Clamping module of electromechanical wheel brake and electromechanical brake device

Abstract

The invention relates to a clamping module for an electromechanical wheel brake and an electromechanical brake device. The invention relates to a clamping module for moving a brake piston in an electromechanically operable wheel brake of a preferably motor vehicle.

Description

Technical Field

[0001] This invention relates to a clamping module for an electromechanical wheel brake and an electromechanical braking device having such a clamping module. The clamping module is used to move the brake piston in an electromechanically operable wheel brake, preferably in a motor vehicle. Background Technology

[0002] Electromechanical wheel brakes (“EMBs”) are increasingly used in modern motor vehicles, and they also serve as service brakes. These wheel brakes offer several advantages over conventional, hydraulically actuated wheel brakes. Therefore, complex hydraulic systems are no longer needed, and electromechanical wheel brakes are significantly more space-efficient.

[0003] Such electromechanical wheel brakes typically have an electronic drive unit that works in conjunction with a mechanism or transmission. Thus, a braking unit can be arranged on the output side, which may include, for example, a brake piston and friction pads that can press against a rotating friction pair by means of translational motion. This allows for deceleration during operation.

[0004] Therefore, the drive unit typically includes at least one motor with a correspondingly high power density. Thus, a mechanical connection can be established with the friction brake, at least by means of a transmission device. Besides factors such as efficiency and rigidity, the mechanical structure, structural space requirements, and transmission characteristic curves, in particular, determine the applicability of wheel brakes.

[0005] To convert the rotational motion of an electric motor into the desired translational or linear motion, corresponding mechanisms are known. Known mechanisms include, for example, rotation / translation converters comprising so-called ramp mechanisms or ramp units. Such mechanisms are known, for example, from the applicant's document DE 199 22 333 A1.

[0006] Alternative mechanisms can be found in ball screw drives (KGTs). Although ball screw drives do not offer the possibility of non-linear force transmission, they also eliminate the need for complex wear compensation because the effective stroke can be longer than that of a rotary / translational converter with a ramp mechanism.

[0007] Therefore, known electromechanical braking devices with ball screw drives as rotation / translation converters are constructed to be relatively long in order to bridge the relatively long path in terms of wear compensation; however, this may be detrimental to the installation environment and space requirements. Here, installation space is more critical in the case of electromechanically operated service brake units compared to, for example, in the case of parking brake units.

[0008] If such clamping modules are to be used, for example, in electromechanical disc brakes serving as service brakes, the axial extension dimension is relatively large. This can pose a challenge in electromechanical disc brakes, especially when they are to be integrated into the front axle of a motor vehicle. At the front axle, due to the steering angle, the smallest possible axial structural length (extension dimension along the piston axis) is desired in order to integrate the electromechanical disc brake into the mounting space of today's passenger vehicle (PKW) front axle. Therefore, the axial structural length of the electromechanical disc brake is particularly important and must be reduced to the smallest possible extent.

[0009] In current designs of ball screw drives (such as those integrated into parking brakes), there is typically no mechanism to prevent relative rotation of the nut or piston towards the brake caliper housing. However, the absence of a form-locking anti-relative-rotation mechanism between the nut and the caliper housing can lead to uncontrolled rotation of components of the ball screw drive (e.g., the nut or piston) relative to the caliper housing. In other words, the nut and / or piston may undergo undesirable rotation, for example, relative to the caliper housing. This can result in the spindle or motor rotation angle no longer being able to be assigned a specific axial position to the piston and / or nut. Consequently, difficulties may arise regarding the controllability of the clamping module or electromechanical brake. Summary of the Invention

[0010] Therefore, the object of the present invention is to provide a clamping module, particularly a clamping module for electromechanical braking devices, which at least reduces or, ideally, eliminates the aforementioned disadvantages. Here, the clamping module is preferably equipped with a ball screw drive mechanism.

[0011] Another advantage is that it reduces the number of required components. Furthermore, it is desirable to achieve the greatest possible modularity in the construction and individual components, as well as good assemblability of the components and parts. Here, the required components (such as the spindle of the ball screw drive mechanism) should also be able to be manufactured as cost-effectively as possible.

[0012] The inventor has undertaken this objective.

[0013] This objective is achieved in a surprisingly simple manner by a clamping module, an electromechanical braking device (especially for motor vehicles), and a motor vehicle as described in one of the independent claims. Preferred embodiments and improvements of the invention are derived from the corresponding dependent claims.

[0014] Therefore, the present invention relates in a first aspect to a clamping module, particularly a clamping module for an electromechanical braking device of a motor vehicle, the clamping module comprising:

[0015] - Ball screw drive mechanism

[0016] - Piston,

[0017] - Axial bearing,

[0018] The ball screw transmission mechanism includes a main shaft and a nut.

[0019] The spindle includes a threaded section and a drive section.

[0020] Furthermore, the threaded section and the drive section are manufactured as separate components and are securely connected to each other.

[0021] The spindle can be supported by axial bearings in a housing (such as the brake caliper housing of a motor vehicle brake).

