Braking system with improved fastness and mechanical strength

Abstract

The present invention relates to a clamping device for a braking system configured to effect relative movement between friction elements using an electric actuator, comprising a conversion mechanism (15) that includes a nut connected to a screw (17) by a plurality of balls to convert the rotational movement of the output shaft of the electric actuator into a translational movement of the ball screw type, and a decoupling mechanism (19) in the radial and / or tangential direction of a stopper (11) configured to receive a friction element with respect to the free end (17a) of the screw (17) of the conversion mechanism (15) in order to improve the mechanical strength of the conversion mechanism (15).

Description

Technical Field

[0001] The present invention relates to the field of braking systems for vehicles, particularly electro-mechanical types of braking systems.

Background Art

[0002] The braking system of a vehicle, particularly an automobile, generally includes a mechanical clamping device having a friction element such as a brake pad connected to an actuator. The actuator brings a pair of friction elements closer to opposite surfaces of a disk coupled to a wheel of the vehicle to clamp the disk, thereby braking the vehicle by the friction of the friction elements against the disk, or the friction elements can be separated to stop the braking.

[0003] In the case of an electro-mechanical type of braking system, the mechanical clamping device includes at least one electric actuator such as a motor having a rotary output shaft. As a result, these electro-mechanical type of mechanical clamping devices need to be provided with a mechanism for converting the rotary motion of the output shaft of the electric actuator into the translational motion required for the approach of the friction elements. Thereby, the friction elements become even more complicated than those of the hydraulic type.

[0004] Furthermore, as the braking system is used, the friction elements are worn away by the friction against the disk. Therefore, the stroke of the conversion mechanism must take into account such distance variations, i.e., the decrease in the thickness of the friction elements, as they wear.

[0005] Furthermore, during braking, particularly in the movement of the friction elements imposed by the inertia of the vehicle, strong tangential stresses are induced by the disk. Therefore, the ends of the conversion mechanism must likewise be dimensioned to withstand the fatigue strength caused by the repetition of these tangential stresses.

Summary of the Invention

Problems to be Solved by the Invention

[0006] The present invention particularly proposes a clamping device for a braking system that guarantees a reversible operation of clamping and unclamping a disk by means of highly reliable friction elements, i.e., while being oriented so that the axial stress exerted by the end of the conversion mechanism can be reproduced by the movement in both directions, and also having robustness, no failures, and a service life comparable to that of a vehicle.

Means for Solving the Problems

[0007] For this purpose, the present invention is a clamping device for a braking system configured to effect relative movement between friction elements, including an electric actuator configured to supply a clamping force, and a frame that supports a mechanism connected to the electric actuator to enable relative movement between the friction elements along a linear axial direction and convert the rotational movement of the output shaft of the electric actuator into a translational movement. The conversion mechanism is of the ball screw type including a nut connected to a screw by a plurality of balls, and the clamping device includes a radial and / or tangential decoupling mechanism of a stopper configured to receive the friction element with respect to the free end of the screw of the conversion mechanism in order to improve the mechanical strength of the conversion mechanism.

[0008] Advantageously, according to the present invention, the conversion mechanism can reduce the friction between the screw and the nut by using point contact with a plurality of balls. Therefore, it can be seen that it hardly affects the efficiency of the force transmitted by the electric actuator, i.e., there is almost no force absorbed by the conversion mechanism. Furthermore, the screw moves according to a very accurate movement such that surface wear can be ignored. Finally, the rotational movement of the output shaft of the electric actuator converted into a translational movement is completely reversible between the approaching position of the friction element, i.e., the contact position with the so-called disk, and the separated position of the friction element where it does not contact the disk, i.e., the so-called rest position, thus guaranteeing extremely high reliability.

[0009] Furthermore, the decoupling mechanism enables a predetermined oscillation of the stopper with respect to the end of the screw and can limit the stress that can deteriorate the thread of the screw and / or the outer surface of at least one ball and / or the threaded portion of the nut. In fact, at the contact position with the friction element, the screw of the conversion mechanism protrudes maximally with respect to the frame, and any stress directed axially outward in the clamp-unclamp movement generates an eccentric moment along the entire length of the screw, and the stress on the end of the screw closest to the electric actuator with respect to the ball and the nut increases due to the lever phenomenon. This is even more serious in the case where the friction element wears very much.

