Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D65/00—Parts or details
  • F16D65/38—Slack adjusters
  • F16D65/40—Slack adjusters mechanical
  • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
  • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
  • F16D65/543—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment comprising a plastically-deformable member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
  • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
  • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
  • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
  • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D65/00—Parts or details
  • F16D65/02—Braking members; Mounting thereof
  • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
  • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
  • F16D65/095—Pivots or supporting members therefor
  • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D65/00—Parts or details
  • F16D65/02—Braking members; Mounting thereof
  • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
  • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
  • F16D65/095—Pivots or supporting members therefor
  • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
  • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
  • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
  • F16D65/0977—Springs made from sheet metal
  • F16D65/0978—Springs made from sheet metal acting on one pad only
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D65/00—Parts or details
  • F16D65/02—Braking members; Mounting thereof
  • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
  • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
  • F16D65/095—Pivots or supporting members therefor
  • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
  • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
  • F16D65/0979—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on the rear side of the pad or an element affixed thereto, e.g. spring clips securing the pad to the brake piston or caliper
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D2125/00—Components of actuators
  • F16D2125/18—Mechanical mechanisms
  • F16D2125/58—Mechanical mechanisms transmitting linear movement
  • F16D2125/582—Flexible element, e.g. spring, other than the main force generating element

Definitions

• Disc brake comprising at least one elastic return spring of a brake pad, elastic return spring, replacement kit and assembly method
• the present invention relates to a disc brake comprising at least one elastic return spring of a brake pad, an elastic return spring and to a method of mounting said elastic return spring.
• the field of the invention is that of braking systems for automobiles.
• the invention proposes an axial elastic return spring of a brake shoe comprising means for taking up, by plastic deformation, the wear clearance of a friction lining of the brake shoe.
• the invention proposes an axial elastic return spring of a brake shoe of a disc brake, from an active position to an inactive position, said spring being intended to be interposed between the brake shoe and a fixed support, said spring.
• spring comprising an elastic deformation portion, a yoke portion arranged to be fixed to the fixed support of the disc brake, and a pad portion.
• the yoke portion comprises a support part and a connecting part comprising at least one connecting ply arranged and configured to bear on an anchoring part of the fixed support, and cooperate with said anchoring part to prevent lifting of the support. said connecting part.
• Motor vehicle disc brakes generally include:
• a brake disc which extends in a plane transverse to the axis of axial orientation of rotation of said disc, an "axial" orientation here meaning an orientation which is parallel to the axis of rotation of the wheel and of the disc ,
• a support called a yoke, fixed relative to a vehicle chassis
• caliper a fixed rotating member, called a caliper, which is held by the yoke and which covers the disc over a portion of its periphery,
• a brake pad each of which comprises a friction lining, one friction face of which cooperates with an associated brake track carried by one of the faces of the disc.
• Such a brake pad is mounted to slide axially, in a housing carried by the yoke, between an active position called “advanced” in which said friction face bears against the associated annular track of the disc, and an inactive position called “retracted”. "Wherein said friction face is axially spaced from said associated annular track of the disc, by a determined operating clearance.
• the two pads of such a pair of brake pads or linings are arranged inside the branches of the caliper, on either side of the disc and facing each other.
• one or more pistons housed in the caliper move towards the disc to apply a clamping force which brings the pads of the same pair closer to each other, which causes them to rub on the pads. friction tracks of the disc and thus slow down its rotation.
• the pads are typically each provided with two lugs which project in a plane parallel to the disc and are arranged in two substantially opposite locations, each lug sliding axially in the housing provided in the yoke.
• the braking operation is thus an operation that can be called “active”, because it is caused by an actuator (the piston).
• the disc does not push back the brake pads with sufficient force to move them away from the disc sufficiently. This can for example occur when the sliding of the brake pads is of insufficient quality, or even seized.
• each of the annular tracks of the latter nevertheless constantly rubs against the friction lining carried by the associated brake shoe.
• the friction linings thus suffer non-functional wear. premature, increasing noise and dust emissions.
• this permanent friction is liable to cause heating which is harmful to certain components of the disc brake.
• This permanent friction also produces a residual torque which opposes the rotation of the disc. This increases the fuel consumption of the vehicle, while reducing its performance.
• document FR 3.004.500 A1 illustrated here in FIGURE 1, proposes a disc brake in which an elastic return spring (48) has a part which deforms plastically when the stroke of the brake pad is greater than the operating clearance. This plastic deformation then modifies the rest position of the pad, thus achieving wear compensation.
• This elastic return spring has the form of a blade folded into several axially oriented parts, and connects the fixed support (14) of the disc brake and one of the brake pads (18). One end of the spring is attached to the edge of the pad. The other end has an axial orientation and slides into a notch in the yoke, in the form of an axially oriented groove, at the bottom of the sliding housing of the pad.
• a fixing part (50) of the spring (48) of elastic return on the fixed support consists of a tab (52) which s 'extends in a plane orthogonal to the direction of axial sliding of the brake pad, and which comprises a through hole so as to fix said spring by riveting on the yoke which constitutes the fixed support.