[0022] A preferred embodiment of the invention also provides a stop bearing washer disposed at the axial end of the radial extension of the spindle, wherein an axial bearing is disposed on the side of the stop bearing washer opposite to the piston.

[0023] In another aspect, the invention also relates to an electromechanical braking device, preferably an electromechanically actuated wheel brake, particularly preferably an electromechanically actuated disc brake, the electromechanical braking device including such a clamping module.

[0024] Finally, the present invention also relates to a motor vehicle comprising at least one electromechanical braking device having at least one clamping module as described above.

[0025] In the context of this invention, a motor vehicle refers to a vehicle having axles, wherein at least one of these axles includes wheels that are steerably guided, and furthermore, the drive mechanism of the wheels of at least one axle can be adjusted in a wheel-specific manner.

[0026] Electromechanical braking devices, specifically electromechanically actuated wheel brakes, can be implemented as electromechanical disc brakes (“eCaliper”), particularly for front and rear axle applications in motor vehicles.

[0027] Electromechanical braking devices may include an electric motor to drive a spindle. The motor can generate driving torque to actuate the wheel brakes. The driving torque can be transmitted from the motor to the spindle via a suitable transmission mechanism.

[0028] The configuration of the electromechanical braking device of the present invention described below is only exemplified by an electromechanical disc brake for setting a defined clamping force. Those skilled in the art can easily convert it to an electromechanical drum brake to set a defined expansion force or braking torque.

[0029] For a braking device, the direction in which the piston moves to generate braking force (i.e., the axial direction) is referred to below as the piston side or piston side, while the opposite direction in which the drive unit can be located on the extension of the main shaft (i.e., the release direction) is also referred to as the drive side or drive side of the braking device.

[0030] Electromechanical disc brakes can be implemented such that clamping force can be generated by means of a motor, a transmission device, and a rotation / translation converter. Here, clamping force refers to the force that presses the brake pads against the brake disc, thereby generating a corresponding braking torque on the observed wheel. Depending on the implementation method and control scheme, the electromechanical disc brake can be operated in such a way that a pre-defined, limited clamping force or a pre-defined, limited braking torque can be set according to the required deceleration request.

[0031] An electromechanically actuated drum brake (e-Drum) can preferably be implemented in such a way that a motor unit / drive unit actuates an expansion module that uses a pre-given expansion force based on the required deceleration request to press the brake pads against the brake drum and thus generate a corresponding braking torque.

[0032] The clamping module may include a brake caliper housing with a common structural form of disc brake housing, or may be integrated into such a brake caliper housing, such as a floating caliper brake. Here, the brake caliper housing may also be implemented as a multi-piston unit or multi-piston brake caliper, and include more than one clamping module, for example, two clamping modules. In this way, the brake caliper housing may, for example, be designed as a dual-piston floating brake caliper. The brake caliper housing may include a retaining element for securing the friction pads to achieve a corresponding retaining element for the disc brake.

[0033] According to the present invention, a clamping module of the type described at the outset is provided, wherein the spindle, the stop bearing washer, and the axial bearing can be designed as separate components. The clamping module may also include a piston and an anti-relative rotation mechanism, particularly an anti-relative rotation element. This allows for high modularity while achieving simple assemblability.

[0034] With the clamping module according to the invention, the anti-relative rotation mechanism and the tangential rotation stop are implemented in a single component or a single assembly. Therefore, the assembly may include a nut, a spindle, a stop bearing washer, and / or an axial bearing. Thus, the desired function can be achieved with a very small number of components. This also reduces the axial length of the clamping module.

[0035] According to a preferred embodiment of the invention, the spindle may be supported in the housing by an axial bearing. The axial bearing may be arranged such that it can absorb axial forces that may be generated during clamping and transmit these axial forces to the housing. The spindle may have a radially extending, preferably annular, stop that enables the axial forces to be transmitted first to the stop bearing washer and then from the stop bearing washer to the axial bearing.

[0036] Therefore, according to a preferred embodiment of the invention, the spindle may have a threaded section on the piston side and a drive section on the drive side, wherein the drive section may have a smaller cross-sectional area than the threaded section, thereby forming an annular stop portion that provides the aforementioned piston-side stop surface for the stop bearing washer. The axial bearing may, for example, be implemented as a single-row or double-row cylindrical roller bearing.

[0037] Applying clamping force can be done using a nut and a spindle, which act as a rotation-to-translation converter. Based on the drive torque of the motor (which can preferably be transmitted to the spindle via a correspondingly designed transmission unit), the piston can be displaced axially relative to the housing by means of the nut. In this way, the friction lining can be moved toward and pressed against a rotating element (e.g., a brake disc) to generate a predetermined braking torque. Therefore, the piston can be designed to axially displace along with the axial movement of the nut.

[0038] Here, the piston can be connected to the housing via a flexible annular element, which can be designed to be elastically deformable, allowing for relative axial displacement between the housing and the piston. In this way, any gaps or voids between the housing and the piston can be sealed to prevent the ingress of particles or other substances.