[0010] Advantageously, according to the present invention, the radial and / or tangential decoupling mechanism reduces and even eliminates any lever phenomenon, corrects any eccentric moment due to the movement of the stopper with respect to the screw, and makes the proportion of non-axial stress transmitted to the ball and the nut of the conversion mechanism negligible. Therefore, deterioration, more generally deformation of various members of the conversion mechanism, is avoided, ensuring excellent robustness, that is, in particular, it can be seen that the clamp device does not need to be replaced during at least the service life of the vehicle.

[0011] The present invention, in a variant embodiment, includes one or more of the following optional features, selected alone or in combination.

[0012] The radial and / or tangential decoupling mechanism includes a sliding pivot connection element between the stopper and the free end of the screw in order to limit the transmission of the radial and / or tangential stress received by the stopper to the ball of the conversion mechanism. Therefore, while limiting the non-axial transmission of stress to the conversion mechanism, to a certain extent, in order to enable the stopper to "follow" the tangential contact stress between the disk and the friction element, it can be seen that a first translational degree of freedom along the tangential direction (perpendicular to the axial direction and substantially parallel to the contact surface of the brake disk) and a rotational degree of freedom centered on the same tangential direction are desired.

[0013] The sliding pivot connection element includes a body, the first end of which cooperates with the seat of the stopper, and the second end of which is fitted into the free end of the screw with a clearance. Therefore, it is this component connected to the stopper that mainly supports the non-axial stress between the disk and the friction element.

[0014] The first end of the sliding pivot connection element has a partially spherical contact surface configured to abut against the bottom of the seat of the stopper, and this bottom has a partially cylindrical concave surface with a circular cross-section oriented to allow tangential translation of the stopper with respect to the sliding pivot connection element.

[0015] The first end of the sliding pivot connection element is blocked to the seat of the stopper using a flange, thereby restricting the rocking of the tangential translation of the stopper with respect to the sliding pivot connection element and allowing only rotation about the axis of the tangential translation of the stopper with respect to the sliding pivot connection element.

[0016] The decoupling mechanism is configured such that the stopper can translate tangentially with respect to the sliding pivot connection element up to 2 millimeters and can rotate about the axis of the tangential translation of the stopper with respect to the sliding pivot connection element up to 2°. Similarly, the decoupling mechanism is configured such that the fitting of the second end with a clearance to the free end of the screw allows the sliding pivot connection element to rotate about the tangential direction with respect to the free end of the screw up to 2 degrees.

[0017] To prevent relative rotation about the axial direction between the stopper and the sliding pivot connection element, the inner wall of the seat of the stopper is asymmetric and is shaped to engage with the peripheral wall of the first end of the sliding pivot connection element. In particular, it can be assumed that at least one tangential planar portion present on the inner wall of the seat is connected to at least one other tangential planar portion present on the peripheral wall of the first end in order to prevent any rotation about the axial clamping / clamp release direction. Of course, the same effect can be obtained if the cross-section of the inner wall of the seat is polygonal and shaped to correspond to the peripheral wall of the first end.

[0018] To prevent relative rotation about the axial direction between the free end of the screw and the sliding pivot connection element, the fit between the second end of the sliding pivot connection element and the free end of the screw is of an asymmetric shape. In particular, it can be assumed that the inner wall of the free end of the screw having a polygonal cross-section is connected to the peripheral wall of the second end having a polygonal cross-section of an engaging shape in order to prevent any rotation about the axial clamping / clamp release direction. Of course, the same effect can be obtained if the cross-section of the inner wall of the free end of the screw is elliptical and shaped to engage with the peripheral wall of the second end.