• the part for fixing the elastic return spring on the fixed support forms a similar fixing tab (52) which is intended to be fixed on an axially oriented pin (350F), force-fitted axially in a complementary hole formed in the fixed support.
• This fixing lug (52) comprises an orifice (53) provided with an internal toothing (366), which deforms elastically when it is mounted by axial engagement on the pin, then axially retains the head of the pin by bracing this internal toothing.
• An object of the invention is also to reduce the residual braking, in duration and / or in intensity, while maintaining or improving the simplicity and reliability of manufacture, maintenance and operation.
• the invention proposes a spring for resilient axial return of a brake pad of a disc brake, from an active braking position to an inactive position.
• the spring is intended to be interposed between the brake shoe and a fixed support of the disc brake.
• Said spring comprises:
• an elastic deformation portion arranged to produce a reaction force when said pad is pressed in the active position, so as to return said brake pad in axial translation to the inactive position
• yoke portion arranged to be fixed to the fixed support of the disc brake, and which is integral with the deformation portion
• the yoke portion comprises a support part having a first support section which:
• the yoke portion includes a connecting portion comprising at least one connecting ply arranged and configured to take bearing on an anchoring part carried by a transverse face of the fixed support and cooperating with said anchoring part to avoid lifting of said connecting part.
• the spring according to the invention makes it possible to move the pad away from the disc as soon as the piston no longer presses on it, and thus to reduce the residual braking in duration and / or in intensity, while facilitating its assembly, by lowering the cost. manufacturing, by simplifying its structure and manufacture, and by improving the optimization compromises in terms of manufacture, assembly and reliability.
• active position of a brake pad is meant a so-called advanced position in which the friction face of said pad bears against the associated annular track of the brake disc.
• inactive position of a brake pad is meant a so-called retracted position taken by the pad when the brake is not actuated and in which said friction face is axially spaced from said associated annular track of the brake disc, a determined operating clearance.
• axial direction is understood to mean, in particular concerning axial sliding or axial support, a direction parallel to the axis of rotation of a brake disc.
• transverse direction is understood to mean (except to refer to the bends of the spring) a direction which is transverse to the axis of rotation and therefore parallel to the plane of the disc and orthogonal to the axis of rotation of this disc.
• a transverse face of the fixed brake support will be a face of this fixed support which is substantially parallel to the plane of the disc, for example by forming an angle of less than 10 ° or 20 ° with this plane.
• radial direction is understood to mean a direction forming a radius of the rotation of the disc around this axis, that is to say passing through the axis of rotation of the disc and perpendicular to this axis, or forming with such a radius a low angle, less than 45 ° or even less than 20 ° or 10 °.
• a tangential direction is defined, at a given point, as a direction tangent to a rotation of this point which would take place around the axis of rotation of the disc, or forming with such a tangent a small angle, of less than 45 ° or even less than 20 ° or 10 °.
• tenon is understood to mean a part or a shape projecting from a given surface, as if to be able to be housed in a groove or a mortise.
• the axial elastic return spring preferably has the shape of an elongated strip, for example rectangular, comprising several transverse folds so as to form the different portions or parts of the spring.
• portion or part of the spring is meant one or more consecutive spring sections within said band; a spring section being delimited by two consecutive folds.
• the elastic deformation portion is an elastic and plastic deformation portion, arranged to undergo an elastic deformation which produces a reaction force when the said braking shoe is pressed, so as to return said braking shoe in translation towards the inactive position, said reaction force being kept substantially constant during the wear of the pad under the effect of plasticization occurring in said spring beyond a determined amplitude of said deformation.
• the reaction force is an elastic return force when the pad is pressed against the brake disc by the caliper piston.
• the elastic and plastic deformation portion thus makes it possible to compensate for the effect of the wear of the lining of the brake pad, and to prevent the return force from being increased under the effect of this wear.
• the connection part comprises a second connection section, a proximal end of which is connected to the first support section by at least one connection fold, the fold axis of which is orthogonal to the axial direction of movement of the brake pad.
• the second connection section extends substantially parallel to the first support section so that it can be inserted under a protuberance of the tenon-shaped anchoring part, and thus prevent lifting by an axial support applied under said protuberance.
• the contact between the connection part of the spring and the anchoring part of the fixed support is substantially linear or surface.
• the protrusion projects in a direction orthogonal, both to the axial direction of movement of the brake pad, and to the bending axis of the spring.
• This arrangement makes it easier to put and maintain the elastic return spring in position.
• connection part comprises at least three connection sections:
• connection section a proximal end of which is connected to the second lateral connection section by a connection bend, the bending axis of which is orthogonal to the axial direction of movement of the brake pad,
• a fourth lateral connection section comprising a distal end, and a proximal end connected to the third section by a connection fold, the fold axis of which is orthogonal to the axial direction of movement of the brake pad.
• the at least three connecting sections and / or the three folds are arranged to form substantially a "U", so that the connecting part can fit over the tenon-shaped anchoring part. , and thus prevent lifting by pinching said tenon.
• the anchoring part has a tenon shape, which may or may not have a protuberance.
• connecting plies may be elastically deformable only, or may be elastically and plastically deformable.
• the second and fourth lateral connection sections are substantially straight and perpendicular to the first support section so as to form a straight "U".
