Improved braking device with movable push head for caliper brake

Abstract

Braking device (5) for a caliper brake, comprising a thrust head (33) cooperating with a piston (7) via elastic members (31) in order to selectively transmit axial forces to the piston (7) during braking. Floating caliper brake comprising at least one such device (5) and corresponding mounting method. Figure for the abstract: Fig. 4

Description

Title of the invention: Improved braking device with movable thrust head for caliper brake Technical field

[0001] The invention relates to the field of caliper brakes, in particular floating caliper brakes for motor vehicles.

[0002] The invention is of particular interest for electrically actuated brakes, in particular fully electric brakes, also called electromechanical brakes (“Electro-Mechanical Brake (EMB)” in English). State of the art

[0003] Floating caliper brakes known in the prior art comprise one or more pistons for exerting a braking force on a disc of a wheel via pads.

[0004] In operation, such a brake is subjected to significant mechanical and thermal stresses, which require a robust drive mechanism capable of withstanding, in particular, multidirectional braking counter-forces. Statement of the invention

[0005] The invention aims to improve prior art caliper brakes, including those with hydraulic actuation.

[0006] To this end, the invention relates to a braking device for a caliper brake, comprising: - a piston having a longitudinal axis, the piston being intended to be moved in translation along the longitudinal axis relative to a body of the caliper, - a thrust head connected to the piston so as to allow movements of the thrust head relative to the piston in a transverse direction, - one or more elastic members extending radially between the piston and the thrust head so as to allow and / or dampen movements of the thrust head in the transverse direction around an equilibrium position relative to the piston and to return the thrust head to the equilibrium position.

[0007] Said transverse direction is preferably perpendicular to said longitudinal axis.

[0008] In one embodiment, one or more of said elastic members form or comprise one or more compression springs, in particular configured to be stressed in at least said transverse direction.

[0009] In particular, one or more of said elastic members may form or comprise one or more spiral springs.

[0010] Preferably, each of said elastic members may comprise turns wound around an axis parallel to the longitudinal axis so as to have a radially internal end which is free.

[0011] In one embodiment: - a first of said elastic members is arranged on a first side of the piston, relative to the longitudinal axis of the piston, so as to exert on the thrust head a return force in a first direction along the transverse direction, - a second of said elastic members is arranged on a second side of the piston, in particular opposite the first side relative to the longitudinal axis of the piston, so as to exert on the thrust head a return force in a second direction along the transverse direction.

[0012] In one embodiment, when the thrust head is in the equilibrium position, each of said elastic members bears on a surface formed by the piston or by a so-called internal part which belongs to the device and which is integral with the piston in translation in the transverse direction.

[0013] Such an internal part may in particular be configured to bear, directly or indirectly, on the piston.

[0014] In one embodiment, when the thrust head is in the equilibrium position, each of said elastic members bears on a surface formed by the thrust head or by a so-called external part which belongs to the device and which is integral with the thrust head in the transverse direction.

[0015] Such an external part may in particular be configured to bear, directly or indirectly, on the thrust head.

[0016] In one embodiment, the device further comprises an elastic ring forming said external part.

[0017] In one embodiment, said elastic ring is configured to be able to exert on one or more of said elastic members a so-called mounting stress capable of releasing the thrust head from a radial load exerted by one or more of said elastic members on the thrust head when the latter is in said equilibrium position.

[0018] In one embodiment, said external part extends circumferentially around the longitudinal axis and, radially, between one or more of said elastic members and a surface formed by the thrust head.

[0019] In one embodiment, one or more of said elastic members are provided with a substance such as grease and / or comprise a material such as polytetrafluoroethylene in order to reduce a coefficient of friction of this or these elastic members, in particular for example between turns when the elastic member(s) form or comprise one or more spiral springs.

[0020] In one embodiment, for each of one or more of said elastic members, this elastic member has at least two surfaces which are configured to rub against each other during its deformation.

[0021] Preferably, these surfaces have a roughness chosen to obtain a determined coefficient of friction, in particular for example increased between turns of a spiral spring.

[0022] In one embodiment, the device further comprises a retaining member configured to connect or secure the piston and the thrust head in translation along the longitudinal axis.

[0023] Preferably, said elastic members are not in contact with the retaining member.

