• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention proposes a spring (48) which successively comprises a fixing portion (50) of the spring on the disk brake, a rigid branch (B2) connected to the fixing portion (50) by a plastically deformable fold (P1). around a first deformation axis (A1); another rigid branch (B3) connected to the previous rigid branch (B2) by a second plastically deformable fold (P2), and yet another rigid branch (B4) connected to the previous rigid branch (B3) by a third plastically deformable fold (P3) and which cooperates, directly or indirectly, with an associated portion of the braking pad, each rigid branch (B2, B3, B4) being a strip which extends in a plane parallel to the first deformation axis (A1).
    公开号:FR3027080A1
    申请号:FR1459731
    申请日:2014-10-10
    公开日:2016-04-15
    发明作者:Alexandre Foucoin；Didier Montegu；Sandra Merrien
    申请人:Chassis Brakes International BV；
    IPC主号:
    专利说明:

    [0001] BACKGROUND OF THE INVENTION The invention relates to a disc brake of a motor vehicle 1 "resilient return spring of a brake shoe having means for compensating the wear clearance, disc brake and replacement kit . The invention relates in particular to a resilient return spring 10 of a braking shoe comprising means of catching, by plastic deformation, the wear set of a friction lining of the braking shoe. BACKGROUND OF THE INVENTION The invention relates more particularly to a motor vehicle disc brake of the type described and shown in French Patent Application No. 1353423 filed on April 16, 2013 which comprises: a disc of brake which extends in a plane transverse to an axis of axial orientation of rotation of the disc; a fixed support relative to a chassis of the vehicle; at least one braking pad, each of which comprises a friction lining whose transverse friction face cooperates with an associated braking track of the disk, the braking pad being slidably mounted axially in the support between an active front position in which the friction face is in abutment against the associated annular track of the disk, and an inactive rear position in which the friction face is spaced axially from the associated annular track of the disk, a determined set of operation; 3027080 2 - at least one elastic return spring of the braking shoe to its inactive position, which is for example interposed between the braking pad and the support. In a disk brake, the sliding of the braking pads to their active position is controlled by a piston. The two braking pads strongly pinch the disc to slow its rotation. The braking operation is thus an active operation. The braking pads are pushed back to their idle position by the rotating disk. It is therefore a passive operation. However, the disc may not push the brake pads back with enough force to drive them away from the disc. This may for example occur when the sliding of the brake pads is of insufficient quality or seized, or if the design creates "restitution". Although the brake pads are no longer actively squeezed against the disc, each of the annular tracks of this latter nevertheless permanently rubs against the friction lining carried by the associated brake shoe. The friction linings thus undergo premature non-functional wear. In addition, this permanent friction is likely to cause a damaging heating for certain members 25 of the disc brake. This permanent friction also causes the appearance of a residual torque which opposes the rotation of the disc. This increases the consumption of the vehicle, while decreasing the performance of the vehicle. In order to solve these wear and heat-up problems, the aforementioned document proposes a disk brake in which the elastic return spring comprises means for compensating a set of wear of the pad friction lining 3027080. brake which plastically deform when the stroke of the braking pad to its active position is greater than said determined set of operation. For this purpose, the elastic return spring comprises at least one axially oriented section which is elastically deformable by traction between a state of rest and a state of maximum elongation whose value is equal to the determined play of operation, the spring comprising at least one plastically deformable section, under the effect of an axial tensile force, forming said means of catching up the wear play, this plastically deformable section being shaped to be plastically elongated when the travel of the brake shoe up to 'at its active position is greater than the determined set of operation. According to the embodiment proposed in this document, the plastically deformable section is formed by an accordion folding of a section of the blade. The invention aims to improve the design and performance of such elastic return springs.
    [0002] BRIEF SUMMARY OF THE INVENTION For this purpose, the invention proposes a resilient axial return spring of a braking pad, a disk brake, to an inactive position, spring comprising means, catching a game. of friction brake pad lining, which deforms plastically when a stroke of the braking pad in an axial direction of travel, to an active braking position, is greater than a determined set of operation , characterized in that the elastic return spring comprises successively at least: a portion for fixing the resilient return spring on the disc brake; a second rigid branch, a proximal end of which is connected to the fixing portion by a first plastically deformable fold, around a first deformation axis orthogonal to the axial direction of movement of the braking pad and parallel to the plane in which s 'extends the second rigid branch; a third rigid branch whose one proximal end is connected to a distal end of the second rigid branch by a second plastically deformable fold around a second deformation axis parallel to the first deformation axis; a fourth rigid branch, of which a proximal end is connected to a distal end of the third rigid branch by a third plastically deformable fold, around a third deformation axis (A3) parallel to the first deformation axis (A1), and which cooperates, directly or indirectly, with an associated portion of the braking pad; Each rigid branch is a strip which extends generally in a plane parallel to the first deformation axis, the fourth rigid branch is spaced transversely with respect to the fixing portion.