• connection folds in particular those located near the proximal and distal ends of the third connection section, are elastically deformable.
• the second and / or fourth lateral connection sections are inclined or curved such that the distance between the proximal end of the second connection section and the distal end of the fourth connection section is less than the length of the third connection section, so as to present an omega or half omega shape, for example as two symmetrical "S" facing each other.
• This feature allows the base of the tenon-shaped anchoring part to be pinched. This pinching thus produces a lateral support which cooperates with the pinched surfaces, by friction and / or engagement, to provide an anti-lifting axial force.
• connection part comprises lugs projecting towards a side connection section.
• the lateral connection sections have lugs projecting towards the opposite connection section.
• the lugs produce elastic claws intended to hook onto the anchoring part, for example by arching.
• the connecting sections have "U" shaped cutouts so as to produce the lugs. The lugs make it easier to hold the connection part of the spring in position on the anchoring part of the fixed support.
• connection part may comprise a fifth connection section comprising a distal end, and a proximal end connected to the fourth section by a connection fold whose fold axis is orthogonal to the axial direction of movement of the brake pad.
• the fifth connection section makes it possible to bear on the fixed support and to facilitate the clipping of the connection part on the anchoring part of said fixed support, and / or to facilitate the holding in position of the connection part of the spring on the anchoring part of the fixed support.
• the fifth section extends in a direction opposite to that of the first support section, thus facilitating for example clipping of the connection part on the anchoring part.
• the fifth section extends substantially in the direction of the first support section, forming for example a claw facilitating the attachment to the wall of the anchoring part and / or under a protuberance of the latter.
• the latter is produced in a single piece by cutting and forming a sheet or a strip of material, for example by stamping and bending, for example of constant width.
• the spring is made of steel.
• the spring comprises at least one rib arranged across a fold and / or between two consecutive folds.
• the term rib is understood to mean a protrusion in order to locally increase the resistance or the mechanical rigidity.
• the rib can be produced by stamping the spring.
• the invention provides an assembly comprising a brake shoe and an axial elastic return spring according to one or more of the characteristics stated in the first aspect of the invention.
• the pad portion of the axial elastic return spring is fixed to the brake pad in an irremovable manner.
• the spring can be riveted or welded to the brake shoe.
• the spring can also be force-fitted.
• the assembly comprises a brake shoe and two axial elastic return springs matched to said brake shoe.
• the invention proposes a fixed support for the brake caliper of a motor vehicle disc brake, in which the support has an anchoring part in the form of a tenon projecting axially from a bearing face of the fixed support, which is preferably in a plane parallel to the disc.
• a tenon is for example produced in the form of a rib projecting from the bearing face.
• the tenon-shaped anchoring part is integrally molded with said fixed support so that it can be receive and cooperate with the yoke portion of an axial elastic return spring according to the first aspect of the invention, or of the axial elastic return spring of an assembly according to the second aspect of the invention.
• the fixed support has an anchoring part carried by a transverse face of said fixed support and comprises at least one protrusion projecting transversely.
• the protuberance is molded in one piece with said fixed support, so as to be able to receive and cooperate with the yoke portion of an axial elastic return spring according to the first aspect of the invention, or of the axial elastic return spring. of an assembly according to the second aspect of the invention.
• the invention proposes a motor vehicle disc brake comprising:
• At least one brake shoe mounted to slide axially in the fixed support between an active position in which the at least one brake shoe bears against the associated brake track of the brake disc, and an inactive position in which the at least one brake shoe is axially spaced from said brake track by a non-zero operating clearance
• At least one axial elastic return spring in accordance with the first aspect of the invention, mounted removably with respect to the fixed support between the at least one brake pad and the fixed support so as to exert a return force of said at least one brake pad towards its inactive position
• a brake caliper arranged and configured to be held by the fixed support and to act on the at least one brake pad towards its active position.