[0024] In other words, it is preferred that the elastic members do not cooperate with the retaining member, that is to say that they are free, floating, relative to the retaining member, both during assembly and in operation.

[0025] The invention also relates to a caliper brake comprising at least one, preferably two, braking devices as defined above.

[0026] In one embodiment, the brake is a floating caliper brake.

[0027] Preferably, the brake comprises at least one electric actuator.

[0028] According to another aspect, the invention also relates to a method of mounting a braking device as defined above.

[0029] The method of the invention preferably comprises a step of arranging the elastic member(s) radially between the piston and the thrust head so that the elastic member(s) exert on the thrust head a force capable of placing it in said equilibrium position relative to the piston.

[0030] Among other advantages, the invention makes it possible to increase the robustness of the piston drive mechanism and to facilitate the assembly of the brake and its mass production.

[0031] The invention as defined in the claims can be implemented in braking devices and / or in brakes as described in the French patent applications filed on July 19, 2023 under the numbers FR2307735 and FR2307736.

[0032] Among other advantages, the invention makes it possible to dissociate, during the braking phase, axial forces, which are exerted perpendicular to the plane of a disc to be braked, and transverse forces which are exerted parallel to the plane of this disc, including tangential forces which result from the driving of friction elements by the rotation of the disc as well as radial and rotational forces of the friction elements which may in particular result from deformation under stress of the caliper. The invention thus makes it possible to dissociate such forces which are exerted on the thrust head, so as to selectively transmit axial forces to the piston drive system, for example to a ball screw system shaft, or to the component interfacing with an internal friction element such as a ball screw. The connection between the piston and the thrust head in fact provides the latter with a kinematic freedom which makes it possible to eliminate, or at least reduce, the transverse forces applied to such a piston, i.e. the forces having at least one component perpendicular to the longitudinal axis.

[0033] Thus, the invention makes it possible to avoid transmitting said transverse forces to the mechanical elements whose operation and / or longevity may be affected by such transverse forces, these mechanical elements being able in particular to comprise a ball screw. Advantageously, the transmission of transverse forces to such mechanical elements may be limited to the elastic constraints of a transverse return element, advantageously tangential, for returning the friction elements to an equilibrium position, typically in the axis of the piston(s).

[0034] According to the invention, the decoupling of the transverse forces exerted on the friction elements until these forces are taken up by the yoke or by a guide spring associated with said yoke, from the residual transverse forces transmitted to the axial thrust mechanism, improves the safety of the brake by increasing the number of possible braking cycles during the operating life of the brake and reduces the operating noise of the brake.

[0035] The invention more generally makes it possible to reduce the size and mass of the brake, in particular by transmitting the forces directly to a force sensor housed in the caliper.

[0036] The invention also makes it possible to facilitate the assembly of the brake and its mass production.

[0037] Other advantages and characteristics of the invention will appear on reading the detailed, non-limiting description which follows. Brief description of the figures

[0038] The following detailed description refers to the accompanying drawings in which: - [Fig.l] is a perspective view of a floating caliper brake according to the invention; - [Fig.2] is a perspective view of a part of a braking device according to a first embodiment of the invention; - [Fig.3] is an axial sectional view of part of the braking device of [Fig.2]; - [Fig.4] is an axial sectional view of part of the braking device of [Fig.2]; - [Fig.5] is a perspective and exploded view of a part of a braking device according to the first embodiment; - [Fig.6] is an axial sectional view of a part of a brake comprising a braking device according to the first embodiment; - [Fig.7] is a view of part of a braking device according to a second embodiment of the invention.

[0039] Common references are used in the various figures to designate identical or similar elements. Detailed description of embodiments

[0040] Figures 1 to 7 include a reference frame defining orthogonal directions D1, D2 and D3.

[0041] [Fig.l] shows a brake 1 according to the invention.

[0042] In a non-limiting manner, the brake 1 is a floating caliper brake intended to be connected to a wheel (not shown) of a motor vehicle (not shown) having an axis of rotation parallel to the direction Dl.

[0043] The brake caliper 1 comprises in this example a solid cast iron body 2 forming bores 3 (only one bore 3 being visible in [Fig.l]) intended to receive columns (not shown) in order to be able to move the caliper relative to a fixed structure (not shown) of the vehicle, in translation in the direction DL

[0044] The brake 1 of [Fig.l] comprises two sub-assemblies 5, also called “braking devices”, which are housed in cavities formed by the body 2 of the caliper.