[0019] The present invention also aims at a vehicle braking system including a set of friction elements configured to cooperate with a disk by friction, the system being characterized in that it includes a clamping device as described above for approaching a pair of friction elements towards opposite faces of the disk to clamp the disk. Preferably, the braking system is of the disk brake type having a floating caliper.

[0020] Furthermore, the present invention aims at a vehicle characterized in that it includes a braking system as described above.

Brief Description of the Drawings

[0021] Other features and advantages of the present invention will become apparent from the following description given by way of example and in no way limiting with respect to the accompanying drawings.

[0022]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Mode for Carrying Out the Invention

[0023] Hereinafter, with respect to directions, the directions shown in the drawings shall be used. In particular, "upper", "lower", "left side", "right side", "above", "below", "forward", and "backward" are generally understood as the directions shown in the drawings. However, the following further distinctions are made:

[0024] - Axial direction A that coincides with the thrust central axis of the friction elements 2a and 2b

[0025] - Radial direction R that passes through the radius of the central plane of the disk 3 and is perpendicular to the axial direction A

[0026] -The tangential direction T perpendicular to the axial direction A due to the friction when the friction elements 2a, 2b approach along the axial direction A and contact the disk 3 coupled to the wheel 5 of the vehicle 4 and rotating along an axis parallel to the axial direction A

[0027] The present invention is applicable to all types of braking systems 1, in particular to vehicles 4 equipped with a tourism-type engine, SUVs ("Sport Utility Vehicule"), motorcycles (in particular motorcycles), airplanes, small trucks, industrial vehicles selected from among "large trucks", - that is, off-road vehicles such as subways, buses, land transportation vehicles (trucks, tractors, trailers), agricultural vehicles or construction vehicles - or to other transportation vehicles or transport vehicles. Further, the present invention is also applicable to vehicles without an engine, such as trailers, semi-trailers or camping trailers in particular.

[0028] The "electromechanical type braking system 1" means any type of braking system 1 including at least one electric actuator 12 configured to bring the friction elements 2a, 2b closer to each other and clamp the disk 3 rotatably coupled to the wheel 5 of the vehicle 4 from the side to brake it.

[0029] In the embodiments of FIGS. 2 to 3, a braking system 1 equipped with a floating caliper type clamping device 7 is used, that is, the frame 8 or the brake includes an electric actuator 12 only on one side, and a yoke 9 fixed to the vehicle 4 and a caliper 10 movable with respect to this yoke 9 and configured to bring the friction element 2b closer when the friction element 2a contacts the disk 3. With such a floating caliper type clamping device 7, the number of electric actuators 12 used can be reduced, thereby enabling further miniaturization.

[0030] Of course, the present invention also applies to a braking system 1 provided with a fixed caliper type clamping device, i.e., a clamping device 7 in which a frame 8 formed from a caliper 10 fixed to a vehicle 4 includes one electric actuator 12 for each of the friction elements 2a, 2b on each side of a disk 3, thereby bringing the friction elements 2a, 2b closer to and into contact with the disk 3 respectively.

[0031] In the embodiments shown in FIGS. 2 to 10, the present invention relates to a clamping device 7 configured to effect relative movement along an axial direction A between friction elements 2a, 2b. A stopper 11 is configured to receive at least one friction element 2a, 2b such as a brake pad, similar to a piston of a hydraulic system. The stopper 11 includes at least one rib 11a that is non-rotatable about the axial direction A and can cooperate with the friction elements 2a, 2b either directly (i.e., without an intermediate part such as an external rib of the friction elements 2a, 2b) or indirectly (i.e., using an intermediate part such as a key between the friction elements 2a, 2b and the stopper 11).

[0032] The clamping device 7 includes a frame 8 that supports an electric actuator 12 configured to supply a clamping force by the stopper 11, and all power members and control members combined to particularly generate an amplitude and an approaching force. The frame 8 also receives a mechanism 15 that converts the rotational movement of the output shaft 13 of the electric actuator 12 into a translational movement along the axial direction A. In the embodiment shown in FIG. 4, the conversion mechanism 15 is connected to the electric actuator 12 using a reduction gear 14. Thus, a relative movement can be obtained between the friction elements 2a, 2b along the substantially straight axial direction A.