• the invention proposes a method of mounting at least one axial elastic return spring, according to the second embodiment of said spring of the first aspect of the invention, on a fixed support in accordance with the third aspect of the invention, said method comprising the steps of:
• the invention provides a method of mounting at least one axial elastic return spring, according to the first embodiment of said spring of the first aspect of the invention, on a fixed support comprising an anchoring part provided with a transverse protuberance, in accordance with the third aspect of the invention, said method comprising the steps of:
• FIGURES 1, 2 and 3 are views of various elastic return springs of the prior art:
• FIGURE 1 being an exploded perspective view of a disc brake comprising two springs, each comprising an axially oriented end,
• FIGURE 2 being a perspective view of a spring comprising an end extending in a plane orthogonal to the direction of axial sliding of a brake pad, said end comprising a through hole,
• FIGURE 3 being a perspective view of a spring assembly comprising an end extending in a plane orthogonal to the direction of axial sliding of a brake pad, said end comprising an orifice provided with toothing interior;
• FIGURES 4a and 4b are perspective views of a disc brake comprising two axial elastic return springs, according to a first family of embodiments, arranged on either side of a brake pad, each spring being on the one hand fixed to one end of a brake shoe, and on the other hand connected by interlocking to the fixed brake support:
• FIGURE 4a showing the brake on the wheel side
• FIGURE 4b showing the brake on the chassis side
• FIGURES 5a, 5b, 6a, 6b, 7a, 7b illustrate three embodiments of a fixed brake support, in particular according to the first family of embodiments of springs, each end of the fixed support comprising a part tenon-shaped anchor:
• FIGURE 5 comprising FIGURE 5a and FIGURE 5b
• FIGURE 5a being a perspective view of a fixed support showing a first embodiment of the axially projecting anchoring portion which has a substantially constant cross section along the axial direction,
• FIGURE 5b being a top view of one end of a fixed support showing an anchoring part according to the first embodiment
• FIGURE 6 comprising FIGURE 6a and FIGURE 6b
• FIGURE 6a being a perspective view of a fixed support showing a second embodiment of the anchoring part projecting axially and which has a transverse protuberance from the axial end of the anchoring part,
• FIGURE 6b being a top view of one end of a fixed support showing an anchoring part according to the second embodiment
• FIGURE 7 comprising FIGURE 7a and FIGURE 7b
• FIGURE 7a being a perspective view of a fixed support showing a third embodiment of the anchoring part projecting axially and which has two transverse protrusions opposed from the axial end of the anchoring part,
• FIGURE 7b being a top view of one end of a fixed support showing an anchoring part according to the third embodiment
• FIGURES 8a, 8b, 9a, 9b, 10a, 10b, 11a, 11b, 12a, 12b, 12c, 12d, 13a, 13b, 14a, 14b illustrate seven embodiments of an axial elastic return spring, according to a first family of embodiments of springs, each being arranged to cooperate with one or more fixed supports according to FIGURES 5a, 5b, 6a, 6b, 7a, 7b:
• FIGURES 8a, 9a, 10a, 11a, 12a, 13a, 14a being perspective views of a spring
• FIGURES 8b, 9b, 10b, 11b, 12b, 13b, 14b being side views of a spring, having from right to left: a pad portion, a deformation portion and a clevis portion, the clevis portion comprising a support part and a connecting part,
• FIGURE 8 comprising FIGURE 8a and FIGURE 8b
• FIGURE 8a being a perspective view of a spring according to a first embodiment in which the connection part has the shape of a "U",
• FIGURE 8b being a side view of a spring according to the first embodiment
• FIGURE 9 comprising FIGURE 9a and FIGURE 9b
• FIGURE 9a being a perspective view of a spring according to a second embodiment in which the connection part has the shape of an "R",
• FIGURE 9b being a side view of a spring according to the second embodiment
• FIGURE 10 comprising FIGURE 10a and FIGURE 10b
• FIGURE 10a being a perspective view of a spring according to a third embodiment in which the connection part has the shape of an omega
• FIGURE 10b being a side view of a spring according to the third embodiment
• FIGURE 11 comprising FIGURE l ia and FIGURE 11b
• FIGURE l ia being a perspective view of a spring according to a fourth embodiment in which the connecting part has the shape of an omega and comprises two ribs,
• FIGURE 11b being a side view of a spring according to the fourth embodiment
• FIGURE 12 including FIGURE 12a, FIGURE 12b, FIGURE 12c and FIGURE 12d, - FIGURE 12a being a perspective view of a spring according to a fifth embodiment in which the connection part has the shape of an omega and comprises cut lugs,
• FIGURE 12b being a side view of a spring according to the fifth embodiment
• FIGURE 12c showing an assembly of a connection part of a spring according to FIGURES 12a and 12b with an anchoring part according to FIGURES 5a and 5b,
• FIGURE 12d being a perspective view of a connection part of a spring according to FIGURES 12a and 12b,
• FIGURE 13 comprising FIGURE 13a and FIGURE 13b
• FIGURE 13a being a perspective view of a spring according to a sixth embodiment in which the connection part has the shape of an omega
• FIGURE 13b being a side view of a spring according to the sixth embodiment
• FIGURE 14 comprising FIGURE 14a and FIGURE 14b
• FIGURE 14a being a side view of a spring according to a seventh embodiment in which the connection part has the shape of an omega and comprises an outer casing,
• FIGURE 14b being a side view of a spring according to the seventh embodiment
• FIGURES 15a and 15d are perspective views of a disc brake comprising two axial elastic return springs, according to a second family of embodiments, arranged on either side of a brake pad, each spring being on the one hand fixed to one end of a brake shoe, and on the other hand connected by interlocking to the fixed brake support:
• FIGURE 15a showing the disc brake on the wheel side
• FIGURE 15d showing the disc brake on the chassis side
• FIGURES 15b and 15c are top views of one end of the fixed support according to FIGURE 15a:
• FIGURE 15b being a top view of one end of the fixed support according to FIGURE 15a comprising an anchoring part in the form of a tenon projecting axially and which has a transverse protuberance from the axial end of the part of anchoring, - FIGURE 15c showing an assembly between the anchoring part according to FIGURE 15b with a spring according to a second family of embodiments of springs,
• FIGURES 15e and 15f are views from below of one end of the fixed support according to FIGURE 15d:
• FIGURE 15e showing the fixed support comprising an anchoring part in the form of a tenon projecting axially and which has a transverse protuberance from the axial end of the anchoring part,
• FIGURE 15f showing an assembly between the anchoring part according to FIGURE 15e with a spring according to a second family of embodiments of springs
• FIGURE 16 comprising FIGURE 16a and FIGURE 16b
• FIGURE 16a is a perspective view of the axial elastic return spring, according to the second family of embodiments of springs, being arranged to cooperate with one or more fixed supports according to FIGURES 15b or 15e,
• FIGURE 16b is a side view of the spring according to FIGURE 16a, showing from right to left: a pad portion, a deformation portion and a yoke portion, the yoke portion comprising a support part and a C-shaped connecting part;
• FIGURE 17 is a diagram illustrating the mechanical actions exerted on a spring according to the invention with the yoke and the shoe, in the context of the first family of embodiments,
• FIGURE 18 is a diagram illustrating the mechanical actions exerted on a spring according to the invention with the yoke and the pad, within the framework of the second family of embodiments.