[0045] In this non-limiting example, each of the subassemblies 5 of the brake 1 of [Fig. 1] comprises a braking device similar to that described below with reference to FIGS. 2 to 7, comprising a piston 7 and a mechanism 8 for driving the piston 7 (see e.g. [Fig. 4] and description further below).

[0046] In a manner known per se, the brake 1 of [Fig. 1] is designed to move pads (not shown) against a disc (not shown) of the wheel, by translation of the pistons of the subassemblies 5 in a direction SI along the direction D1, relative to the body 2 of the caliper, and by translation of the caliper, via the columns, relative to said fixed structure of the vehicle in a direction S2 opposite to the direction SI, so as to exert a braking force on the disc.

[0047] The braking device 5 of the embodiment of FIGS. 2 to 6 will now be described.

[0048] In this embodiment, the device 5 comprises the following components: - said piston 7 (see figures 3 to 6), - a shaft / screw 23 and a nut 24 forming a ball screw system with recirculating balls which forms said mechanism 8 for driving the piston 7 (see figures 2 to 4 and 6), - two springs 31 (see figures 4 to 6), - a retaining plate 32 (see figures 2 to 6), - a thrust head 33 (see figures 2 to 6), - a sealing ring 34 (see [Fig.6]), - a mounting ring 200 (see figures 2 to 6).

[0049] Figures 2 to 6 show the device 5 in an assembled configuration, in which it has a longitudinal axis A1 around which its components extend. The axis A1 is in this example parallel to the direction D1.

[0050] With reference to [Fig. 5], the piston 7 forms in this example a head 63 defining a first axial end of the piston 7 as well as a base 64 defining a second axial end of the piston 7.

[0051] The base 64 of the piston 7 has a generally annular geometry with an axis Al in line with which the head 63 extends.

[0052] The head 63 of the piston 7 forms a surface 110 which extends generally in the directions D2 and D3 and which is configured to come into contact with an axial surface 81 of the thrust head 33 (see figures 3, 4 and 6 and description further below).

[0053] The head 63 of the piston 7 also forms two notches 101 transversely on one side and the other of the piston 7 in the direction D2 (only one notch 101 being visible in [Fig.5]).

[0054] The notches 101 of the piston 7 are configured to each receive a respective one of the springs 31 (see further below).

[0055] Axially opposite the surface 110, the base 64 of the piston 7 forms two circumferential stops 68 (only one stop 68 being visible in [Fig. 5]). The stops 68 are in this example formed transversely on one side and the other of the piston 7 in the direction D2, so as to each form a surface passing through a plane perpendicular to the directions DI and D2, and are configured to cooperate with corresponding surfaces (not shown) of the nut 24 in order to prevent rotation about the axis A1 of the nut 24 relative to the piston 7 during braking (see further below).

[0056] With reference to [Fig. 6], the piston 7 forms a cavity passing through the base 64 and a part of the head 63 so as to open axially on the side of said second end of the piston 7. This cavity is configured to receive one end of the screw 23 of the drive mechanism 8.

[0057] The subassembly comprising the retaining plate 32 and the thrust head 33 will now be described, as well as the assembly of these components with the piston 7.

[0058] With reference to [Fig.5], the plate 32 has a body which has a generally annular geometry extending around the axis A1.

[0059] In this example, the plate 32 forms, radially inwards, four notches 77 which are regularly spaced circumferentially. Radially outwards, the plate 32 forms four hooks 78 which extend axially in the direction of the thrust head 33 and which, circumferentially, are regularly spaced from each other.

[0060] The thrust head 33 is generally in the form of a disc with an axis A1.

[0061] The head 33 forms a radially external surface provided with four grooves 84 which are circumferentially spaced from each other in a regular manner (only two grooves 84 are visible in [Fig.5]) and an annular groove 86.

[0062] The head 33 forms a surface 90 extending generally in a plane parallel to the directions D2 and D3 and which constitutes an end surface of the device 5.

[0063] The head 33 also forms a two-stage cavity which opens axially on the side of the piston 7 (see [Fig.6]). This cavity is delimited axially by said axial surface 81 and, radially, by a surface 82 which delimits its first stage and by a surface 83 which delimits its second stage.