[0033] Advantageously, according to the present invention, the conversion mechanism 15 is of the ball screw type. The conversion mechanism 15 mainly includes a nut 16, a screw 17, and a ball 18. The free end 17a of the screw 17 translates along the axial direction A by the external thread of the screw 17 that is connected to the threaded portion of the nut 16 via the ball 18. The rotation of the nut 16 is controlled when the output shaft 13 of the electric actuator 12 transmits the rotation. The screw 17 is also rotationally driven by guiding the ball 18 within the nut 16 while causing the free end 17a of the screw 17 to translate along the axial direction A with respect to the frame 8.

[0034] Advantageously, according to the present invention, the conversion mechanism 15 can reduce the friction between the screw 17 and the nut 16 by using a point contact with the ball 18. Therefore, it can be seen that it hardly affects the efficiency of the force transmission of the electric actuator 12, that is, the force absorbed by the conversion mechanism 15 is almost zero. Also, the screw 17 moves according to a very accurate motion such that surface wear can be ignored. Further, the rotational motion of the output shaft 13 of the electric actuator 12 that is converted into a translational motion along the axial direction A is completely reversible between the approaching position of the friction elements 2a, 2b, i.e., the contact position with the so-called disk 3, and the separating position of the friction elements 2a, 2b, i.e., the rest position shown in FIG. 2 where the friction elements 2a, 2b do not contact the disk 3, thus ensuring a very high reliability. As is known, the translation depending on the distance depending on the wear of the friction elements 2a, 2b, i.e., the thickness, is performed between the contact position and the rest position.

[0035] Advantageously, according to the invention, the clamping device 7 includes a radial and / or tangential decoupling mechanism 19 of the stopper 11 configured to receive the friction elements 2a, 2b with respect to the free end 17a of the screw 17 of the conversion mechanism, in order to improve the mechanical strength of the conversion mechanism. In fact, the decoupling mechanism 19 allows a predetermined rocking of the stopper 11 with respect to the free end 17a of the screw 17, i.e., preferably two degrees of freedom, and can limit the stresses that can deteriorate the thread of the screw 17 and / or the outer surface of at least one ball 18 and / or the threaded portion of the nut 16.

[0036] In fact, at the contact position of the friction elements 2a, 2b where the screw 17 of the conversion mechanism 15 protrudes maximally with respect to the frame 8, all the stresses directed outside the axial direction A of the clamping-unclamping movement generate an eccentric moment along the entire length of the screw 17, and the stresses on the end of the screw 17 closest to the electric actuator 12 with respect to the ball 18 and the nut 16 increase due to the lever phenomenon. This becomes even more serious in cases where the friction elements 2a, 2b are very worn and the lever phenomenon is amplified, resulting in a longer translation distance. The radial, especially tangential, stresses are due to the friction of the friction elements 2a, 2b on the disk 3.

[0037] Advantageously, according to the invention, the radial and / or tangential decoupling mechanism 19 reduces and even eliminates all lever phenomena, corrects any eccentric moments caused by the movement of the stopper 11 with respect to the screw 17, and makes the proportion of non-axial stresses transmitted to the ball 18 and the nut 16 of the conversion mechanism 15 negligible. Therefore, it can be seen that deterioration, more generally deformation, of the various members of the conversion mechanism 15 is avoided, ensuring excellent robustness, i.e., in particular, it is not necessary to replace the clamping device 7 during at least the service life of the vehicle 4.

[0038] The radial and / or tangential decoupling mechanism 19 includes a connecting element 21 and a flange 23. The connecting element 21 preferably forms at least one sliding pivot type connection between the stopper 11 and the free end 17a of the screw 17, thereby restricting the transmission of radial and / or tangential stresses received by the stopper 11 to the ball 18 of the conversion mechanism 15.