• an “axial” direction A is a direction parallel to this axis.
• the mechanism which clamps the disc occupies a region located on the periphery of the disc and occupies a restricted angular sector.
• a “radial” direction R will thus be a direction which approaches the axis of the disc
• a “tangent” direction T will be a direction which is substantially parallel to the movement of the disc in its zone of contact with the pad.
• transverse direction is understood to mean (except to refer to the bends of the spring), in particular concerning a transverse face of a fixed brake support or a transverse support, a direction parallel to the plane of the disc.
• the tangential direction T and the radial direction R are both transverse directions.
• the three axial, radial and tangential directions are here represented schematically by a trihedron A, R, T.
• FIGURES 4a, 4b, 15a, 15d illustrate a motor vehicle disc brake 100 of the sliding caliper type.
• the disc brake comprises a brake disc (not shown) which is mounted to rotate about an axis of rotation of axial orientation A.
• the brake disc is integral in rotation with a wheel (not shown) of the motor vehicle.
• the disc brake 100 comprises a fixed support 140, also called a yoke, which is mounted fixed relative to the chassis (not shown) of the vehicle.
• the fixed support 140 comprises two pairs of legs intended to span a peripheral sector of the brake disc.
• the fixed support 140 comprises two outer or front legs 142 connected together to form a "U"; and two inner or rear legs 141 interconnected to form a "U” and which are fixed to the suspended part of the frame by two bores. These legs extend substantially radially along the sector of the brake disc.
• Each outer leg 142 is connected to an inner leg 141 by means of an axial beam 143 which spans the periphery of the disc.
• These beams 143 are arranged to receive the stirrup in an axial sliding connection, and here each have a hollow shape (not visible because opening out on the side of the rear legs 141) which is intended to receive a column (not shown) for sliding the l brake caliper.
• the disc brake 100 further comprises two opposing brake pads 118 (FIGURE 4b), called rear and front (also called interior and exterior or also chassis side and wheel side), mounted to slide axially in the fixed support 140 on both sides. other of the brake disc.
• the brake shoe 118 is in the form of a transverse plate serving as a friction lining support.
• the two brake pads 118, rear and front, most often have a structure and a arrangement on the fixed support 140 which are symmetrical to each other around a median transverse plane, generally vertical with respect to the road.
• the fixed support 140 comprises four shoe housings 11 formed in the four legs, on their face vis-à-vis their shoe (two housings are visible in the FIGURES). These housings 11 are arranged and configured to receive a brake pad in a fixed manner in rotation and sliding axially. The pad housings 11 are arranged so as to receive the longitudinal ends of the two brake pads or "ears", and guide them in their axial translation.
• the disc brake 100 comprises a brake caliper 36 comprising two branches intended to span a sector of the brake disc with one branch on each side of the disc.
• the caliper 36 comprises an arch 38 which extends axially above the fixed support 140, covering it and spanning the disc, and two rear 40 and front 42 branches which extend radially from the rear and front ends of the arch 38 towards the axis of rotation of the brake disc.
• the front branch 42 extends opposite the brake shoe 118 before it maintains towards the disc (see FIGURE 4a), and the rear branch 40 extends opposite the rear brake shoe 118 which it maintains towards the disc. disc (see FIGURE 4b).
• the inner or rear branch 40 comprises a piston cylinder arranged and configured to receive an axial brake piston (not visible) slidably mounted and a transverse bearing face of which is arranged opposite the support plate of the brake pad. 118 rear (chassis side).
• the brake piston is arranged to cooperate with said inner brake shoe 118 in order to apply the shoe lining against an inner face of the brake disc, for example but not necessarily under the effect of hydraulic pressure.
• the caliper 36 is here mounted to slide axially with respect to the fixed support 140 by means of two parallel guide columns (represented only by their axis in phantom, see FIGURES 4a and 4b) fixed in two bores of the caliper, and each of which is slidably received in an associated axial bore of a beam 143 of the fixed support 140.
• Each brake shoe 118 is thus mounted to slide in an axial direction, parallel to the axis of rotation of the brake disc, in the fixed support 140 along an operating stroke between: - an active position in which the friction lining of the brake pad is resting against the opposite face of the brake disc, and
• the tightening of the brake pads 118, from their inactive position to their active position, is controlled by a brake caliper 36 of the disc brake 100.