[0064] The surfaces 82 and 83 are cylindrical in this example.

[0065] For information purposes, the thrust head 33 comprises in this example a nitrided steel type “32CDV13” according to the AFNOR standard and is designed to have a mechanical resistance greater than or equal to 1150 MPa and a hardness greater than or equal to 600 HV.

[0066] In this example, the piston 7 comprises the same material as the thrust head 33.

[0067] The plate 32 is configured to be arranged on the head 63 of the piston 7 so that the notches 77 of the plate 32 cooperate with corners formed by the head 63 of the piston 7, in order to secure the plate 32 and the piston 7 in rotation around the axis A1, and so that the hooks 78 of the plate 32 cooperate with the grooves 84 of the thrust head 33 (see [Fig.2]).

[0068] The plate 32 thus makes it possible to connect the piston 7 and the thrust head 33 so as to secure these parts on the one hand in rotation around the axis Al and, on the other hand, in translation along this axis AL.

[0069] The subassembly comprising the springs 31, the thrust head 33 and the piston 7 which are configured to form a transverse force absorption member will now be described with reference to FIGS. 2 to 6.

[0070] In this example, each of the springs 31 is wound in a spiral around a respective axis parallel to the direction D1, so as to have a radially internal end 71 and a radially external end 72 also called a “strand” (see [Fig.5]).

[0071] For information purposes, the springs 31 comprise in this example a stainless steel, for example a steel known under the designation “X10CrNil8-8” (+ C1300), and are designed to have a mechanical resistance of the order of 1300 MPa.

[0072] In a non-limiting manner, each of the springs 31 may comprise four turns and be formed from one or more blades having a section of 0.6 mm by 6 mm.

[0073] In the assembled configuration which is illustrated in particular in Figures 4 and 6, each of the springs 31 is radially interposed between a respective one of the notches 101 of the piston 7 and the ring 200, which matches the surface 82 of the thrust head 33.

[0074] The end 71 of the springs 31 is free. In particular, the end 71 of the springs 31 is not in direct contact with any other component of the device 5.

[0075] The springs 31 thus mutually exert on the piston 7 and the thrust head 33, a force tending to return the thrust head 33 to a position centered on the axis A1, also called the “equilibrium position”, while allowing a transverse displacement of the thrust head 33 relative to the piston 7, in this example in translation along the direction D2.

[0076] More precisely, a first of the springs 31 being arranged on one side of the piston 7 in the direction D2, this first spring 31 makes it possible to exert on the thrust head 33 a return force in a first direction in the direction D2. The second of the springs 31 being arranged on the other side of the piston 7 in the direction D2, this second spring 31 makes it possible to exert on the thrust head 33 a return force in a second direction in the direction D2, the second direction being opposite to the first direction.

[0077] The springs 31 thus make it possible to dampen movements of the thrust head 33 in the direction D2 around the equilibrium position relative to the piston 7 and, in particular at the end of the braking phase, to return the thrust head 33 to the equilibrium position.

[0078] In this particular example, the surface 110 formed by the head 63 of the piston 7 as well as the surface 81 formed by the thrust head 33 are curved and configured to allow sliding following a rotational movement of the thrust head 33 on the piston 7 during braking (see figures 3 and 5).

[0079] In other words, the thrust head 33 is in this example mounted to move according to a floating pivot type connection relative to the piston 7.

[0080] With reference to [Fig.6], the sealing ring 34 comprises in this example a folded bellows structure which defines a radially internal end 121 housed in the groove 86 of the thrust head 33 and a radially external end 122.

[0081] In the example of [Fig.6], the end 122 of the ring 34 has an annular geometry and cooperates with an annular surface of the body 2 which delimits an axial end of a cavity of the body 2 receiving the device 5, the device 5 passing through the body 2 in the direction DI.

[0082] The braking device 5 described above can be assembled to the body of a caliper according to the following configuration.

[0083] In this example, the assembly includes the following additional components, visible in particular in Figures 3 and 4: - a 210 washer, - a 212 roller bearing, - a 214 ball bearing, - an elastic washer 216, - a retaining ring 218.

[0084] In the example of [Fig. 6], the retaining ring 218 is housed in a groove of the body 2 so as to form an axial stop for the elastic washer 216, which is configured to axially press the bearing 214 onto a bearing surface formed by a collar of the nut 24 (see FIGS. 3 and 6) and to stabilize the device and in particular the drive mechanism 8, in particular with regard to vibrations.

