WO2016088152A1 - ドラムブレーキ装置 - Google Patents
ドラムブレーキ装置 Download PDFInfo
- Publication number
- WO2016088152A1 WO2016088152A1 PCT/JP2014/006024 JP2014006024W WO2016088152A1 WO 2016088152 A1 WO2016088152 A1 WO 2016088152A1 JP 2014006024 W JP2014006024 W JP 2014006024W WO 2016088152 A1 WO2016088152 A1 WO 2016088152A1
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- WIPO (PCT)
- Prior art keywords
- brake
- sleeve
- axial direction
- drum
- tappet
- Prior art date
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Classifications
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- 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
- F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
Definitions
- the present invention relates to a drum brake device, and more particularly to a drum brake device having a gap adjusting mechanism.
- the drum brake is provided in the vehicle and is a pair of cylinder-shaped brake drums that are attached to the axle so as to be rotatable integrally therewith, and are disposed along the inner peripheral surface of the brake drum so as to be swingable by the anchor bracket.
- the brake drum (the wheel provided on the axle) is made using the friction generated between the two by pressing the lining provided on the brake shoe against the inner surface of the brake drum. ) Is to brake the rotation.
- an expander that protrudes outward according to the brake operation is attached to the tip of the brake shoe, and the brake shoe is swung by the expander extending operation so that the lining is attached to the inside of the brake drum.
- the expander of the drum brake includes a tappet, a sleeve coaxially attached to the tappet, and a screw screwed into the sleeve and having an outer end connected to the lining, and the tappet is formed in the housing. It is configured to be inserted into.
- the tappet and the sleeve are connected via a circlip, and relative movement in the axial direction is restricted.
- a one-way clutch is disposed between the tappet and the sleeve so that rotation of the sleeve relative to the tappet in one direction around the axis is permitted, and rotation in the other direction around the axis is restricted.
- the lining wears due to friction with the brake drum, but if the gap between the lining and the brake drum (hereinafter also referred to as shoe clearance) increases due to this wear, the effectiveness of the brake may be deteriorated.
- the drum brake is provided with a gap adjusting mechanism that automatically adjusts the gap between the lining and the brake drum so that the gap between the lining and the brake drum is always kept constant by reducing the shoe clearance according to the wear of the lining.
- the clearance adjustment mechanism rotates the sleeve independently relative to the screw (rotating in the one direction) and swings the lining outward by projecting the screw that is screwed into the sleeve to the shoe clearance. Is configured to pack.
- the sleeve is rotated in one direction so that the gap adjusting mechanism operates normally, and the rotation of the sleeve in one direction by an external force that is not related to the brake operation is restricted to control the gap adjusting mechanism. It is necessary to make it compatible with preventing malfunction.
- the drum brake described in the above-mentioned patent document is provided with a configuration that imparts a frictional resistance that does not hinder normal operation with respect to the rotation of the sleeve.
- the outer peripheral surface on the long diameter side of the circlip is brought into contact with the tappet, and the inner peripheral surface on the short diameter side of the circlip is used as the sleeve.
- a predetermined resistance is given to the relative rotation of the sleeve.
- the conventional circlip is formed in an elliptical ring shape having a cut end and can be elastically deformed in the major axis direction and the minor axis direction, but it is difficult to apply a large tension in a limited accommodation space. At the same time, it is difficult to set the balance between the tensions acting in the major axis direction and the minor axis direction, so that it is difficult to arbitrarily set the resistance to the relative rotation of the sleeve, and as a result, the degree of freedom in design is reduced. There was a problem.
- the present invention has been made in view of such a problem, and a drum brake device capable of arbitrarily setting a resistance for preventing a malfunction of the gap adjusting mechanism and increasing the degree of freedom in design.
- the purpose is to provide.
- a drum brake device includes a cylindrical brake drum that is provided on a rotating member and is rotatable together with the rotating member, and a brake member that is swingably provided on a fixed member.
- a brake device comprising: a brake shoe disposed along an inner peripheral surface of the brake drum; and an expander that swings the brake shoe in response to a brake operation and contacts the inner peripheral surface of the brake drum.
- the expander is provided with a pressing member that applies a pressing force in the axial direction according to a brake operation, and is provided on the pressing member so as to be relatively rotatable about the axis, and transmits the pressing force from the pressing member.
- a transmission member screwed in the axial direction with respect to the transmission member, and non-rotatably connected to the brake shoe about the axis;
- a connecting member for bringing the brake shoe into contact with the inner peripheral surface of the brake drum by a pressing force transmitted from the material, and rotating the transmitting member relative to the axis so that the connecting member is moved in the axial direction.