• the axial brake piston axially urges the brake pad towards the disc to exert an axial force to clamp the friction lining resting against the face of the brake disc (FIGURE 4b).
• the caliper 36 slides axially backwards and, symmetrically, the front branch 42 urges the front brake pad 118 (wheel side) to tighten the friction lining of the front brake pad 118 resting against the opposite side of the brake disc (figure 4a).
• the disc brake 100 is equipped with means for resiliently returning the brake pad 118 to its inactive position.
• These elastic return means are produced in the form of elastic return springs which interconnect the brake pad 118 and the fixed support 140.
• the disc brake 100 comprises, by way of nonlimiting example, four axial elastic return springs 1, also called “spreader” springs, of which each - without limitation - is here arranged to interconnect a leg of the fixed support 140 and an associated side lug of a brake pad 118.
• each brake pad 118 rear or front, is here associated with two axial elastic return springs 1, each of which cooperates with the plate forming the back of the pad and which carries the friction lining.
• the four axial elastic return springs of the same brake are of the same overall design and they are arranged in the same way on the fixed support 140.
• the design principle of only one of these axially elastic return springs of the brake shoe 18 will therefore be described here in detail.
• it is entirely planned to mix different types of springs on the same brake for example different versions of springs according to the invention but also springs according to the invention with springs of a known type.
• An axial elastic return spring 1 is in the form of a metal strip, for example steel, of rectangular shape and which for example produced by cutting, stamping and bending a stainless steel sheet of constant thickness. All the material of the axial elastic return spring is of the elasto-plastic type. By way of example, the thickness of the strip of material is between 0.5 and 0.8 millimeter and the material is a stainless steel with reference X2CrNbCu21 or with reference 304L (X2CrNil8-9 / X2CrNil9-l).
• each spring 1 bears against a transverse face, called the axial bearing face 141a, 142a, which is here substantially parallel to the plane of the brake disc.
• each axial elastic return spring comprises, as illustrated by ellipses in phantom in FIGURE 8b:
• a portion of the pad 63 having the form of a fixing lug designed to be fixed to a brake pad or to receive a support from said pad,
• an elastic and plastic deformation portion 65 provided to produce a reaction force during the axial support of said shoe so as to return said brake shoe in translation to the inactive position.
• the pad portion 63 here comprises a through hole so as to be able to fixing said spring on the shoe, for example by riveting on the surface of the plate which forms the back of the shoe and supports the friction lining material.
• the pad portion 63 can also be inserted under a part of the pad forming the return, for example under the plate forming the back of the pad, and thus exert its return force by simple axial support.
• the pad portion 63 is connected to the deformation portion 65 by an elbow, produced by bending in a direction transverse to the spring, so that the angular difference between the yoke portion and the deformation portion is between 60 degrees and 90 degrees.
• the deformation portion 65 is produced by bending so as to present several successive sections interconnected by deformation folds Ci, here four successive sections 66, 67, 68 and 69, see FIGURES 8b, 9b, 10b, 11b , 12b, 13b, 14b and 16b.
• Each section 66, 67, 68 and 69 is preferably rectilinear and substantially rigid (or at least elastic).
• the deformation folds Ci make it possible to achieve the elasticity which induces a sufficient and necessary return action of the brake shoe, and the plasticity makes it possible to accumulate sufficient plastic deformation to follow the wear of the friction lining of the brake shoe .
• the pad portion 63 is rigidly connected to the deformation portion via the proximal end of the first section 66.
• the distal end of the first section 66 is connected to the second section 67.
• the second rigid section 67 is connected to the first rigid section 66 by a first deformable deformation ply C1.
• the first elbow-shaped ply C1 constitutes a zone which can be deformed both elastically and plastically, this portion is weakened mechanically, here by means of a window or light F1 which is here an opening cutout of rectangular shape.
• the third rigid section 68 is connected to the second rigid section 67 by a second elastically and plastically deformable second deformation ply C2, which comprises a window F2 in the strip of material.
• the fourth section 69 is connected to the third rigid section 68 by a third elastically deformable deformation bend C3 and plastically.
• the third fold C3 comprises a window F3 similar to the windows F1 and F2.
• the fourth and here last rigid section 69 is rectilinear and generally axially oriented and is rigidly extended by the yoke portion.
• the maximum plastic displacement corresponding to maximum wear is typically equal to approximately 14 millimeters.
• the maximum displacement corresponds approximately to the maximum wear thickness of a friction lining of a brake pad.
• the elastic return spring and its folds Ci first deform elastically to the yield point of its weakest parts, the folds Ci.
• the elasticity and strength of these folds Ci is chosen and determined so that this elastic stroke corresponds to the desired functional clearance.
• the braking pad 118 When the braking operation ends, the braking pad 118 is returned to its inactive position by the elastically deformable parts which return to their rest state, but in a position which has been brought closer to the disc by the plastic deformation of the folds.
• the brake shoe 118 is then moved away from the brake disc again under the effect of the elastic return of the axial spring 1, but only by a distance equal to the single determined operating clearance.