    [0003] According to other characteristics of the spring: the fixing portion comprises a first rigid branch which is a strip which extends in a plane parallel to the first axis of deformation, the proximal end of the second rigid branch is connected to a distal end of the first rigid branch by the first plastically deformable fold; the first rigid branch extends parallel to the axial direction of displacement of the braking pad; each rigid branch is rectilinear; Each rigid branch comprises stiffening means; each elastically deformable fold has an area of weakening of its mechanical properties; Each elastically deformable fold is a bent portion of a strip comprising a window of orientation parallel to the first deformation axis; - The spring is made in one piece by cutting and forming a sheet of material; The spring is made in one piece by cutting, stamping and folding a sheet of metal; - The rigid branches and the folds are made in one piece by cutting stamping and folding a band of constant width; The second rigid branch and the third rigid branch are of substantially equal lengths; in a state before any plastic deformation of the folds, the first rigid branch and the second rigid branch form an angle equal to approximately 14 degrees; In a state before any plastic deformation of the folds, the third rigid branch and the fourth rigid branch form an angle equal to about 19 degrees; in the state of maximum plastic deformation of the folds, the third rigid branch and the fourth rigid branch are substantially aligned; in the state of maximum plastic deformation of the folds, the second rigid branch and the third rigid branch form a substantially straight angle; in the state of maximum plastic deformation of the folds, the first rigid branch and the second rigid branch form a substantially straight angle; the spring is made of a material chosen from a group comprising, in particular, stainless steel, X2CrNbCu21 steel, 304L steel, gold, lead, a synthetic material, a synthetic material reinforced with a polymeric matrix reinforced with natural or synthetic fibers; the spring is made of a material whose elongation at break is between 30 and 60%, whose tensile strength is between 400 MPa and 1000 MPa, and whose elastic limit is between 0.degree. 500 MPa; the spring is made of a material whose elongation at break is between 40 and 60%, whose tensile strength is between 400 MPa and 700 MPa, and whose elastic limit is between 150 and 400 MPa; the spring is made of a material whose elongation at break is between 50 and 60%, whose tensile strength is between 400 MPa and 600 MPa, and whose conventional elastic limit is between 200 and 300 MPa. The invention also proposes a motor vehicle disc brake which comprises: a brake disc which extends in a plane transverse to an axis of axial orientation of rotation of the disc; A fixed support relative to a chassis of the vehicle; at least one braking pad which comprises a friction lining of which a transverse friction face cooperates with an associated braking track of the disk, the braking pad being axially slidably mounted in the fixed support between an active front position in which the friction face is in abutment against the associated annular track of the disk, and an inactive rear position in which the friction face is spaced axially from the associated annular track of the disk, a determined set of operation, characterized in that it comprises at least one elastic return spring of the braking shoe to its inactive position made according to the invention. According to other features of the disc brake: 3027080 7 - the elastic return spring is interposed between the brake pad and the fixed support; - The attachment portion of the elastic return spring on the disc brake is fixed by axial insertion in a slider 5 of axial orientation of the fixed support; the first rigid branch of the elastic return spring is fixed by axial insertion in an axially oriented notch of the fixed support; the braking pad comprises at least one sliding guide lateral lug which is received in an axial slide of the fixed support, and the fixing notch is formed in a bottom of the slide; the braking pad comprises at least one sliding guide lateral lug which is received in an axial slide of the support, and the notch is formed by the slide; - The disk brake comprises a slide which follows the walls of the slide and which is fixed to the fixed support; the first rigid branch of the elastic return spring 20 on the disk brake comprises a stop which is in contact with a face facing the fixed support to block the axial sliding of the elastic return spring in the direction corresponding to the axial displacement of the brake pad to its active braking position.
    [0004] The invention also proposes a replacement kit for a motor vehicle disc brake according to the invention, characterized in that it comprises at least one braking pad and two elastic return springs matched to the braking pad, each of which is realized according to the invention.
    [0005] The replacement kit may further include two springs for mounting the brake pad in the disc brake.
    [0006] BRIEF DESCRIPTION OF THE FIGURES Other features and advantages of the invention will appear on reading the detailed description which follows, for the understanding of which reference will be made to the appended drawings in which: FIG. exploded perspective which represents a disk brake made according to an embodiment of the invention; FIG. 2 is a front view showing the fixed support of the disc brake of FIG. 1 provided with slides for receiving elastic return springs of an associated brake shoe in its inactive position; FIG. 3 is a detail perspective view showing a resilient return spring of the braking shoe according to the invention; - Figure 4 is a view similar to that of Figure 3 according to another perspective angle; FIG. 5A is a side view of the return spring 20 illustrated in FIGS. 3 and 4, in a "new" state that is not deformed elastically or plastically; FIG. 5B is a view similar to that of FIG. 5A, which shows the spring for catching up the game after its maximum plastic deformation and corresponding to a position of the associated active braking shoe tight against the disk; FIG. 5C is a view similar to that of FIG. 5B, which shows the spring for catching up the game after its maximum plastic deformation and corresponding to a position of the associated braking shoe brought back into its inactive position by the elastic return spring; FIG. 6A is a schematic view in section along a horizontal plane passing through the lateral lugs of the braking shoe which represents an elastic return spring and the braking pad 3027080 9 spaced apart from the friction disc by a greater distance than the game Operating ; - Figure 6B is a view similar to that of Figure 6A which shows the brake pad spaced from the friction disc 5 of a wear clearance after having traversed the operating clearance by elastically deforming the elastic return spring relative to at its position shown in Figure 6A; FIG. 6C is a view similar to that of FIG. 6A showing the braking pad in a tight active position against the disk after plastic deformation of the play retrofit spring with respect to FIG. 6B; FIG. 6D is a view similar to that of FIG. 6A in which, with respect to FIG. 6C, the braking pad has been returned to its inactive position by the elastic return spring. FIG. 7A is a diagrammatic perspective view illustrating an alternative design in which each lug of a braking pad is equipped with a "radial" spring; Figure 7B is a sectional detail view of Figure 7A; - Figure 8 is an 8 is a view similar to those of Figures 3 and 4 which illustrates an alternative embodiment of the elastic return spring according to the invention.