[0039] Thus, while restricting the transmission of the stress of the conversion mechanism 15 in the non-axial direction, to some extent, in order to allow the stopper 11 to "follow" in the radial and / or tangential directions of the contact stress between the disk 3 and the friction elements 2a, 2b, a first translational degree of freedom β, -β along the tangential direction T (particularly perpendicular to the axial direction A as shown in FIG. 10) and a rotational degree of freedom α, -α centered on the same tangential direction T (such as shown in FIG. 9) are desired.

[0040] Therefore, the sliding pivot connecting element 21 includes a generally cylindrical elongated body 21a configured to connect the stopper 11 to the free end 17a of the screw 17. As shown in the embodiments of FIGS. 5-6 and FIGS. 9-10, the body 21a includes a first end 20 configured such that the contact surface 20a abuts against the bottom 24c of the seat 24 of the stopper 11. The contact surface 20a is preferably partially spherical, and the bottom 24c of the seat 24 of the stopper 11 preferably has a partially cylindrical concave surface with a circular cross-section oriented to allow the tangential translation β, -β of the stopper 11 with respect to the sliding pivot connecting element 21, and similarly, in particular, to allow rotation α, -α centered on the same tangential direction T as the translation. Thus, it is this connecting element 21 connected to the stopper 11 that mainly supports the non-axial stress between the disk 3 and the friction elements 2a, 2b.

[0041] For the purpose of preventing rotation centered on the radial direction and setting the translations β, -β and the rotations α, -α, the first end 20 of the sliding pivot connection element 21 is blocked to the seat 24 of the stopper 11 using the flange 23. More specifically, the flange 23 generally includes an annular body 23a, the central opening 23d of which receives the body 21a of the connection element 21. The body 23a includes a collar forming an attachment element 23e for the outer surface of a ring 11c consisting of an annular cutout 11b in the stopper 11. It can be seen that the contact surface 20a is held against the bottom 24c of the seat 24 of the stopper 11 by the elastic fitting of the inner diameter of the attachment element 23e to the outer diameter of the ring 11c.

[0042] Preferably, the decoupling mechanism 19 is arranged such that the stopper 11 allows translational movements β, -β in the tangential direction up to 2 millimeters with respect to the sliding pivot connection element 21, i.e., it allows the maximum possible tangential rocking (between β and -β) of the connection element 21 within the opening 23d of the flange 23 by the engagement of the peripheral wall 20b with each translational limiting element 23c of the flange 23.

[0043] Furthermore, the decoupling mechanism 19 is arranged such that the stopper 11 allows rotations α, -α about the translational axis T in the tangential direction up to two times with respect to the sliding pivot connection element 21, i.e., it allows the maximum possible angular rocking (between α and -α) of the connection element 21 in the tangential direction about the tangential axis T within the opening 23d of the flange 23 by the engagement of the rear face 20c with each rotational limiting element 23b of the flange 23. Similarly, the shape of the engagement between the rear face 20c and the rotational limiting element 23b restricts and further prevents the radial rotation of the stopper 11 with respect to the connection element 21, as well as the axial and radial translations, thereby facilitating the translational movements β, -β in the tangential direction.

[0044] Furthermore, in order to prevent relative rotation about the axial direction A between the stopper 11 and the sliding pivot connection element 21, the inner walls 24a, 24b of the seat 24 of the stopper 11 are asymmetric and are shaped to engage with the peripheral wall 20b of the first end 20 of the sliding pivot connection element 21. In the embodiments shown in FIGS. 5-6 and 9-10, the inner wall includes a tangential planar portion, i.e., forms a flat surface shaped to engage the planar portion of the peripheral wall 20b of the connection element 21 to prevent any rotation about the axial direction A of clamping / clamp release. The inner wall includes at least one portion 24a (two parallel portions 24a shown in FIG. 5).

[0045] In the embodiment shown in FIG. 5, the two parallel portions 24a are joined to each other laterally by an arcuate portion 24b to form the inner wall of the seat 24 extending about the bottom 24c. The arcuate portion 24b does not necessarily have a shape that engages the peripheral wall 20b of the connection element 21. This is because these portions are not configured to contact, and as suggested in FIG. 10, it is the translational limiting element 23c of the flange 23 that performs this function. Of course, the same effect can be obtained if the cross-section of the inner wall of the seat 24 is polygonal and shaped to correspond to the peripheral wall 20b of the first end 20.