• the wear clearance having been absorbed by the plastic deformation of the plastically deformable folds Ci.
• the elastic return spring 1 thus makes it possible to guarantee that the brake pad 118 is returned to an inactive position which is always at the same distance from the disc despite the wear of the pad.
• the response time of the brake system remains constant regardless of the wear of the friction lining, as well as the force required to actuate the pads.
• This plastic deformation also makes it possible to prevent the clamping force to be exerted by the brake piston to actuate the brake pad 118 towards its active position from becoming higher when the wear increases.
• the elastic axial return spring 1 is plastically deformed and, like the worn brake shoe, it must be replaced.
• the axial elastic return spring comprises a yoke portion 70 arranged to be fixed on the fixed support 140 of the disc brake.
• the yoke portion 70 comprises a support portion 71 and a connecting portion 72, as illustrated by ellipses in phantom in FIGURE 8b.
• the support portion 71 includes a first support section S1 which:
• connection part 72 comprises at least one connection ply PI arranged and configured to bear on an anchoring part 145 carried by the transverse bearing face 141a, 142a of the fixed support 140.
• the connection part 72 cooperates with the anchoring part to prevent M2 lifting of said spring connection part 1 (see FIGURES 12c, 17 and 18).
• FIGURES 4a to 14b illustrate a first family of embodiments of axial elastic return springs, in which the connection part 72 of the yoke portion 70 surrounds the anchoring part 145 of the yoke 140.
• FIGURE 17 shows in more detail the mode of interaction of the spring with the yoke and with the pad.
• the pad portion 63 shown here is slid under the plate constituting the back of the pad 118, which thus drives it towards the disc without needing to be fixed thereto.
• the pad portion can also be fixed to the top of the pad plate, for example by riveting as illustrated in FIGURE 18.
• the pad portion 63 is driven by the pad 118.
• the support portion 71 bears on the bearing surface 142a of the yoke so to exert an axial bearing force, represented by the arrow Tl.
• the connection part 72 clamps the opposite faces of the tenon of the anchoring part 145 so as to exert a clamping force, represented by the arrows T3, which thus opposes its uplift, represented by the arrow M2.
• this connection part 72 comprises at least three connection sections:
• connection fold PI whose fold axis is orthogonal to the axial direction A of the movement of the brake pad 118, and which rises along a first face of the anchoring part 145;
• connection section S3 a third connection section S3, a proximal end S3p of which is connected to the second section S2 by a connection fold P2, the fold axis of which is orthogonal to the axial direction A of the movement of the pad brake 118, and which extends above the anchoring part 145 and spans the latter;
• a fourth lateral connection section S4 comprising a distal end S4d, and a proximal end S4p connected to the third section S3 by a connecting ply P3 whose bending rate is orthogonal to the axial direction A of the movement of the brake pad 118, and which descends on the other side of the anchoring part 145, along a second face thereof opposite to its first face.
• the three sections S2, S3, S4 and / or the three folds PI, P2, P3 are arranged to form substantially a "U", so that the connecting part 72 can fit on the part.
• anchor 145 in the form of a tenon, and thus prevent M2 lifting (see FIGURE 12c) by pinching T3 of said tenon.
• the connection sections S2, S3, S4 are rigid.
• the folds P2 and P3 are elastically deformable so that the spacing of the side connecting sections S2 and S4 can increase.
• connection part 72 clamps T3 the base of the anchoring part 145 in the form of a tenon in order to prevent M2 lifting of the spring.
• the second S2 and fourth S4 side connecting sections are substantially straight and perpendicular to the first support section S1 so as to form a straight "U".
• the other examples of this family will be described only in their differences.
• the second S2 and fourth S4 lateral connection sections are substantially inclined such that the distance between the proximal end S2p and the distal end S4d is less than the length of the third connection section S3, so that the connecting part has the shape of an omega.
• connection part comprises five connection sections:
• connection section S3 a third connection section S3, a proximal end of which is connected to the first intermediate connection section S2 ',
• FIGURE 13b shows the elastic portion 65 in two different positions, in a manner which applies similarly to all other embodiments.
• the dotted line represents the position at rest before assembly.
• the complete line shows an already deformed position, in which it can be seen that the pad part 63 has an axially offset position, lower in the figure and corresponding to a pad closer to the disc.
• connection portion 72 comprises lateral lugs 73 arranged to project from a lateral connection section S2, S4 towards the opposite lateral connection section.
• the lugs 73 produce resilient claws provided for hooking or bracing on the anchoring part 145 of the fixed support.
• connection part 72 comprises four lugs 73: two lugs per side connection section.
• the pins 73 are obtained by "U" -shaped cutouts of the metal strip of the spring. The cutouts are made so that the base of the "U” is in a side connection section S2, S4 and the branches of the "U” extend to the level of the folds P1 and P4, see FIGURE 12d.
• connection portion comprises a fifth connection section S5 which includes a distal end S5d, and a proximal end S5p connected to the fourth section S4 by a fold P4, the fold axis of which is orthogonal to the axial direction A of the movement of the brake shoe 118.
• the fifth connection section extends in the direction of the first support section S1 or the second connection section S2, so as to produce a hook or d 'bracing with the anchoring part.
