermore, the stop bearing washer 2 is formed with a radially protruding shoulder 45, which provides a tangential rotation stop for the stop bearing washer 2 and the nut 5 and / or the rotation protection element 9.

[0091] Figure 4 An external view of the tension module 1 according to the application is shown (without the Figure 2 and Figure 3 stop bearing washer 2). The outer contour of the screw 4 can be easily recognized as a hexagon with a diametrically opposite design with an exact fit to the inner contour of the stop bearing washer 2, and the stop bearing washer 2 is axially plugged onto this hexagon. Furthermore, the centering device 52 can be seen, which, in the installed position, lies on the centering collar 50 of the stop bearing washer 2.

[0092] According to the application, the stop bearing washer 2 combines the following functions in a very compact manner in a single component:

[0093] - the stop bearing washer forms a running surface for the axial bearing 3 or the rolling bodies of the axial bearing 3, and

[0094] - the stop bearing washer forms a tangential rotation stop between the screw 4 and the nut 5.

[0095] Figure 5 A ball screw drive according to the application is shown according to Figure 4 the tension module 1 according to the application, without the caliper housing 6, as a result of which the anti-rotation protection device is more visible. The anti-rotation protection device is designed as an annular anti-rotation protection element 9. As can also be seen from Figure 1 , in this embodiment, the anti-rotation protection element 9 is seated on the nut 5. The piston 7 comprises a recess 55, which extends in an annular manner in order to receive the anti-rotation protection element 9, as a result of which the anti-rotation protection element 9 is received by the piston 7 and is thus arranged mainly within the piston 7. This region of the piston comprises a further recess 53, which will also be discussed further below.

[0096] The anti-rotation protection element 9 can be plugged onto the nut 5 in the axial direction. In the embodiment shown in Figure 5 , the outer contour of the nut 5 is provided for this purpose with three flat sections 54 in the example. The inner contour of the anti-rotation protection element 9 is for this purpose a diametrically opposite design with an exact fit, with corresponding flat sections 56, as a result of which a form-locked connection is produced between the nut 5 and the anti-rotation protection element 9.

[0097] The anti-rotation protection element 9 comprises a radially protruding attachment portion 46. As can be clearly seen in Figure 4 , this attachment portion 46 can be received by the recess 53 of the piston 7. In Figure 1 , this attachment portion 46 is not visible. As a result, an anti-rotation protection device can be formed between the nut 5 and the piston 7.

[0098] In the preferred embodiment of the application shown, the attachment portion 46 also has a protruding design relative to the housing surface of the piston 7 and is thus guided through a corresponding portion of the piston 7 so that it can be guided further into the housing 6. The attachment portion 46 thus protrudes radially relative to the housing surface of the piston 7.

[0099] Preferably, the attachment portion 46 protrudes here to such an extent that it can engage into a recess of the housing 6, for example with an exactly fitting diametrically opposite design. The attachment portion can then be guided in this recess in the housing 6 in the case of an axial movement of the piston 7 and in this way a rotation protection device can be realized between the nut 5 and the housing 6 in a particularly compact design.

[0100] According to the application, the attachment portion 46 further comprises a protrusion or pin 47 at its radial end, which has a substantially axial orientation.

[0101] The pin 47 protrudes axially relative to the rotation protection element 9 or an end face of the rotation protection element 9 in the direction opposite to the piston 7. In the embodiment shown, the pin does not protrude in the radial direction beyond the attachment portion 46 so as to be guided likewise in a recess of the housing 6.

[0102] This embodiment thus combines the following functions:

[0103] - the pin 47 forms a rotation protection device for the nut 5 in the housing 6. To this end, the housing 6 is provided with a recess having an exactly fitting diametrically opposite design.

[0104] - the pin 47 forms a rotational stop against which the stop bearing washer 2, in particular the shoulder 45, can be contacted tangentially. This forms a rear stop of the tensioning module 1.