    [0007] DETAILED DESCRIPTION OF THE FIGURES In the remainder of the description, elements having an identical structure or similar functions will be designated by the same references.
    [0008] Nonlimiting and without reference to earth gravity, axial, vertical and transverse orientations will be adopted with reference to the triad "A, V, T" of the figures.
    [0009] The axial orientation "A" is directed from back to front, parallel to a "B" axis of rotation of the disk 12. The horizontal plane is defined as being a transverse axial plane.
    [0010] FIG. 1 diagrammatically shows a disc brake 10 of a motor vehicle. This is a disk brake 10 called "floating caliper" or "sliding caliper". In known manner, the disk brake comprises a disk 12 which is rotatably mounted about an axis "B" rotation axially oriented. The disc 12 is secured in rotation with a wheel (not shown) of the motor vehicle. The disc brake 10 comprises a support 14, also called clevis, which is fixedly mounted relative to the chassis (not shown) of the vehicle. The fixed support 14 overlaps a peripheral edge 15 of the disc 12. Two opposing braking pads 18, rear and front (also called inside and outside) are mounted sliding axially in the fixed support 14 on either side of the disc 12. The two rear and front brake shoes 18 have a structure and an arrangement on the fixed support 14 which are symmetrically identical to a median vertical transverse plane. Subsequently, only the rear brake pad 18 will be described, the description being applicable to the braking pad 18 before reversing the forward and reverse directions. The rear brake pad 18 is in the form of a vertical transverse plate 19 friction lining support. The braking pad 18 has a front face 20, which is oriented towards a rear face 22 facing the disk 12 which is in the form of an annular track. The front face 20 carries a friction lining 24 whose transverse face and vertical front friction 25 is adapted to cooperate with the face 22 of the disc 12.
    [0011] Each of the opposite transverse ends of the braking pad 18 comprises a lateral lug 26 which is slidably mounted, with play, in an associated slide 28 of an associated arm of the yoke or fixed support 14.
    [0012] Each slide 28 is axially oriented and has, in section by a vertical and transverse plane orthogonal to the axes A and B, a shape of "C" open transversely to the associated lateral lug 26 of the braking pad 18. The slide 28 is bounded transversely by a bottom 30 of axial orientation and 10 generally vertical. In the example shown in the figures, a slide 32 is interposed transversely between each lateral lug 26 and the associated slide 28. Each slider 32 is formed by a "C" section leaf spring which engages the walls of the associated slider 28. The slide 32 thus has a bottom 34 of vertical and axial orientation which is arranged facing the bottom 30 of the slide 28. The slide 32 allows a determined degree of movement of the braking pad 18 in the fixed support 14 is that is, generally, but not exclusively, an axial sliding movement, and a transverse sliding movement accompanying the rotation of the disc 12, during a braking action. Without departing from the scope of the present invention, and according to a design not shown, each side lug 26 may be equipped with a so-called mounting spring, of the type described and represented in document FR-A1-2.925.636 and illustrated in Figures 7A and 7B. The braking pad 18 is thus slidably mounted in an axial direction, parallel to the axis of rotation B of the disk 12, in the fixed support 14 over an operating stroke between: an active front position in which the face front transverse friction 25 of the friction lining 24 bears against the face 22 facing the disk 12; and an inactive rear position in which the front transverse friction face of the friction lining 24 of the braking pad 18 is spaced axially from the associated face 22 of the disk 12, with a determined operating clearance "J1 ". During a braking operation, the clamping of the braking pads 18, from their inactive position to their active position, is controlled by a brake caliper 36 of the disk brake 10. In known manner, the caliper 36 comprises an arch 38 which extends axially above the fixed support 14 by covering it 15 and two rear wings 40 and 42 which extend radially from the rear end edges and before the arch 38 towards the axis "B". The front wing 42 extends opposite the front brake pad 18, and the rear wing 40 extends opposite the rear braking pad 18. The yoke 36 is here mounted to slide axially relative to the fixed support 14 by means of two parallel guide columns 44, each of which is slidably received in an associated axial bore 45 of the fixed support 14.
    [0013] In known manner, the rear wing 40 of the yoke 36 carries at least one axial piston 46, a transverse front face of support is likely, during a braking operation, to cooperate with the transverse face screw to screw of the rear brake shoe 18 to urge it axially forward, to exert an axial force 30 of clamping the front transverse friction face 25 of the friction lining 24 against the face 22 opposite the disk 12.