• connection part comprises a fifth connection section S5 which extends in a direction opposite to that of the first support section S1, so as to provide a support tab being able to rest on the bearing face of the fixed support, so as to the first support section relative to the anchoring part.
• the fifth connection section S5 extends in the direction opposite to that of the first support section SI, produces a folding loop and returns to double the connection part over its entire outer surface, so as to form an outer casing or extra thickness. This characteristic makes it possible to mechanically reinforce the yoke portion without changing the thickness of the metal tape used for the manufacture of the spring.
• FIGURES 15a to 16b illustrate a second family of embodiments of axial elastic return springs, which will only be described in terms of its differences from the first family.
• the connection part 72 of the yoke portion 70 comprises a second connection section S2, a proximal end S2p of which is connected to the first support section SI by a connection ply PI the fold axis of which is orthogonal to the axial direction A of the movement of the brake shoe.
• the PI fold substantially forms a half-cylinder.
• the second section S2 extends substantially parallel to the first support section S1 so that it can be inserted under a protuberance 146 of the tenon-shaped anchoring part 145, see FIGURES 15c and 15f, and thus prevent lifting M2 by an axial support T2 applied under said protuberance, see FIGURE 18.
• FIGURE 18 shows in more detail the mode of interaction of the spring with the yoke and with the pad in this family of embodiments.
• the pad portion 63 shown here is fixed to the back of the pad 118, for example by a rivet.
• the pad portion can also be slid under the plate constituting the back of the pad 118, which thus drives it towards the disc without needing to be fixed thereto, for example as illustrated in FIGURE 18.
• the pad portion 63 is driven by the pad 118.
• the support portion 71 bears on the bearing surface 142a of the yoke so as to exert an axial bearing force. , represented by the arrow Tl.
• the connection part 72 comes to rest under the protuberance 146 of the anchoring part 145 so as to exert an axial lifting force, represented by the arrow T2, which protuberance 146 thus opposes its lifting M2.
• the axial elastic return spring may comprise at least one rib 74 disposed across a fold and / or between two consecutive folds.
• the spring 1 comprises ribs 74 at the base of the deformation portion.
• the spring 1 here comprises a rib 74 between the support part 71 and the second lateral connection section.
• the spring 1 comprises a rib 74 on the upper face of the third connection section S3.
• the spring 1 comprises ribs 74 arranged on the connecting folds P2 and P3.
• the anchoring part 145 of a fixed support 140 has the general shape of a tenon projecting axially from a bearing face 141a, 142a of the fixed support 140.
• the anchoring part is preferably molded from a single piece with said fixed support so as to be able to receive and cooperate with the yoke portion of an axial elastic return spring defined above.
• the bearing face 141a, 142a arranged on each leg 141 or 142 extends in a plane parallel to the plane of the brake disc.
• FIGURES 5b, 6b and 7b illustrate in more detail different shapes provided for this anchoring part 145, which can be combined. with the different shapes of the connection part 72.
• the anchoring part has the shape of a tenon, all of the edges of which are rounded.
• the anchoring part has a cutting section substantially in the form of a half cylinder.
• the anchoring part 145 comprises at least one protuberance 146 or a bead projecting transversely from the axial distal end so as to define an overhang between said protuberance and the bearing face 141a, 142a, of the fixed support.
• the protuberance is molded integrally with said support so as to be able to receive and cooperate with the yoke portion of said spring.
• the protrusion 146 extends from one or both sides of the anchoring part.
• each protuberance extends transversely (and in particular tangentially) by a length equal to between 10% and 30% of the width of the anchoring part, preferably between 15% and 20% of the width of the part. anchor.
• the size of the protrusion is chosen in particular as a function of the elastic capacity of the connection part, in particular of the maximum possible spacing between the plies PI and P4 due to the elastic deformation of the connection part.
• the anchoring part is intended to be surrounded by the connection part of the spring. Under the effect of the pinching T3, each of these overhangs 146 allows better anti-lifting retention M2 of the connecting part 72 of the spring.
• the anchoring part comprises a protuberance 146 extending transversely (and in particular tangentially ) at its end, of a length equal to between 40% and 100% of the width of the anchoring part, preferably between 50% and 60% of the width of the anchoring part.
• the size of the protuberance is in particular chosen as a function of the elastic capacity of the deformation portion, in particular of the ability of the fold C2 to deform elastically so that the sections 67 and 68 come together in order to introduce the connection part.
• 72 under protrusion 146 see FIGURES 15c and 15f.
• the spring is thus held in position by means of support T2 under the protuberance 146 of the anchoring part 145.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Braking Arrangements (AREA)

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• 2019
  • 2019-06-26 FR FR1906953A patent/FR3097923B1/fr active Active
• 2020
  • 2020-06-17 EP EP20735280.8A patent/EP3990799A1/de active Pending
  • 2020-06-17 CN CN202080047240.0A patent/CN114026348A/zh active Pending
  • 2020-06-17 WO PCT/EP2020/066787 patent/WO2020260098A1/fr unknown
  • 2020-06-17 US US17/596,564 patent/US20220252120A1/en active Pending

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