[0085] In the configuration of [Fig. 6] and as also illustrated in [Fig. 3], the ring 218, the washer 216 and the bearing 214 extend axially on one side of said collar of the nut 24, while the bearing 212 and the washer 210 extend axially on the other side of this collar. The ring 218 extends radially around and axially at the base 64 of the piston 7, the bearing 214 extends radially around and axially at a first axial end of the nut 24, and the bearing 212 and the washer 210 each extend radially around and axially at a second axial end of the nut 24, the washer 210 being configured to bear axially on the body 2 of the caliper.

[0086] In the configuration of [Fig.6], the end 122 of the ring 34 cooperates with the aforementioned annular surface of the body 2 so as to allow a translation along DI of the ring 34 relative to the body 2.

[0087] The device 5 is configured to allow a translation of the piston 7 and consequently of the thrust head 33 in the direction DI under the action of a rotation around the axis Al of the shaft 23 of the ball screw system.

[0088] To do this, the shaft 23 can be driven in rotation around the axis A1 by a transmission member (not shown) which can comprise one or more toothed wheels.

[0089] In the particular example of [Fig.l] in which the brake 1 comprises two braking devices 5 such as that described above, the transmission member may typically comprise a toothed wheel (not shown) passing through a lateral opening 152 of the body 2 so as to simultaneously drive the shafts 23 of the two devices 5 around the corresponding axis A1. Such a toothed wheel may be driven, for example via a transmission (not shown), by an electric motor (not shown).

[0090] In a non-limiting manner, the brake 1 of [Fig.l] can be used as a service brake.

[0091] In operation, for each of the devices 5 of the brake 1, the piston 7 and the thrust head 33 are moved from a rest configuration as illustrated in [Fig.6] to a deployed configuration (not shown) until the brake pads come into contact with the disc and then a braking force is applied.

[0092] In this example and purely for information purposes, each of the devices 5 is configured so that an input torque of approximately 33 Nm applied to the shaft 23 of the ball screw system can produce a braking force of approximately 35 kN on the disc and, in reaction, a counter-braking force on a sensor (not shown) associated with this device 5.

[0093] During braking, the rotation of the disc exerts transverse forces on the thrust head 33, in particular in the direction D2, which causes a translation of the surface 81 of the thrust head 33 in the direction D2 then, in a phase of increasing force, a pivoting of the surface 81 of the thrust head 33 on the surface 110 of the piston 7. The springs 31 make it possible to take up at least part of these transverse forces without transmitting them to the piston 7, thus decoupling the axial forces and the transverse forces.

[0094] In this example, said sensor of each of the devices 5 is connected to a computer (not shown) in order to transmit to it information, in the form of electrical signals, relating to the axial forces applied to the sensors.

[0095] In this example, the computer is configured to control said electric motor and thus adapt the braking force, and / or one or more other parameters such as a torque or a deceleration, as a function of this information and taking into account a braking instruction.

[0096] At the end of braking, each of the devices 5 of the brake 1 is returned to the rest configuration by reversing the direction of rotation of the motor.

[0097] Such a brake 1 can also be used in a similar manner as a parking brake.

[0098] In this non-limiting example, the springs 31 are mounted by arranging the springs 31 against the notches 101 of the piston 7, by arranging the elastic ring 200 radially outside the subassembly comprising the piston 7 and the springs 31 thus arranged, then by deforming the ring 200 so as to compress the springs 31, sufficiently to be able to insert the thrust head 33 by arranging its surface 82 radially opposite the ring 200.

[0099] With reference to Figures 2 and 5, the ring 200 comprises in this example two fingers 202 extending radially outwardly in order to allow a tool (not shown) to exert on the ring 200 a deformation force tending to bring the fingers 202 closer to each other and thus compress the springs 31.

[0100] In other words, the ring 200 makes it possible to exert on the springs 31 a so-called mounting stress which makes it possible to insert the thrust head 33 in the manner indicated above, this mounting stress in fact releasing the thrust head 33 from any radial load exerted by the springs 33 at the end of the mounting.