[0046] As shown in the embodiments of FIGS. 5-7 and 9-10, the body 21a includes a second end 22 configured to be fitted onto the free end 17a of the screw 17 with a gap. More specifically, the contact surface 22a and the peripheral wall 22b of the second end 22 preferably have shapes that engage with the bottom 17c and the inner wall 17b of the free end 17a of the screw 17, respectively. This prevents relative rotation about the axial direction between the free end 17a of the screw 17 and the sliding pivot connection element 21, while allowing relative rotational movement γ, -γ in the tangential direction and relative rotational movement δ, -δ in the radial direction between the connection element 21 and the screw 17, thereby enabling it to "follow" in particular the sliding pivot connection movement of the first end 20.

[0047] In the embodiments of FIGS. 5-7 and FIGS. 9-10, since the contact surface 22a and the bottom 17c are partially spherical in shape where the convex and concave portions engage with each other, due to the gaps in the fitting, the tangential relative rotations γ, -γ and the radial relative rotations δ, -δ between the connecting element 21 and the screw 17 are made possible to a certain extent. The decoupling mechanism 19 allows the tangential relative rotations γ, -γ and the radial relative rotations δ, -δ between the connecting element 21 and the screw 17 up to two degrees, that is, by locking the peripheral wall 22b of the connecting element 21 to the inner wall 17b of the free end 17a of the screw 17, it is arranged to allow the maximum possible angular oscillations (between γ and -γ and between δ and -δ) of the connecting element 21 about the tangential direction T and the radial direction R respectively.

[0048] Furthermore, the cross-sections of the peripheral wall 22b of the second end 22 and the inner wall 17b of the free end 17a of the screw 17 have an asymmetric engagement shape in order to prevent relative rotation about the axial direction A between the free end 17a of the screw 17 and the sliding pivot connecting element 21. In the embodiments of FIGS. 5-7 and FIGS. 9-10, the cross-sections of the peripheral wall 22b of the second end 22 and the inner wall 17b of the free end 17a of the screw 17 are polygonal (octagonal in FIGS. 5 and 7). Of course, the same effect can be obtained if the cross-section of the inner wall 17b of the free end 17a of the screw 17 is elliptical and engages with the peripheral wall 22b of the second end 22.

[0049] The present invention is not limited to the presented embodiments and modified embodiments, and other embodiments and modified embodiments will be apparent to those skilled in the art. Therefore, the embodiments and modified embodiments can be combined with each other without departing from the scope of the present invention. Without being at all limiting, other geometric shapes of the connecting element 21 and / or the sheet 24, and / or other geometric shapes of the fitting between the free end 17a of the screw 17 and the connecting element 21 are possible, and furthermore, without departing from the scope of the present invention, the sliding pivot connection may be replaced with a fitting with gaps.

Explanation of Reference Numerals

[0050] 1 Brake system 2a Friction element 2b Friction element 3 Disk 4 Vehicle 5 Wheel 7 Clamping device 8 Frame 9 Yoke 10 Caliper 11 Stopper 11a Groove 11b Annular cutout 11c Attachment ring 12 Electric actuator 13 Output shaft 14 Reduction gear 15 Conversion mechanism 16 Nut 17 Screw 17a Free end of the screw 17b Inner wall of the free end of the screw 17c Bottom of the free end of the screw 18 Ball 19 Radial and / or tangential decoupling mechanism 20 First end of the connecting element 20a Contact surface of the first end 20b Peripheral wall of the first end 20c Back surface of the first end 21 Connecting element 21a Body of the connecting element 22 Second end of the connecting element 22a Contact surface of the second end 22b Peripheral wall of the second end 23 Flange 23a Body of the flange 23b Rotation limiting element of the flange 23c Translation limiting element of the flange 23d Opening of the flange 23e Attachment element of the flange 24 Stopper seat 24a Inner wall portion forming a tangential planar portion 24b Arc-shaped inner wall portion 24c Bottom of the stopper seat α Tangential relative rotation between the connecting element and the stopper β Tangential relative translation between the connecting element and the stopper γ Tangential relative rotation between the connecting element and the screw δ Radial relative rotation between the connecting element and the stopper