    [0014] By reaction, the stirrup 36 slides axially rearwardly and, in a symmetrical manner, the front wing 42 urges the braking pad 18 forward to clamp the rear transverse friction face 25 of the friction pad 24 of the pad braking system 18 5 before bearing against the front face 22 opposite the disk 12. When, after the braking operation, the piston 46 stops to urge the rear brake pad 18, the return of the pads The braking circuit 18, from their active position to their inactive position, is generally caused by the rotation of the disk 12 which "pushes" each braking pad 18 to its inactive position. Nevertheless, in some cases, it has been found that the repulsive force exerted by the disk 12 is not sufficient to push each of the braking pads 18 to its respective inactive position. The friction lining 24 of the braking pads 18 thus continues to rub against the disc 12, while no action of clamping the friction linings of the braking pads by the stirrup 36 is controlled. At the end of a braking operation, to ensure that each braking pad 18 returns to an inactive position, the disk brake 10 is provided with elastic return means of the braking pad 18 to its inactive position. These elastic return means are made in the form of resilient return springs which are interposed between the braking pad 18 and the fixed support 14. The disk brake 10 here comprises four elastic return springs 48, also called springs "spacers "each of which - without limitation - is here arranged between the fixed support 14 and an associated side lug 26 of a braking pad 18.
    [0015] Thus, a braking pad 18, rear or front, is here associated with two resilient return springs 48 each of which cooperates, directly or indirectly, with the plate 19 friction lining door.
    [0016] 3027080 14 will now be described an embodiment of an elastic return spring 48 according to the invention as shown in particular in Figures 3 and 4. Non-limiting, the four springs 48 resilient return 5 are all identical and they are arranged in the same way on the fixed support 14. Only one of these springs 48 resilient return of the rear brake pad 18 will therefore be described in detail later. The elastic return spring 48 is in the form of a metal strip, for example of steel, of rectangular section whose width extends vertically and which is produced for example by cutting, stamping and bending a metal sheet. stainless steel of constant thickness. Referring in particular to Figures 3 and 4, the elastic return spring 48 comprises a first portion 50, said fixing, generally shaped hairpin forming the fixing means of the spring 48 on the fixed support 14. The portion 50 comprises a blade 52 which extends axially from a bend 54 to a free end.
    [0017] The portion 50 comprises a second blade or strip, connected to the blade 52 by the bend 54 forming an elastic hinge, which extends generally axially parallel to the blade 52, and which, in the sense of the invention constitutes a first rigid branch B1 which extends in an axial and vertical plane.
    [0018] The first branch B1 is stiffened by stiffening means consisting of a stamped zone Z1. The blade 52 has an abutment surface 60 of vertical and transverse orientation which is intended to be in axial contact with a face 69 facing the fixed support 14 for axially locking the blade 52, and therefore the spring 48, towards the disc 12.
    [0019] More specifically, the abutment face 60 is here formed by the front face of a boss 58 made in the body of the blade 52, for example by stamping. The boss 58 protrudes transversely in the face of the blade 52 which is opposed to the first rigid leg B1. The boss 58 has an axially elongate shape. The fixing part 50 is inserted axially forward, by its bend 54 forming a hinge, into an associated slide 28 of the fixed support 14.
    [0020] The fastening part design 50 and the slide 28 are such that the fixing portion 50 is mounted flush, or equivalently, to ensure its stability with respect to the fixed support 14, in particular counteracting tilting phenomena. in rotation around the axes A, V and T.
    [0021] For this purpose, the vertical bottom 30 of the slide 28 may be shaped in a groove or axial notch sized to receive, virtually without play, the blade 52. The shape and dimensions of the notch 30 also allow to center vertically the return spring 48 relative to the slide 28. Starting from the fixing portion 50, and more precisely from the first rigid rectilinear branch of axial orientation B1, the elastic return spring 48 is successively extended by three further rectilinear rigid branches B2, B3 and B4 respectively. Each rectilinear rigid branch Bi has a proximal end Bip relative to the fixing portion 50, and a distal end Bid. Thus, the first branch B1 has its proximal end 30 Bip connected to the elbow 54, while its distal end B1d is located axially out of the slide 28 to be connected to the second rigid branch B2.
    [0022] The proximal end B2p of the second rigid branch B2 is connected to the distal end B1 d of the first rigid branch B1 by a first ply P1 plastically deformable around a first deformation axis A1.
    [0023] Like the first branch B1, the second rigid branch B2 is shaped in a strip in the extension of the first rigid branch B1. The first deformation axis A1 is orthogonal to the axial direction A of displacement of the braking pad and it is parallel to the planes in which extend the first rigid branch B1 and the second rigid branch B2. So that the first bend P1 in the form of a bend constitutes a plastically deformable zone, this portion is mechanically weakened, here by means of a window or light F1 which is here a rectangular opening and axial orientation along the Al axis. The invention is not limited to this embodiment of the plastically deformable zone constituting the ply P1, any other means of modifying the mechanical characteristics of the constituent material in this zone to make it plastically deformable at sense of the invention that can be used, such as for example a reduction in the thickness of the material in this area. In the same way, the proximal end B3p of the third rigid branch B3 is connected to the distal end B2d of the second rigid branch B2 by a second plastically deformable fold P2 which is deformable about a second axis of deformation A2 parallel to the first deformation axis A1. The second fold P2 is a bent portion of the web of material having a window F2. Finally, the proximal end B4p of the fourth branch B4 is connected to the distal end B3d of the third rigid branch B3 by a third plastically deformable fold P3 3027080 17 allowing deformation around a third deformation axis A3, parallel to the first deformation axis Al. The third fold P3 comprises a window F3 similar to the windows F1 and F2.