[0101] When the thrust head 33 is thus positioned, the deformation force of the ring 200 is eliminated, thus releasing the springs 31 from the mounting constraint which, by restoring the mechanical energy thus stored, press the ring 200 against the surface 82 of the thrust head 33 so as to exert on the latter a force placing it in said equilibrium position relative to the piston 7.

[0102] The preceding description is of course not limiting. Among other variants, the braking device 5 described above may have a different architecture and / or parts which are arranged differently and / or which have other geometric and / or dimensional and / or material characteristics.

[0103] Thus, in a non-limiting manner, said transverse force compensation member may comprise an elastic member as illustrated in [Fig.7].

[0104] The embodiment of [Fig.7] differs from that of figures 2 to 6 in that the ends 72 of the springs 31 are connected to each other to form a single elastic member.

[0105] In other words, the device 5 of [Fig.7] comprises an elastic member forming two spiral springs 31 arranged in the same way as in the device of Figures 2 to 6.

[0106] The description of figures 1 to 6 above applies of course by analogy to the embodiment of [Fig.7].

[0107] The various embodiments described above may have numerous variations, including those which follow.

[0108] In each of the embodiments of Figures 2 to 7, the braking device 5 may be devoid of the ring 200, the latter making it easier to mount but being optional. In the absence of such a member 200, the springs 31 or more generally the elastic member(s) may thus come to bear directly on the thrust head 33.

[0109] According to another variant not shown, compatible with the presence or absence of such a ring 200, one or more parts (not shown) can be interposed radially between one or more of said elastic members and the piston 7.

[0110] In an alternative embodiment, the push head 33 comprises a silicone or rubber material of the “EPDM” type (for “ethylene-propylene-diene monomer”).

[0111] In a variant not shown, the drive mechanism of the piston 7 can be replaced by a conventional drive mechanism, including or not including a ball screw system.

[0112] The drive may further be achieved by means other than a toothed wheel. For example, in an embodiment not shown, the brake may comprise a drive element forming with the drive mechanism 8 a bevel gear, or a worm wheel gear.

[0113] The braking device of the invention may be configured to produce a clamping force different from that indicated above, for example a maximum braking force of 25 kN, or 35 kN, or 45 kN, or even 65 kN.

[0114] For information purposes, said transverse force absorption member can typically be used to absorb transverse forces of 122.4 N, or 176.9 N, or 130.9 N, or even 231.5 N, depending in particular on the configuration of the brake.

[0115] The transmission of axial forces to the sensor, coming from the piston 7, can be achieved by means of one or more parts, including for example a washer and / or a stop.

[0116] In an alternative embodiment, not shown, the device may comprise a piston guide member 7, which may for example form a seal.

[0117] The coefficient of friction of the springs 31 - or more generally of the elastic member(s) forming said transverse force absorption member - can be improved by using a substance such as grease and / or a material such as polytetrafluoroethylene (PTFE).

[0118] The different embodiments described above can be applied to each of the sub-assemblies 5 of the brake 1 of [Fig.l] or to just one of these sub-assemblies 5 or even to a brake comprising a single braking device according to the invention.

[0119] More generally, the invention also covers a brake comprising at least one braking device 5 according to the invention.

[0120] Compared with a brake provided with a single braking device according to the invention, a brake having two braking devices according to the invention typically makes it possible to reduce the forces, in particular transverse forces, applied to each of these devices and, consequently, to withstand greater forces together.

[0121] In the embodiment of [Fig.l], the body 2 of the caliper is in one piece and each of the sub-assemblies 5 can be pre-assembled, at least partially, then inserted into the corresponding cavity of the body 2 by passing it into the space intended to receive the disc and the pads.

[0122] In an alternative embodiment, the body 2 of the caliper is a composite part. In the context of such an alternative, a braking device 5 according to the invention can be inserted, partially or totally preassembled, into a cavity of the body of the caliper from one or other of the ends of the cavity, depending on the geometry of the caliper, the braking device and the method of assembling the body.