[0039] To withstand large axial loads and / or simultaneously achieve a very compact axial configuration, it is advantageous to have a relatively large spindle diameter. However, on the other hand, the diameter of the spindle's drive section must be chosen to be quite small, especially to accommodate axial bearings. These geometric requirements for the spindle may result in the outer diameter of the drive section being very small compared to the outer diameter of the threaded section. This can be disadvantageous for spindles manufactured, for example, by cold forming. However, alternative manufacturing methods (such as machining) are associated with very high costs.

[0040] Therefore, according to the invention, the spindle is implemented as a two-part unit. In other words, the spindle according to the invention may include a threaded section and a drive section, wherein the threaded section and the drive section are manufactured as separate components and can then be securely, in particular, connected to each other in a manner that prevents relative rotation. The term "prevents relative rotation" can be understood as allowing torque to be transmitted without slippage. This makes it particularly advantageous to select the corresponding cost-effective manufacturing method for the respective sections of the spindle.

[0041] Furthermore, different materials can be selected for these two sections. Therefore, compared to the drive section, which may have lower requirements, a higher-quality material with superior stiffness characteristics and surface hardness can be selected for the threaded section, for example. This also saves costs. Corresponding steel alloys can be provided as materials.

[0042] The threaded section and drive section of the spindle can be connected to each other in a material-locking manner.

[0043] The threaded section and drive section of the spindle can be force-locked together.

[0044] The threaded section and drive section of the spindle can also be connected to each other in a form-locking manner.

[0045] It is particularly advantageous to combine, for example, form-locking connections and force-locking connections together, such as as a combination of meshing and press-fitting.

[0046] For this purpose, the threaded section may, for example, have internal teeth in its drive-side region. The drive section may include external teeth in its piston-side region. Here, the external and internal teeth can be formed in a precisely fitting and completely complementary manner. For connection, the external teeth of the drive section can be pushed into the internal teeth, thereby creating a form-locking engagement. A press fit can then be provided between the threaded section and the drive section to prevent loosening.

[0047] This allows the drive section to have a significantly smaller outer diameter than the threaded section. Consequently, an annular stop can also be formed, which can (e.g., as a stop bearing washer) provide a stop surface on the piston side.

[0048] In this way, for example, a spindle can be produced, wherein the outer diameter D of the threaded section of the spindle is... G The outer diameter D of the drive section of the spindle A For comparisons, the following relationship applies: D G > 1.3 * D A Preferably D G > 1.5 * D A D is particularly preferred G > 1.7 * DA Therefore, the corresponding outer diameter can be very well adapted to the corresponding function.

[0049] According to a preferred embodiment of the present invention, different functions can be integrated into one component. In this way, the number of components in the clamping module can be reduced and the construction can be simplified.

[0050] Therefore, the stop bearing washer can, for example, have a substantially annular shape with a through hole so that it can be inserted into the spindle. To allow for a non-rotatable connection with the spindle, the stop bearing washer can have teeth, preferably internal teeth, in the area of ​​the through hole.

[0051] According to the improved embodiment of the present invention, the stop bearing gasket and / or drive section can be formed as an integral, monolithic component, which can bring further cost advantages.

[0052] The non-rotatable connection between the stop bearing washer and the spindle can also take other forms, such as by means of the engagement of the external teeth of the drive section, for example in the extension of the teeth for connecting to the threaded section in a non-rotatable manner.

[0053] The stop bearing gasket may also include a centering collar / centering flange on the piston-facing end, which facilitates precise assembly with the spindle.

[0054] According to another particularly preferred embodiment of the invention, the stop bearing washer may include a radially extending shoulder. This provides a particularly advantageous end stop by which the termination position of the actuator can be identified.

[0055] According to another particularly preferred embodiment of the invention, an anti-relative rotation mechanism may also be provided. The anti-relative rotation mechanism may include an anti-relative rotation element or a fixing element.

[0056] The anti-relative rotation element may have at least one of the following features: The anti-relative rotation element may be designed as a through-hole, annular, or substantially annular element so that it can be inserted into a nut and connected to the nut in a manner that prevents relative rotation. The anti-relative rotation element may also include a radially extending protrusion that can engage in a notch or groove to achieve anti-relative rotation. The anti-relative rotation element may also include a pin-shaped portion that preferably extends axially relative to the end side in the direction opposite to the piston. For this purpose, the pin-shaped portion may be arranged on the protrusion and have a stop portion at a specific rotational position of the stop bearing washer for the radially extending shoulder.

[0057] Another embodiment of the invention may include a fixing element (e.g., a pin or nail) as an anti-relative rotation mechanism, which may be arranged, for example, between the nut and the housing and / or the piston.

[0058] By means of the proposed components or the design of the electromechanical braking device according to the invention, reliable and safe operation can be ensured for the clamping module and thus the electromechanically actuated wheel brake, especially the electromechanically actuated disc brake, equipped with the clamping module, wherein a form-locking anti-rotation mechanism is provided for the nut and / or piston relative to the surrounding housing (especially the brake caliper housing of the wheel brake).

[0059] Here, most advantageously, the rotation angle of the motor and spindle can always be assigned a defined axial piston stroke, and thus reliable function and control of the piston stroke can be achieved by means of electronics and suitable software. The electronics and software can be housed in a drive unit, which can be connected to the housing. The drive unit may also include a motor and / or a transmission device or transmission mechanism to drive the clamping module.