Claims

1. A clamping device (7) for a braking system (1) configured to perform relative movement between friction elements (2a, 2b), comprising a frame (8) supporting an electric actuator (12) configured to supply a clamping force and a mechanism (15) connected to the electric actuator (12) to convert the rotational motion of the output shaft (13) of the electric actuator (12) into translational motion in order to enable relative movement between the friction elements (2a, 2b) along a linear axial direction (A), wherein the conversion mechanism (15) is of the ball screw type, comprising a nut (16) connected to a screw (17) by a plurality of balls (18), and the clamping device (7) comprising a radial and / or tangential decoupling mechanism (19) of a stopper (11) configured to receive the friction elements (2a, 2b) against the free end (17a) of the screw (17) of the conversion mechanism (15) in order to improve the mechanical strength of the conversion mechanism (15).

2. The clamping device (7) according to claim 1, wherein the radial and / or tangential decoupling mechanism (19) includes a sliding pivot connecting element (21) between the stopper (11) and the free end of the screw (17) to limit the transmission of radial and / or tangential stresses received by the stopper (11) to the ball (18) of the conversion mechanism (15).

3. The clamping device (7) according to claim 2, wherein the sliding pivot connecting element (21) includes a main body (21a), the first end (20) of which cooperates with the seat (24) of the stopper (11), and the second end (22) is fitted with a gap onto the free end (17a) of the screw (17).

4. The clamping device (7) according to claim 3, wherein the first end (20) of the sliding pivot connecting element (21) has a partially spherical contact surface (20a) configured to abut against the bottom (24c) of the sheet (24) of the stopper (11), and the bottom (24c) has a partially cylindrical concave surface with a circular cross-section oriented to allow tangential translation (β, -β) of the stopper (11) relative to the sliding pivot connecting element (21).

5. The clamping device (7) according to claim 4, wherein the first end (20) of the sliding pivot connecting element (21) is blocked by the seat (24) of the stopper (11) using a flange (23) so as to restrict the tangential translation (β, -β) oscillation of the stopper (11) relative to the sliding pivot connecting element (21) and the rotation (α, -α) of the stopper (11) relative to the sliding pivot connecting element (21) about the tangential translation (β, -β) axis (T) of the stopper (11) relative to the sliding pivot connecting element (21).

6. The clamping device (7) according to claim 5, wherein the decoupling mechanism (19) is configured such that the stopper (11) can be translated tangentially (β, -β) up to 2 mm with respect to the sliding pivot connecting element (21), and the stopper (11) can rotate (α, -α) about a tangential translation (β, -β) axis (T) up to 2° with respect to the sliding pivot connecting element (21).

7. The clamping device (7) according to claim 3, wherein the inner walls (24a, 24b) of the sheet (24) of the stopper (11) are asymmetrical and shaped to engage with the peripheral wall (20b) of the first end (20) of the sliding pivot connecting element (21) in order to prevent relative rotation between the stopper (11) and the sliding pivot connecting element (21) about an axial direction (A).

8. The clamping device (7) according to claim 3, wherein the fitting between the second end (22) of the sliding pivot connecting element (21) and the free end (17a) of the screw (17) is shaped to prevent relative rotation about the axial direction (A) between the free end (17a) of the screw (17) and the sliding pivot connecting element (21).

9. A braking system for a vehicle (1) comprising a pair of friction elements (2a, 2b) configured to cooperate with a disc (3) by friction, wherein the braking system comprises at least one clamping device (7) according to claim 1, which brings the pair of friction elements (2a, 2b) closer to opposing sides of the disc (3) to clamp the disc.

10. The braking system (1) according to claim 9, which is a disc brake type having a floating caliper.

11. A vehicle (4) comprising at least one braking system (1) according to claim 9 or 10.

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