    [0024] The fourth rigid branch B4 is rectilinear and of axial general orientation parallel to the first rigid branch B1, and not limited to, it is extended here by an active lug 62 intended to be connected directly or indirectly to the associated brake shoe 18 .
    [0025] The active tab 62 is here produced by extension of the constituent band Bi branches and extends from the distal end B4d of the fourth rigid branch B4 in a transverse plane orthogonal to the plane of the fourth rigid branch B4.
    [0026] By way of example, the free end portion of the active lug 62 has an axial opening hole 64 capable of enabling it to be fastened to an associated part of the braking pad 18, and for example of its plate 19 of friction. Non-limitingly, each of the branches Bi is here stiffened by a stamped zone Zi formed in the constituent body of each branch Bi. As can be seen in FIGS. 3 and 4, the stamped zone Z4 for stiffening the fourth rigid branch B4 extends into the body of the active tab 62 so that the right-angle elbow 66 connecting them is itself rigidly to ensure, in use, the right-angle conformation between the first rigid leg B4 and the active tab 62. In Figures 3, 4 and 5A, the elastic return spring 48 is shown in a "new" initial state, that is to say before any plastic deformation of the plies Pi. In this state, new or initial, the first branch B1 and the fourth rigid branch B4 are substantially parallel to each other and axially oriented by being arranged at a distance 3027080 18 transverse to each other, that is to say spaced a distance D shown in Figure 5A. By way of nonlimiting example, and as illustrated in the figures, the second and third rigid branches B2 and B3 are of equal length and form between them an acute angle a2, here equal to about fifty-eight degrees. In the same way, the second rigid branch B2 forms with the first rigid branch B1 an obtuse angle α which is here substantially equal to the obtuse angle a3 formed between them by the third rigid branch B3 and the fourth rigid branch B4, here equal to about one hundred and fifty-one degrees. By comparison, and as can be seen more particularly in FIGS. 5A to 5C, in the state of maximum plastic deformation of the elastic return spring 48, the first and fourth rigid branches B1 and B4 are always substantially parallel, of orientation axial and spaced from each other substantially the distance D, while the three plies Pi have been deformed plastically, respectively around the deformation axes Ai.
    [0027] The first angle α1 has closed in such a way that the first section B1 and the second rigid branch B2 form between them an angle whose value α1 is close to a right angle, here equal to about eighty degrees. The angle a2 between the first rigid branch B2 and the second rigid branch B3 has opened in such a way that they form between them an angle whose value is close to a right angle, here equal to about one hundred degrees. Finally, the third angle a3 has been opened in such a way that the third branch B3 and the fourth rigid branch B4 extend axially substantially in the extension of one another with an angle a3 whose value is here close from a flat angle to 180 degrees.
    [0028] By way of example, the thickness of the strip of material is between 0.5 and 0.8 millimeters and the material is a reference stainless steel X2CrNbCu21 or reference 304L (X2CrNi18-9 / X2CrNi19-11). .
    [0029] By way of example, the maximum displacement corresponding to the maximum wear J2 is equal to about 14 millimeters. We will now describe the operation of the outer resilient return spring 48E made according to the invention with reference to Figures 6A to 6D.
    [0030] FIG. 6A shows the braking pad 18 in an inactive position with pronounced wear of the friction lining 24. The braking pad 18 is thus arranged axially behind the disc 12 and the front transverse face of friction 25 the friction lining 24 is at a distance equal to the sum of: - the set clearance "J1" of operation; and - a game "J2" of wear. In the figures, for the purposes of the description, the games "J1, J2" have been exaggerated. The elastic return spring 48, and its elastically deformable portions 20, is then in its rest state. When the braking pad 18 is biased to its active position by the piston 46, it first runs through the path corresponding to the game "J1" determined operation, as shown in Figure 6B.
    [0031] During this first part of the stroke, the braking pad 18 drives the active tab 62 of the elastic return spring 48 and the leg B4 so as to elastically tension the elastic return spring 48 between the fixing portion 50 fixed to the support fixed 14, and the active tab 62 attached to the braking pad 18. The elastically deformable portions of the elastic return spring 48 then reach their maximum elongation state.
    [0032] The folds Pi deform, first elastically, then plastically. The front transverse face of the friction lining 24 of the braking pad 18 is further spaced, with respect to the associated annular face or track of the disk 12, by a distance equal to the wear clearance "J2". The braking pad 18 therefore continues its axial stroke to its active position shown in Figure 6C. During this second part of the race, the elastically deformable parts being no longer able to deform "elastically", the clamping force is transmitted to the plastically deformable folds Pi of the resilient return spring 48. The plastically deformable folds Pi thus undergo a force which tends to cause plastic angular deformations of the folds Pi around the associated deformation axes Ai.