[0060] The anti-relative rotation mechanism according to the present invention can achieve two functions: on the one hand, it provides anti-relative rotation by form-locking the surrounding housing, especially the brake caliper housing, and on the other hand, it provides tangential rotation stop for the main shaft and nut. Attached Figure Description

[0061] Further details of the invention will be derived from the description of the illustrated embodiments and the appended claims.

[0062] In the attached diagram:

[0063] Figure 1 A cross-sectional view of an exemplary clamping module according to a first embodiment of the present invention is shown.

[0064] Figure 2 Shown from Figure 1 The external view of the clamping module of the present invention.

[0065] Figure 3 Showing from a perspective view Figure 1 The stop bearing gasket of the clamping module of the present invention,

[0066] Figure 4 Showing from a perspective view Figure 1 The drive section of the main shaft of the clamping module of the present invention,

[0067] Figure 5 Showing from a perspective view Figure 1 The threaded section of the main shaft of the clamping module of the present invention,

[0068] Figure 6 Shown from Figure 1An external view of the clamping module of the present invention without the stop bearing washer.

[0069] Figure 7 Showing with Figure 6 Correspondingly, in the ball screw drive mechanism of the clamping module of the present invention, which is without a housing, the anti-relative rotation mechanism is more clearly visible.

[0070] Figure 8 Showing with Figure 5 Correspondingly, the ball screw transmission mechanism of the clamping module of this invention lacks an anti-relative rotation mechanism.

[0071] Figure 9 A cross-sectional view of the clamping module of the present invention according to another embodiment is shown.

[0072] Figure 10 Showing from a perspective view Figure 9 The drive unit of the main shaft of the clamping module of the present invention,

[0073] Figure 11 Showing another oblique view from Figure 9 The drive unit of the main shaft of the clamping module of the present invention,

[0074] Figure 12 Showing from a perspective view Figure 9 The threaded section of the main shaft of the clamping module of the present invention,

[0075] Figure 13 Showing from a perspective view Figure 9 The fixing element of the clamping module of the present invention,

[0076] Figure 14 A cross-sectional view of the clamping module according to another embodiment of the present invention is shown.

[0077] Figure 15 Showing with Figure 14 Correspondingly, the ball screw transmission mechanism of the clamping module of this invention lacks an anti-relative rotation mechanism.

[0078] Figure 16 Showing from a perspective view Figure 14 The stop bearing gasket of the clamping module of the present invention, and

[0079] Figure 17 Shown from Figure 14 The external view of the clamping module of the present invention. Detailed Implementation

[0080] In the following detailed description of preferred embodiments, for clarity, the same reference numerals denote components that are substantially the same in these embodiments or in the embodiments. However, for better illustration of the invention, the preferred embodiments shown in the figures are not illustrated to scale. For clarity, only elements relevant to the design of the inventive solution are shown here.

[0081] Figure 1 , Figure 9 and Figure 14 This illustrates a possible embodiment of the clamping module 1 of the present invention. The clamping module 1 is particularly suitable for use in an electromechanical braking device 100 of a motor vehicle and includes:

[0082] - Ball screw drive mechanism

[0083] - Piston 7, and

[0084] - Axial bearing 3,

[0085] The ball screw transmission mechanism includes a main shaft 4 and a nut 5.

[0086] The spindle 4 includes a threaded section 42 and a drive section 43.

[0087] Furthermore, the threaded section 42 and the drive section 43 are manufactured as separate components and are securely connected to each other, especially in a manner that prevents relative rotation.

[0088] Brake caliper housing 6 (in Figure 1 (Only partially visible in the middle) is provided for receiving the clamping module 1 and is designed accordingly. In the brake caliper housing 6, the main shaft 4 is supported by the axial bearing 3.

[0089] exist Figure 1 In the clamping module 1, a stop bearing washer 2 is further included, wherein the stop bearing washer is arranged at the axial end of the radial extension of the spindle, particularly at the transition between the threaded section and the drive section, and wherein the axial bearing is arranged on the side of the stop bearing washer opposite to the piston.

[0090] The rotation / translation converter of the clamping module 1 is designed as a ball screw drive mechanism, which has a nut 5, a spindle 4 and balls 11 that can travel in the corresponding grooves of the nut 5 and / or the spindle 4.

[0091] The spindle 4 includes a threaded section 42 with grooves 16 on its outer surface. The spindle 4 also includes a separately manufactured drive section 43 connected to the threaded section 42 in a non-rotatable manner. The drive section 43 includes a piston-side region that, in the axial direction, overlaps with the threaded section 42 and is designed to provide a non-rotatable connection with the threaded section 42. The drive section 43 also includes a drive-side region that protrudes relative to the piston 7 and / or nut 5 on the drive side and passes through the stop bearing washer 2 and the axial bearing 3. This region is guided to the drive unit (not shown).