[0105] In the embodiment shown, the rotation protection element 9 is of one-piece or single-piece design with the attachment portion 46 and the pin 47. However, a multi-piece embodiment is also conceivable and possible, for example an embodiment in which the pin 47 is designed as a separate bolt and is plugged into the attachment portion 46.

[0106] Figure 6 A ball screw drive according to the application is shown for a tensioning module 1 according to Figure 5 without a rotation protection device. In this illustration, three flat portions 54 on the outer contour of the nut 5 can be seen, on which the rotation protection element 9 is placed axially.

[0107] In the embodiment of the tensioning module 1 according to the application shown in Figure 7 the stop bearing washer 2 has a narrow design in the axial direction. As a result, installation space in the axial direction can again be saved.

[0108] In the embodiment of the invention shown here, the diameter of the threaded portion 42 of the screw spindle 4 is chosen to be very large, in particular relative to the diameter of the drive portion 43. In Figure 7 particular, the diameter of the threaded portion 42 is more than twice the diameter of the drive portion 43, even approximately three times the diameter of the drive portion. This makes it possible for the fixed connection for co-rotation between the screw spindle 4 and the stop bearing washer 2 to have a correspondingly different configuration, as a result of which the stop bearing washer 2 can have a shorter design viewed in the axial direction, which advantageously shortens the length of the tensioning module 1.

[0109] The background is that the stop bearing washer 2 is configured on the piston-side end face with a toothing 59, into which a diametrically opposite flat portion 57 of the screw spindle 4 engages with an exact fit. In this way, a form-fit and thus a fixed connection for co-rotation is created.

[0110] The diameter of the piston-side toothing 59 is greater than the diameter of the axial bearing 3, wherein, in the case of the toothing 59, the outer circular path surrounding the tips of the teeth 58 is meant. Thus, the stop bearing washer 2 can have a thinner configuration than Figure 1 the embodiment of the invention in which the stop bearing washer 2 has a thicker configuration in the axial direction in order to close the force flow from the stop 44 to the axial bearing 3. In other words, in the embodiment of the invention Figure 1 in which the diameter of the axial bearing 3 is greater than the diameter of the threaded portion 42 of the screw spindle 4, the stop bearing washer 2 has a thicker configuration in the axial direction.

[0111] Figure 8 An external view of the tensioning module 1 according to the invention in Figure 7 is shown, and Figure 9 a sectional view of the tensioning module 1 according to the invention in Figure 7 is shown.

[0112] Furthermore, Figure 10 an external view of the tensioning module 1 according to the invention is shown (without the stop bearing washer 2 of Figure 8 and Figure 9 ), and Figure 11 a ball screw drive of the tensioning module 1 according to the invention is shown (without the housing) and the more visible anti-rotation protection according to Figure 10 .

[0113] Finally, Figure 12 a ball screw drive of the tensioning module 1 according to the invention is shown (without the anti-rotation protection) according to Figure 10 .

[0114] List of reference signs:

[0115] 1 tension module

[0116] 2 stop bearing washer

[0117] 3 axial bearing

[0118] 4 lead screw

[0119] 5 nut

[0120] 6 housing

[0121] 7 piston

[0122] 8 ring element

[0123] 9 anti-rotation protection element

[0124] 10 fixing ring

[0125] 41 through hole

[0126] 42 threaded portion

[0127] 43 drive portion

[0128] 44 stop

[0129] 45 shoulder

[0130] 46 attachment portion

[0131] 47 pin

[0132] 48 toothed structure

[0133] 49 tooth

[0134] 50 centering collar

[0135] 51 external toothed structure

[0136] 52 centering means

[0137] 53 recess

[0138] 54 flat portion

[0139] 55 annular recess

[0140] 56 flat portion

[0141] 57 flat portion

[0142] 58 tooth

[0143] 59 toothed structure

Claims

1. A tensioning module (1), in particular for an electromechanical brake device of a motor vehicle, comprising: - a ball screw drive, - a stop bearing washer (2), and - an axial bearing (3), wherein the ball screw drive comprises a screw spindle (4) and a nut (5), wherein the stop bearing washer (2) is arranged at a radially extending axial end of the screw spindle (4), and a rotation protection is provided between the nut (5) and a housing (6) surrounding the tensioning module (1).