[0123] In one embodiment, not shown, the brake comprises a high-efficiency reversible geared motor, associated with a parking locking mechanism for the brake in a braking position. List of cited documents

[0124] - 1: Caliper brake - 2: Caliper body - 3: Bore for column - 5: Braking device - 7: Piston - 8: Piston drive mechanism - 23: Shaft / screw of ball screw system of the drive mechanism - 24: Ball screw system nut of the drive mechanism - 31: Spiral spring - 32: Retaining plate - 33: Push head - 34: Sealing ring - 63: Piston head - 64: Piston base - 68: Circumferential stop of the piston - 71, 72: End of the spiral spring - 77: Notch of the support plate - 78: Support plate hook - 81, 82, 83, 90: Surface of the thrust head - 84: Push head groove - 86: Thrust head throat - 101: Piston notch - 110: Piston surface - 121, 122: End of the sealing ring - 152: Opening the caliper body - 200: Elastic ring - 202: Elastic ring finger - 210: Washer 212: Roller bearing 214: Ball bearing 216: Spring washer 218: Retaining ring Al: Longitudinal axis DI: Axial / longitudinal direction (reference) D2, D3: Transverse direction (reference) SI, S2: Direction of movement

Claims

Claims

1. Braking device (5) for a caliper brake (1), comprising: - a piston (7) having a longitudinal axis (Al), the piston (7) being intended to be moved in translation along the longitudinal axis (Al) relative to a body (2) of the caliper, - a thrust head (33) connected to the piston (7) so as to allow movements of the thrust head (33) relative to the piston (7) in a transverse direction (D2), - one or more elastic members (31) extending radially between the piston (7) and the thrust head (33) so as to allow and / or dampen movements of the thrust head (33) in the transverse direction (D2) around an equilibrium position relative to the piston (7) and to return the thrust head (33) to the equilibrium position.

2. Device (5) according to claim 1, wherein one or more of said elastic members (31) form or comprise one or more compression springs, each of said elastic members (31) preferably comprising turns wound around an axis parallel to the longitudinal axis (Al) so as to have a radially internal end (71) which is free.

3. Device (5) according to claim 1 or 2, wherein: - a first of said elastic members (31) is arranged on a first side of the piston (7), relative to the longitudinal axis (A1) of the piston (7), so as to exert on the thrust head (33) a return force in a first direction along the transverse direction (D2), - a second of said elastic members (31) is arranged on a second side of the piston (7), in particular opposite the first side relative to the longitudinal axis (A1) of the piston (7), so as to exert on the thrust head (33) a return force in a second direction along the transverse direction (D2).

4. Device (5) according to any one of claims 1 to 3, in which, when the pushing head (33) is in the equilibrium position, each of said elastic members (31) is supported on: - a surface (101) formed by the piston (7) or by a so-called internal part which belongs to the device (5) and which is integral with the piston (7) in translation in the transverse direction (D2), and / or - a surface formed by the thrust head (33) or by a so-called external part (200) which belongs to the device (5) and which is integral with the thrust head (33) in the transverse direction (D2).

5. Device (5) according to claim 4, further comprising an elastic ring (200) forming said external part, the elastic ring (200) being configured to be able to exert on one or more of said elastic members (31) a so-called mounting stress capable of releasing the thrust head (33) from a radial load exerted by one or more of said elastic members (31) on the thrust head (33) when the latter is in said equilibrium position.

6. Device (5) according to claim 4 or 5, wherein said external part (200) extends circumferentially around the longitudinal axis (Al) and, radially, between one or more of said elastic members (31) and a surface (82) formed by the thrust head (33).

7. A device (5) according to any one of claims 1 to 6, wherein one or more of said elastic members (31) are provided with a substance such as grease and / or comprise a material such as polytetrafluoroethylene in order to reduce a coefficient of friction of this or these elastic members (31).

8. Device (5) according to any one of claims 1 to 7, wherein, for each of one or more of said elastic members (31), this elastic member has at least two surfaces which are configured to rub against each other during its deformation, these surfaces having a roughness chosen to obtain a determined coefficient of friction.

9. Device (5) according to any one of claims 1 to 8, further comprising a retaining member (32) configured to connect or secure the piston (7) and the thrust head (33) in translation along the longitudinal axis (Al), said elastic members (31) not being in contact with the retaining member (32).

10. Brake (1) with caliper, preferably floating, comprising at least one, preferably two, braking devices (5) according to any one of claims 1 to 9.

11. Method of mounting a braking device (5) according to any one of claims 1 to 9, comprising a step of arranging the elastic member(s) (31) radially between the piston (7) and the thrust head (33) so that the elastic member(s) (31) exert on the thrust head (33) a force capable of placing it in said equilibrium position relative to the piston (7).

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