[0092] In the illustrated embodiment, the clamping module 1 further includes a piston 7. The piston 7 is axially movably arranged relative to the housing 6. The clamping module 1 may include a drive unit (not shown in detail) having a motor and a transmission mechanism designed to generate a drive torque that can be applied to the spindle 4 during operation. For this purpose, the drive section 43 of the spindle 4 is operatively connected to the transmission mechanism. The drive section 43 has a significantly smaller outer diameter than the threaded section 42, thereby allowing the drive section to be easily guided through the stop bearing washer 2 and the axial bearing 3.

[0093] Based on the drive torque of the drive unit, the piston 7 can be displaced axially relative to the housing 6 along its axis of rotation. A nut 5 is provided to transmit a force component to the piston 7 via this axial displacement. In this way, the piston 7 can press the friction lining 15 against the brake disc (not shown) to generate a predetermined braking torque or a predetermined clamping force for the wheel brake in the case of a disc brake.

[0094] In the design shown, the piston 7 is connected to the brake caliper housing 6 via an elastic annular element 8, wherein the elastic annular element 8 is elastically deformable, enabling relative axial displacement between the brake caliper housing 6 and the piston 7.

[0095] exist Figure 1 The bushing 12 and retaining ring 13, as well as the mating washer 14 beside the retaining ring 13, can also be seen. Furthermore, in the illustrated embodiment, an axial retaining ring 10 is provided in the piston 7, which allows the piston to be released in the loosening direction (in...) by means of the nut 5. Figure 1 (From center to right) Actively pull piston 7.

[0096] Figure 2 Shown from Figure 1 The external view of the clamping module 1 of the present invention.

[0097] Figure 3 Showing from a perspective view Figure 1The stop bearing gasket 2 of the clamping module 1 of the present invention is shown, wherein the side facing the piston 7 is shown.

[0098] Figure 4 Showing from a perspective view Figure 1 The driving section 43 of the main shaft 4 of the clamping module 1 of the present invention.

[0099] Figure 5 Showing from a perspective view Figure 1 The threaded section 42 of the main shaft 4 of the clamping module 1 of the present invention.

[0100] In order to withstand large axial loads while achieving a very compact structure in the axial direction, the outer diameter of the threaded section 42 of the spindle 4 is chosen to be relatively large. However, at the same time, the drive section 43 of the spindle 4 is chosen to be quite small so that the stop bearing washer 2 and the axial bearing 3 can be inserted without being significantly weakened by the required through openings in these components.

[0101] Therefore, a spindle 4 is implemented as a two-part unit to achieve cost-optimal manufacturing. Accordingly, the threaded section 42 and the drive section 43 are manufactured as separate components. Then, in a subsequent engagement process, the threaded section 42 and the drive section 43 are securely connected to each other, in particular in a manner that prevents relative rotation. This allows for the selection of the corresponding cost-optimal manufacturing method for the respective sections of the spindle 4.

[0102] To achieve a connection that prevents relative rotation between the threaded section 42 and the drive section 43 of the spindle 4, a form-locking and / or force-locking connection is provided. Alternatively or supplementarily, a material-locking connection may also be used.

[0103] exist Figure 4 In one embodiment, the drive section 43 of the main shaft 4 has an external tooth 61 and a collar 63 formed on the piston side. Figure 5 In the embodiment, the internal tooth portion 62 of the threaded section 42 can be seen, which includes the inner wall portion of the threaded section 42 of the spindle 4 having a through opening.

[0104] In this manner, a spindle 4 can be provided with particular advantage, wherein the outer diameter D of the threaded section 42 of the spindle 4 is... G The outer diameter D of the drive section 43 of the main spindle 4 is significantly larger than that of the spindle 4. A Therefore, for example, a spindle 4 can be provided particularly cost-effectively, wherein the outer diameter D of the drive section 43 of the spindle 4 is... A The outer diameter D of the threaded section 42 of the main spindle 4 G For comparisons, the following relationship applies: D G > 1.3 * D A Preferably D G> 1.5 * D A D is particularly preferred G > 1.7 * D A For the illustrated embodiments, D is applicable, for example. G ≈ 3 * D A .

[0105] Therefore, it is particularly advantageous to form an annular stop surface 17, which can provide a stop for the stop bearing gasket 2.

[0106] For assembly, drive section 43 can be located on the piston side (in... Figure 5 The collar 63 is inserted into the threaded section 42 from the left side until it reaches another stop on the inner wall. In this way, the external and internal teeth can form a locking connection, and the threaded section and the drive section are connected to each other via the teeth. Therefore, torque can be transmitted from the drive section 43 to the threaded section 42 via the teeth.

[0107] Furthermore, according to a particularly preferred embodiment of the invention, a press fit is provided between the external and internal gears. In this way, the drive section 43 and the threaded section 42 of the spindle 4 can also be axially fixed.

[0108] On the side opposite to the external gear 61 of the drive section 43 of the main shaft 4, another form-locking profile 64 is formed. Figure 4 In the embodiment shown, a quincunx profile is illustrated purely by way of example. This profile 64 allows the drive section 43 of the spindle 4 to be connected to the output of the transmission device in order to transmit torque.

[0109] To further assemble the clamping module 1, the clamping module can be embedded in the housing 6, and then the clamping module 1 and the drive section 43 can be axially fixed in the housing by means of the retaining ring 13.