    [0033] The plies Pi are then plastically deformed, the elastic deformations of the plastically deformable parts being negligible with respect to their plastic deformation. When the braking operation ends, the braking pad 18 is returned to its inactive position by the elastically deformable portions 20 which resume their rest state, as shown in FIG. 6D. The braking pad 18 is thus again spaced from the disk 12 by a distance equal to the only set "J1" determined operation; the play "J2" of wear having been absorbed by the plastic deformation of plastically deformable folds Pi. The elastic return spring 48 thus ensures that the braking pad 18 is returned to its inactive position. In addition, the arrangement of plastically deformable folds Pi makes it possible to prevent the clamping force to be exerted by the piston 46 to actuate the braking pad 18 towards its active position to become too high. In addition, maintaining a game "J1" of constant operation between the braking pad 18 in the inactive position and the disk 3027080 21, the response time of the braking system remains constant regardless of the wear of the friction lining 24 For the choice of the material in which an elastic return spring 48 is made, preferably but not limited to, the elongation at break "A", the tensile strength or tensile strength Rm, and the limit conventional elastic Rp0,2 are selected in the following ranges of values: 10 - 30 <A% <60%; preferably 40 <A% <60%; and more preferably 50 <A% <60%, - 400 <Rm <1000 MPa; preferably 400 <Rm <700 MPa; and more preferably 400 <Rm <600 MPa, - 0 <Rp0.2 <500 MPa; preferably 150 <Rp0.2 <400 MPa; and more preferably 200 <Rp0.2 <300 MPa, with 1 MPa = 106 Pa. FIG. 7 schematically shows a spring 100 for mounting the braking pad 18 capable of equipping the lugs 26 with a pad braking device 18 for mounting and guiding the braking pad 18 in the associated axial slides 28 of the fixed support 14, with or without the presence of slides 34. In a known manner, each pad spring 100 comprises a lower branch 102 of sliding which cooperates with a lower horizontal face of the associated slide and which solicits an upper horizontal facet of the lug 26 bearing vertically upwards against an upper face opposite the slide 28. According to the illustrated conformation in FIG. 7, the spring 100 of a shoe is commonly called a "snail spring" and it comprises a branch 104 bearing under a lower horizontal facet of the lug 26 of the braking pad 18, this brancel he 104 forming part of a fastening branch, or clip, 3027080 22 106 which resiliently clips the ear 26 to ensure the fixing of the spring 100 of the shoe on the ear 26. The spring 100 pad also has a curved branch 108 which connects the securing branch 106 to the lower sliding branch 102 by providing mainly the elasticity of the slipper spring 100. At maximum complete wear of the friction lining, the elastic return spring 48 is plastically deformed and, as the used brake shoe 18, it must be replaced.
    [0034] Thus, an assembly or kit for replacing a worn set of brake pads 18 comprises, for each brake shoe, a nine brake pad 18 itself and at least one set of two elastic return springs 48 constituting a pair resilient return springs matched to the associated brake shoe 15. If the braking shoe is of the type equipped with pad mounting springs 100, the replacement kit comprises, for each braking pad, a new pad equipped with its two pad springs 100, one for each of its two radial ears. 26. Depending in particular on the design of the attachment portion 50, the two springs on a brake shoe may be identical and interchangeable, or be a pair of two springs associated and matched to a brake pad 25 before and / or back . The design according to the invention of an elastic return spring is not limited to the main embodiment which has just been described. In particular, it may vary considerably as regards the design of the connecting part, or of connecting the distal end B4d of the fourth rigid branch B4 with the braking pad to act, directly or indirectly, on the latter. this.
    [0035] It can also vary by the design of the fixing part 50. By way of example, FIG. 8 shows schematically an alternative embodiment in which the fixing part 50 is constituted by a similar tab 52. to the tab 62 which is connected to the proximal end Blp of the first rigid branch B1 and which extends in an orthogonal plane to be fixed, for example by riveting, on an associated part of the fixed support 14. 10
    权利要求:
    Claims (30)
    [0001]
    REVENDICATIONS1. Spring (48) resilient axial return of a brake pad (18), a disc brake (12), to an inactive position, spring (48) comprising means for catching a wear clearance (J2) of a friction lining (24) of the braking shoe (18), which deforms plastically when a stroke of the braking shoe in an axial direction of displacement, to an active braking position, is greater at a determined operating clearance (J1), characterized in that the elastic return spring (48) successively comprises at least: - a fixing portion (50) of the elastic return spring (48) on the disc brake (14 ); a second rigid branch (B2) whose proximal end (B2p) is connected to the fixing portion (50) by a first plastically deformable fold (P1) around a first deformation axis (A1) orthogonal to the direction axial (A) movement of the brake pad (18) and parallel to the plane in which extends the second rigid branch (B2); a third rigid branch (B3) whose proximal end (B3p) is connected to a distal end (B2d) of the second rigid branch (B2) by a second plastically deformable fold (P2) around a second deformation axis (A2) parallel to the first deformation axis (A1); a fourth rigid branch (B4), of which a proximal end (B4p) is connected to a distal end (B4d) of the third rigid branch (B3) by a third plastically deformable fold (P3), around a third axis of deformation (A3) parallel to the first deformation axis (A1), and which cooperates, directly or indirectly, with an associated portion of the braking shoe (18); In that each rigid branch (B2, B3, B4) is a band which extends generally in a plane parallel to the first deformation axis (A1), and in that the fourth rigid branch (B4) is spaced apart. transversely (D) relative to the fixing portion (50).