2. The tension module (1) according to the preceding claim, wherein The tensioning module (1) comprises a piston (7) which is configured such that it can be axially displaced by a nut (5) driven axial movement, wherein the stop bearing washer (2) is preferably arranged on the side of the screw spindle (4) opposite the piston (7).

3. The tension module (1) according to any one of the preceding claims, wherein The screw spindle (4) is supported in the housing (6) by the axial bearing (3).

4. The tension module (1) according to any one of the preceding claims, wherein The piston (7) is connected to the housing (6) by an elastic ring element (8), wherein the elastic ring element (8) is elastically deformable such that the housing (6) and the piston (7) can be axially displaced relative to each other.

5. The tension module (1) according to any one of the preceding claims, wherein, The screw spindle (4) comprises a threaded portion (42) and a drive portion (43), wherein the drive portion (43) has a smaller cross-sectional area than the threaded portion (42).

6. The tension module (1) according to any one of the preceding claims, wherein The screw spindle (4) comprises a stop (44) extending in an annular manner for the stop bearing washer (2).

7. The tension module (1) according to any one of the preceding claims, wherein The stop bearing washer (2) has at least one of the following features: - the stop bearing washer (2) has an annular shape with a through-hole, - the stop bearing washer (2) comprises a radially protruding shoulder (45).

8. The tension module (1) according to any one of the preceding claims, wherein The stop bearing washer (2) comprises a centring collar (50) on the end face pointing towards the piston (7).

9. The tension module (1) according to any one of the preceding claims, wherein The stop bearing washer (2) comprises a toothing (48), preferably an internal toothing, particularly preferably an internal toothing with 12 teeth (49), in the region of the through-hole, wherein the corresponding drive portion (43) of the screw spindle (4) has an exactly matching counter toothing for forming a form-locking connection.

10. The tension module (1) according to any one of the preceding claims, wherein The stop bearing washer (2) comprises a toothing (59) on the piston-side end face, wherein the screw spindle (4) has an exactly complementary mating flat portion (57) for forming a form-locking connection.

11. The tension module (1) according to any one of the preceding claims, wherein The rotation protection comprises a rotation protection element (9) which engages with the nut (5) and the piston (7) and provides a rotation protection of the nut (5) relative to the piston (7).

12. The tension module (1) as claimed in the preceding claim, wherein The rotation protection element (9) further engages with the housing (6) and provides a rotation protection of the nut (5) relative to the housing (6).

13. The tension module (1) according to any of the two preceding claims, wherein The rotation protection element (9) has at least one of the following features: - the rotation protection element (9) is essentially designed as an annular element, - the rotation protection element (9) comprises a radially protruding attachment (46), - the rotation protection element (9) comprises a pin (47) which protrudes axially, preferably in the direction opposite the piston (7), from the end face, - the pin (47) is arranged on the attachment (46).

14. The tension module (1) according to any one of the preceding claims, wherein The stop bearing washer (2) provides a running surface for the axial bearing (3), and / or wherein the stop bearing washer (2) forms a tangential rotational stop between the lead screw (4) and the nut (5).

15. The tension module (1) according to any one of the preceding claims, wherein, The lead screw (4), the stop bearing washer (2) and the axial bearing (3) are designed as separate components.

16. An electromechanical brake device, preferably an electromechanically operable disc brake, comprising a tensioning module (1) according to one of the preceding embodiments, and an electric motor connected with the lead screw (4) for driving the lead screw (4).

17. A motor vehicle comprising at least one electromechanical brake device according to the preceding claim.

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