[0110] The clamping module 1 also includes a stop bearing washer 2 and an axial bearing 3. Figure 3 The stop bearing washer 2 of an advantageous embodiment of the invention is shown in oblique view. According to the invention, the stop bearing washer 2 integrates the following functions into a single component in a very compact manner:

[0111] - This component forms the running surface for the rolling elements of the axial bearing 3, or more precisely, the axial bearing 3.

[0112] - This component forms a tangential rotation stop between the main shaft 4 and the nut 5.

[0113] Therefore, according to this embodiment, the stop bearing washer 2 is designed so that it can be at least partially directly inserted into the threaded section 42 of the spindle 4 in the axial direction. Here, the stop bearing washer 2 has a substantially annular shape with a through hole 41 through which the drive section 43 of the spindle 4 can be guided.

[0114] To enable a connection with the spindle 4 that prevents relative rotation, teeth 48 are provided on the end side of the threaded section 42. Figure 3 In the embodiment shown, which has 12 serrated teeth 49, the teeth 48 are preferably as follows: Figure 3 As shown, it is achieved with a large diameter so that a relatively small tangential force can be achieved in the teeth for the torque to be transmitted.

[0115] As in Figure 3 As can be seen, tooth 48 represents the narrowing region of the axial bearing washer 2 and is surrounded by a thicker outer rim. In this way, the thickness of the axial bearing washer 2, and therefore its length, can be kept very small in the axial direction, because a small tangential force can be supported on a very narrow surface. According to a preferred embodiment of the invention, the depth of the tooth (i.e., the extension dimension in the axial direction) can include approximately half the thickness of the axial bearing washer 2. In this way, the component can also withstand greater torsional stress.

[0116] Therefore, the corresponding threaded section 42 of the spindle 4 can have mating teeth or external teeth 51 to achieve a form-locking connection after axial insertion. In this way, the driving torque can be reliably transmitted between the spindle 4 and the stop bearing washer 2.

[0117] In addition, the stop bearing washer 2 is formed with a radially extending shoulder 45, which forms a tangential rotation stop between the stop bearing washer 2 and the nut 5, or more precisely, the anti-relative rotation element 9 that is inserted therein, to prevent relative rotation.

[0118] Figure 6 Shown from Figure 1 An external view of the clamping module of the present invention without the stop bearing washer 2. The external teeth 51, which are the mating contours with the contour of the stop bearing washer 2, are clearly visible. In this embodiment, the external teeth 51 are implemented as hexagonal external teeth on the spindle 4.

[0119] Figure 7 Showing with Figure 6 Correspondingly, the ball screw drive mechanism of the clamping module 1 of the present invention, which does not have a surrounding piston 7, makes the anti-relative rotation mechanism more clearly visible.

[0120] Figure 8 Showing with Figure 5Correspondingly, the ball screw transmission mechanism of the clamping module 1 of the present invention does not have an anti-relative rotation mechanism.

[0121] If from Figure 1 As can be seen, the anti-relative rotation element 9 is arranged between the nut 5 and the section surrounding the piston 7 of the piston 7 and the housing 6.

[0122] The anti-relative rotation element 9 is designed as an annular or substantially annular element. In this way, the anti-relative rotation element can be inserted into the nut 5 in the axial direction. The section provided for this purpose in the nut can be designed to provide a form-locking connection between the anti-relative rotation element 9 and the nut 5, and thus connect them in a manner that prevents relative rotation. Figure 8 In the embodiment shown, a flattened portion 54 is provided for the outer contour of the nut 5. In the example, there are a total of three such flattened portions 54, and one such flattened portion 54 may be sufficient. The inner contour of the anti-relative rotation element 9 is designed to fit precisely and be completely complementary, thereby creating a form-locking connection after assembly.

[0123] The anti-relative rotation element 9 includes a radially extending protrusion 46. The protrusion 46 can be received by the recess 53 of the piston 7, as in... Figure 6 It can be seen in the image.

[0124] In the illustrated embodiment, the protrusion 46 is configured to extend relative to the outer surface of the piston 5 and thus be guided through a corresponding section of the piston 5 so that it can be further guided into the brake caliper housing 6. This enables a particularly compact implementation. Therefore, the protrusion 46 extends relative to the annular portion of the anti-relative-rotation element 9 and relative to the piston 5 such that the protrusion can engage with a recess in the housing 6 (e.g., a precisely fitted, completely complementary groove) and can be axially guided therein. In this way, relative rotation between the nut 5 and the housing is prevented.

[0125] According to the invention, the protrusion 46 further includes a projection or pin-shaped portion 47 at its radial end, the projection or pin having a substantially axial orientation. The pin-shaped portion 47 extends axially relative to the anti-relative rotation element 9, more precisely, the end side of the anti-relative rotation element 9, in a direction opposite to that of the piston. Here, viewed in the radial direction, the pin-shaped portion does not extend beyond the protrusion 46. This allows the following functions to be achieved:

[0126] - The pin-shaped portion 47 forms a structure to prevent relative rotation of the nut 5 within the housing 6. For this purpose, the housing 6 is provided with a groove 21 that is precisely fitted and completely complementary.