    [0002]
    2. Spring according to claim 1, characterized in that the fastening portion (50) comprises a first rigid branch (B1) which is a strip which extends in a plane parallel to the first deformation axis (A1), and that the proximal end (B2p) of the second rigid branch (B2) is connected to a distal end (Bld) of the first rigid branch (B1) by the first plastically deformable fold (P1).
    [0003]
    3. Spring according to claim 2, characterized in that the first rigid leg (B1) extends parallel to the axial direction (A) of movement of the braking pad.
    [0004]
    4. Spring according to any one of the preceding claims, characterized in that each rigid branch (B1, B2, B3, B4) is rectilinear.
    [0005]
    5. Spring according to any one of the preceding claims, characterized in that each rigid branch (B1, B2, B3, B4) comprises stiffening means (Z1, Z2, Z3).
    [0006]
    6. Spring according to any one of the preceding claims, characterized in that each elastically deformable fold (P1, P2, P3) comprises a zone (F1, F2, F3) 25 of weakening of its mechanical properties).
    [0007]
    7. Spring according to claim 6, characterized in that each elastically deformable fold (P1, P2, P3) is a bent portion of a strip having a window (F1, F2, F3) oriented parallel to the first deformation axis (A1). 30
    [0008]
    8. Spring according to any one of the preceding claims, characterized in that it is made in one piece by cutting and forming a sheet of material. 3027080 26
    [0009]
    9. Spring according to claim 8, characterized in that it is made in one piece by cutting, stamping and folding a metal sheet.
    [0010]
    10. Spring according to any one of the preceding claims, characterized in that the rigid branches (B1, B2, B3, B4) and the folds (P1, P2, P3) are made in one piece by cutting stamping and bending. a band of constant width.
    [0011]
    11. Spring according to any one of the preceding claims, characterized in that the second rigid branch (B2) and the third rigid branch (B3) are of substantially equal length.
    [0012]
    12. Spring according to claim 2, characterized in that, in a state before any plastic deformation of the folds (P1, P2, P3), the first rigid branch (B1) and the second rigid branch (B2) form an angle ( ai) equal to about 14 degrees.
    [0013]
    13. Spring according to claim 12, characterized in that, in a state before any plastic deformation of the folds, the third rigid branch (B3) and the fourth rigid branch (B4) 20 form an angle (a3) equal to about 19 degrees .
    [0014]
    14. Spring according to any one of the preceding claims, characterized in that, in the state of maximum plastic deformation of the folds (P1, P2, P3), the third rigid branch (B3) and the fourth rigid branch (B4). are substantially aligned.
    [0015]
    15. Spring according to any one of the preceding claims, characterized in that, in the state of maximum plastic deformation of the folds (P1, P2, P3), the second rigid branch (B2) and the third rigid branch (B3). form a substantially straight angle (a2).
    [0016]
    16. Spring according to claim 12, characterized in that, in the state of maximum plastic deformation of the folds (P1, 3027080 P2, P3), the first rigid branch (B1) and the second rigid branch (B2) form a angle (ai) substantially straight.
    [0017]
    17. Spring according to any one of the preceding claims, characterized in that it is made of a material 5 selected from a group including in particular stainless steel, X2CrNbCu21 steel, 304L steel, gold lead, a synthetic material, a polymeric matrix synthetic material reinforced with natural or synthetic fibers.
    [0018]
    18. Spring according to any one of the preceding claims, characterized in that it is made of a material whose elongation at break (A%) is between 30 and 60%, whose tensile strength ( Rm) is between 400M Pa and 1000 MPa, and the conventional elastic limit (Rp0,2) is between 0 and 500 MPa. 15
    [0019]
    19. Spring according to the preceding claim, characterized in that it is made of a material whose elongation at break (A%) is between 40 and 60%, whose tensile strength (Rm) is between 400M Pa and 700 MPa, and whose conventional elastic limit (Rp0,2) is between 150 and 400 MPa.
    [0020]
    20. Spring according to the preceding claim, characterized in that it is made of a material whose elongation at break (A%) is between 50 and 60%, whose tensile strength (Rm) is between 400M Pa and 600 MPa, and the conventional elastic limit (Rp0,2) is between 200 and 300 MPa.
    [0021]
    21. A disc brake (10) of a motor vehicle which comprises: a disc (12) of brake which extends in a plane transverse to an axis (A) of axial orientation of rotation of the disc; a support (14) fixed with respect to a chassis of the vehicle; 3027080 28 - at least one braking pad (18) which comprises a friction lining (24) of which a transverse friction face (25) cooperates with an associated braking track (22) of the disk (12), the braking pad (18) being axially slidably mounted in the fixed support (14) between an active front position in which said friction face (25) bears against the associated annular track (22) of the disc (12), and a rear position inactive in which said friction face (25) is spaced axially from said associated annular track of the disk, a set of game (J1) determined operation, characterized in that it comprises at least one spring (48) elastic return from the braking pad (18) to its inoperative position according to any one of claims 1 to 17.