[0127] - The pin-shaped portion 47 forms a rotation stop portion, and the stop bearing washer 2, especially the shoulder 45, can tangentially stop at this rotation stop portion. This forms a rear stop for the clamping module 1.

[0128] In the illustrated embodiment, the anti-relative rotation element 9, having the protrusion 46 and the pin-shaped portion 47, is implemented integrally or as a single unit. However, multi-part embodiments are also conceivable and possible, such as embodiments where the pin-shaped portion 47 is designed as a separate pin and inserted into the protrusion.

[0129] Figures 9 to 13 Another embodiment of the clamping module 1 of the present invention is shown.

[0130] Here, Figure 9 A cross-sectional view of another clamping module 1 of the present invention is shown.

[0131] Figure 10 Showing from a perspective view Figure 9 Another driving unit for the spindle of the clamping module 1 of the present invention.

[0132] Figure 11 Showing another oblique view from Figure 9 Another driving unit for the spindle of the clamping module 1 of the present invention.

[0133] Figure 12 Showing from a perspective view Figure 9 Another threaded section of the spindle of the clamping module 1 of the present invention.

[0134] Figure 13 Showing from a perspective view Figure 9 Another fixing element of the clamping module 1 of the present invention.

[0135] In this embodiment of the invention, the drive section 43 and the stop bearing washer 2 are designed as a common component, and an external tooth 61 is designed on one side of the stop bearing washer. In other words, in this embodiment of the invention, the stop bearing washer 2 and the drive section 43 are manufactured as a single, integral component, which can bring cost advantages and stability advantages.

[0136] For fastening and assembly, a retaining ring 18 may be provided, such as... Figure 11 As shown, it is pre-assembled. When the stop bearing washer 2 or the drive section 43 is inserted into the internal tooth 62 of the threaded section 42 of the spindle 4, the retaining ring 18 can engage with the groove on the stop bearing washer. After the stop bearing washer 2 is inserted to the stop portion, the retaining ring 18 clamps. In this way, the stop bearing washer 2 can be axially fixed to the threaded section 42 of the spindle 4, and can be connected via... Figure 1 The toothed portion of the embodiment transmits torque.

[0137] The stop bearing washer 2 and the drive section 43 also include a shoulder 45 with the same function as described above, thereby forming a tangential rotation stop between the stop bearing washer 2 and the nut 5. In addition, the stop bearing washer 2 still forms the running surface of the axial bearing 3.

[0138] In this embodiment, an alternative variant of the anti-relative rotation mechanism for the ball screw drive is shown, which can of course also be used with... Figure 1 Used together with the embodiments.

[0139] exist Figure 9 In this mechanism, a locking element 19 (e.g., a pin or nail) is provided to prevent relative rotation of the ball screw drive mechanism. The locking element 19 is located in... Figure 13 As shown in the diagram. The retaining element 19 can be inserted into the opening 20 in the nut 5, as can be seen from... Figure 12 As can be seen, the nut 5 can thus be axially fixed inside the piston 7. The retaining element 19 can, for example, include a circular segment inserted into a correspondingly precisely fitting, completely complementary opening 20, which is implemented as a hole. Then, the opposite segment of the retaining element 19 can, for example, be inserted into a groove 21 in the housing 6. Thus, the nut 5 can be secured to prevent rotation relative to the housing 6.

[0140] like Figure 12 As shown, the nut 5 also has a lug 22 on its end face as a rotation stop, and the shoulder 45 of the stop bearing washer 2 provides a tangential stop at this rotation stop. This forms a rear stop for the clamping module 1.

[0141] Figures 14 to 17 Another embodiment of the clamping module 1 of the present invention is shown.

[0142] to this end, Figure 14 A cross-sectional view of the clamping module 1 of the present invention according to another embodiment of the present invention is shown.

[0143] Figure 15 Showing with Figure 14 Correspondingly, another embodiment of the clamping module 1 of the present invention, which lacks an anti-relative rotation mechanism, is a ball screw transmission mechanism.

[0144] Figure 16 Showing from a perspective view Figure 14 The stop bearing gasket of another embodiment of the clamping module 1 of the present invention.

[0145] Figure 17 Shown from Figure 14 An external view of another embodiment of the clamping module 1 of the present invention.

[0146] As shown in the first embodiment, the spindle 4 is implemented in two parts: a drive section 43 and a threaded section 42. In this embodiment, the external gear 61 extends in the direction of the drive mechanism, as shown... Figure 15 This is visible in the image. This allows for a form-locking engagement with the stop bearing washer 2. Therefore, as seen from... Figure 16 As can be seen, the stop bearing washer 2 has precisely fitted, completely complementary internal teeth 62 in the through hole. Therefore, the stop bearing washer 2 can be inserted into the external teeth 61 on the drive section 43, as... Figure 17 As shown.

[0147] Therefore, torque can be transmitted via these teeth, and the external teeth 51 of the nut 5 used to transmit torque between the stop bearing washer 2 and the main shaft 4 can be omitted.

[0148] The clamping module 1 according to the invention can be used in particular for electromechanical braking devices, preferably for electromechanically actuated wheel brakes, and especially preferably for electromechanically actuated disc brakes.

[0149] The present invention also includes a motor vehicle that includes at least one such electromechanical braking device.

[0150] List of reference numerals in the attached diagram:

[0151] 1 clamping module

[0152] 2. Stop bearing gaskets

[0153] 3-axis bearings

[0154] 4 spindles

[0155] 5 nuts

[0156] 6 shells

[0157] 7 Pistons

[0158] 8 ring elements

[0159] 9 Anti-relative rotation elements

[0160] 10 fixing rings

[0161] 11 ball bearings

[0162] 12 bushings

[0163] 13 fixed rings

[0164] 14 Matching gaskets

[0165] 15 Friction Liners

[0166] 16 grooves

[0167] 17 stops

[0168] 18 fixing rings

[0169] 19 Fixed Components

[0170] 20 opening

[0171] 21 grooves

[0172] 22 protruding ears

[0173] 41 through hole

[0174] 42 thread section

[0175] 43 drive section

[0176] 45 shoulder

[0177] 46 protrusions

[0178] 47 pin-shaped part

[0179] 48 teeth

[0180] 49 teeth

[0181] 51 External teeth

[0182] 53 notch

[0183] 54 flattened part

[0184] 61 External teeth

[0185] 62 Internal teeth

[0186] 63 rings

[0187] 64 outlines

[0188] 100 braking device.

Claims

1. A clamping module (1), in particular for an electromechanical brake device (100) of a motor vehicle, The clamping module comprises: - a ball screw drive, - a piston (7), and - an axial bearing (3), wherein the ball screw drive comprises a spindle (4) and a nut (5), wherein the spindle (4) comprises a threaded section (42) and a drive section (43), wherein the threaded section (42) and the drive section (43) are manufactured as separate components and are connected to one another fixedly, in particular in a rotationally fixed manner.

2. Clamping module (1) according to claim 1, characterized in that The spindle (4) is supported in the housing (6) by the axial bearing (3).

3. Clamping module (1) according to any one of the preceding claims, characterized in that A stop bearing washer (2) is also provided, wherein the stop bearing washer (2) is arranged on an axial end of a radial expansion of the spindle (4), in particular at a transition between the threaded section (42) and the drive section (43), wherein the axial bearing (3) is arranged on the side of the stop bearing washer (2) opposite the piston (7).

4. Clamping module (1) according to any one of the preceding claims, characterized in that The stop bearing washer (2) and the drive section (43) are designed as one-piece, integral components.

5. Clamping module (1) according to any one of the preceding claims, characterized in that The threaded section (42) and the drive section (43) of the spindle (4) are connected to one another form-lockingly, wherein, preferably, the threaded section (42) comprises an inner toothing (62) on the region of its drive side, and / or, preferably, the drive section (43) comprises an outer toothing (61) on the region of its piston side.

6. Clamping module (1) according to any one of the preceding claims, characterized in that The threaded section (42) and the drive section (43) of the spindle (4) are connected to one another force-lockingly.

7. Clamping module (1) according to any one of the preceding claims, characterized in that The threaded section (42) and the drive section (43) of the spindle (4) are connected to one another materially.

8. Clamping module (1) according to any one of the preceding claims, characterized in that The stop bearing washer (2) comprises an inner toothing (62).

9. Clamping module (1) according to any one of the preceding claims, characterized in that The inner toothing (62) of the threaded section (42) and the outer toothing (61) of the drive section (43) and / or the stop bearing washer (2) are formed precisely complementary and in a complete interlocking manner and are in operative connection with one another in the assembled position by means of the toothing.

10. Clamping module (1) according to any one of the preceding claims, characterized in that A press fit is provided between the inner toothing (62) of the threaded section (42) and the outer toothing (63) of the drive section (43) and / or the stop bearing washer (2).

11. Clamping module (1) according to any one of the preceding claims, characterized in that The drive section (43) has a smaller outer diameter than the threaded section (42), so that an annular stop (44) is formed, which provides a piston-side stop face for the stop bearing washer (2).

12. Clamping module (1) according to any one of the preceding claims, characterized in that the outer diameter D of the threaded section of the spindle G the outer diameter D of the drive section of the spindle A , the following relationship applies: D G > 1.3 * D A , preferably D G > 1.5 * D A , particularly preferably D G > 1.7 * D A .

13. Clamping module (1) according to any one of the preceding claims, characterized in that A form-locking securing element (19) is provided to prevent rotation of the ball screw drive.

14. Clamping module (1) according to any one of the preceding claims, characterized in that A rotation-preventing element (9) is provided, which is preferably designed as an annulus.

15. Clamping module (1) according to claim 14, characterized in that The rotation-preventing element (9) comprises a radially protruding projection (46), which is received by a recess (53) of the piston (7).

16. An electromechanical brake device (100), preferably an electromechanically actuatable disc brake, comprising a clamping module (1) according to any one of the preceding claims and an electric machine connected to the spindle (4) to drive the spindle (4).

17. A motor vehicle comprising at least one electromechanical brake device (100) according to claim 16.

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