    [0022]
    22. Disk brake according to claim 21, characterized in that the elastic return spring (48) is interposed between the braking pad (18) and the fixed support (14).
    [0023]
    Disc brake (10) according to claim 21, characterized in that the portion (50) for securing the resilient return spring (48) to the disc brake is axially inserted into a slide (28). axial orientation of the fixed support (14).
    [0024]
    Disc brake (10) according to claim 21, taken into account with claim 2, characterized in that the first rigid leg (B1) of the resilient return spring (48) is fixed by axial insertion in a notch ( 30) of axial orientation of the fixed support (14).
    [0025]
    Disc brake (10) according to claim 24, characterized in that said at least one brake pad (18) has at least one sliding guide side lug (26) which is received in a slide (28). axial of the fixed support (14), and in that said fixing notch (30) is formed in a bottom of the slide (28). 3027080 29
    [0026]
    Disc brake (10) according to claim 24, characterized in that the brake shoe (18) has at least one sliding guide lateral lug (26) which is received in an axial slide (28) of the carrier, and in that said notch (30) is formed by the slider (28).
    [0027]
    27. Disc brake (10) according to claim 21, characterized in that it comprises a slide (32) which follows the walls of the slide (28) and which is fixed to the fixed support (14).
    [0028]
    Disc brake (10) according to any one of claims 23 to 26, characterized in that the first rigid leg (B1) of the resilient return spring (48) on the disc brake (12) has a stop (60) which is in contact with a face facing the fixed support (14) to block the axial sliding of the elastic return spring (48) in the direction corresponding to the axial displacement of the braking shoe (18) towards its active braking position.
    [0029]
    29. Replacement kit for a motor vehicle disc brake according to any one of claims 21 to 28, characterized in that it comprises at least one brake pad 20 (18) and two springs (48) elastic return paired with said brake pad (18) each of which is made according to any one of claims 1 to 17.
    [0030]
    30. Replacement kit according to claim 29, characterized in that it further comprises two springs (10C) for mounting the brake shoe in the disc brake.
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    同族专利:
    公开号 | 公开日
    MX2015014315A|2016-08-30|
    EP3006763A1|2016-04-13|
    JP6178376B2|2017-08-09|
    CN105508475A|2016-04-20|
    MX365361B|2019-05-30|
    CN105508475B|2018-10-09|
    FR3027080B1|2018-03-09|
    US10030729B2|2018-07-24|
    EP3006763B1|2020-02-19|
    ES2790585T3|2020-10-28|
    BR102015025142A2|2018-02-14|
    JP2016080170A|2016-05-16|
    US20160102721A1|2016-04-14|
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    法律状态:
    2015-09-28| PLFP| Fee payment|Year of fee payment: 2 |
    2016-04-15| PLSC| Publication of the preliminary search report|Effective date: 20160415 |
    2016-10-24| PLFP| Fee payment|Year of fee payment: 3 |
    2017-09-21| PLFP| Fee payment|Year of fee payment: 4 |
    2017-11-17| CA| Change of address|Effective date: 20171017 |
    2018-09-19| PLFP| Fee payment|Year of fee payment: 5 |
    2019-09-19| PLFP| Fee payment|Year of fee payment: 6 |
    2020-09-17| PLFP| Fee payment|Year of fee payment: 7 |
    2021-09-22| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1459731|2014-10-10|
    FR1459731A|FR3027080B1|2014-10-10|2014-10-10|"ELASTIC RECALL SPRING FOR A BRAKE SKATE HAVING MEANS FOR REAGGING THE WEAR GAME, DISC BRAKE, AND REPLACEMENT KIT"|FR1459731A| FR3027080B1|2014-10-10|2014-10-10|"ELASTIC RECALL SPRING FOR A BRAKE SKATE HAVING MEANS FOR REAGGING THE WEAR GAME, DISC BRAKE, AND REPLACEMENT KIT"|
    BR102015025142-4A| BR102015025142A2|2014-10-10|2015-09-30|RETURN SPRING OF A BRAKE SHOE INCLUDING MEANS OF WEAR OFFSET DISC BRAKE AND REPLACEMENT KIT|
    EP15188554.8A| EP3006763B1|2014-10-10|2015-10-06|Return spring of a brake shoe including wear play compensation means, disk brake and replacement kit|
    ES15188554T| ES2790585T3|2014-10-10|2015-10-06|Elastic return spring of a brake shoe including wear play compensation means, disc brake and replacement kit|
    MX2015014315A| MX365361B|2014-10-10|2015-10-09|Return spring of a brake shoe including wear play compensation means, disk brake and replacement kit.|
    JP2015201360A| JP6178376B2|2014-10-10|2015-10-09|Brake shoe return spring, disc brake, and replacement kit including wear clearance compensation means|
    US14/879,483| US10030729B2|2014-10-10|2015-10-09|Return spring of a brake shoe including wear play compensation means, disk brake and replacement kit|
    CN201510654842.3A| CN105508475B|2014-10-10|2015-10-10|The replacement external member of spring, the disk brake containing spring and disk brake|
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