- a gap adjusting mechanism that adjusts a gap between the brake shoe and the inner peripheral surface of the brake drum by disengaging the connecting member with respect to the transmission member and displacing the relative position in the axial direction;
- the pressing member and the transmission member are fitted in the axial direction and connected via a connecting member provided between the fitting surfaces and a lap spring that exerts an urging force in the axial direction,
- the wrap spring is formed of a compression coil spring wound around the axis, and one end side is locked to the pressing member and the other end side is locked to the transmission member.
- the compression member is disposed in a compressed state between the pressing member and the transmission member, and among the relative rotation of the transmission member with respect to the pressing member, relative rotation in one direction around the axis that reduces the diameter of the compression coil spring is performed.
- the relative rotation in the other direction around the axis that allows the compression coil spring to expand is restricted, and the transmission member is urged in the axial direction with respect to the pressing member to transmit the pressing member and the transmission.
- the wrap spring is formed by a compression coil spring and acts as a one-way clutch that allows only relative rotation in one direction of the transmission member, and the transmission member is attached in the axial direction.
- the frictional resistance imparted to the relative rotation of the transmission member is stabilized over a long period of time by causing the two side surfaces of the connecting member to abut against each other while being elastically sandwiched between the pressing member and the transmission member.
- the frictional resistance value applied to the relative rotation of the transmission member can be arbitrarily and easily set according to the set load determined by the spring constant and the set length (shrinkage amount) of the lap spring.
- the degree of freedom in designing the drum brake device can be improved, and further, without increasing the number of parts compared to the conventional drum brake device, And restricting the relative rotation of the transfer member caused by movement and the like, it is possible to reliably prevent erroneous operation of the gap adjusting mechanism.
- the drum brake device of the present embodiment in order to prevent the gap adjusting mechanism from malfunctioning, as in the conventional case, the drum brake device is formed into an elliptical ring shape having a cut surface and applies tension in the major axis direction and the minor axis direction.
- the compression coil spring is Because it can be manufactured at low cost and the number of assembly steps to the housing is reduced (because it can be assembled with an automatic machine), it is possible to improve the productivity of the drum brake device and reduce the production cost. become.
- FIG. 2 is a cross-sectional view taken along arrow II-II in FIG. 1 and shows a state where the drum brake is not operated.
- FIG. 2 is a cross-sectional view taken along arrow II-II in FIG.
- It is a side view of the sleeve in the expander.
- It is sectional drawing which shows an example of the conventional sleeve assembly (A) is an exploded state, (B) shows an assembly state.
- the drum brake B is swingably provided on a drum unit 3 provided on an axle 1 and provided with a brake drum 31 rotatable with the axle 1 and an anchor bracket 2 fixed to the vehicle body.
- the brake shoe unit 4 having a pair of brake shoes 40, 40 disposed along the inner peripheral surface of the brake drum 31, and the brake shoes 40, 40 are swung in response to a brake operation to brake the brake drum 31.
- the expander 5 is pressed against the inner peripheral surface of the main body.
- the anchor bracket 2 has a circular opening 2a at the center, and an axle housing (not shown) of a vehicle body via a bolt (not shown) inserted into a bolt hole 2b provided around the opening 2a. Fixed to.
- the lower part of the anchor bracket 2 has a support arm part 2c that is bifurcated in the thickness direction (perpendicular to the plane of FIG. 1).
- the support arm part 2c has a front side in the thickness direction and a rear side in the thickness direction. In each of these, circular hole-shaped pin insertion openings 2d, 2d are opened side by side in the front view.
- a wheel rim (not shown) is attached to a wheel hub (not shown) rotatably attached via a bearing on an axle 1 protruding outward from the opening 2a of the anchor bracket 2.
- the brake drum 31 is combined.
- a wheel is attached to the wheel rim, and the brake drum 31 and the wheel rotate together via a wheel hub.
- the brake shoe unit 4 includes two brake shoes 40 disposed on the left and right of the front view across the anchor bracket 2.
- the brake shoe 40 includes a web part 41 extending in an arc shape, a rim part 42 attached to the outer peripheral end of the web part 41, and a lining 43 fixed to the rim part 42 by rivets or the like.
- the brake shoe 40 is disposed along the inner peripheral surface of the brake drum 31, and the lining 43 is opposed to the inner peripheral surface of the brake drum 31.
- the brake shoe 40 is pivotally fixed to the anchor bracket 2 via an anchor pin 44 inserted into the pin insertion opening 2d of the support arm portion 2c, and the brake shoe 40 is pivoted to the left and right in FIG. It can swing in the direction.
- a return spring 45 is connected between the tip portions of the pair of brake shoes 40, 40 to connect them together.
- an expander 5 fixed to the anchor bracket 2 is disposed between the tip portions of the brake shoes 40, 40.
- the expander 5 causes the distal ends of the brake shoes 40 and 40 to be biased by the return spring 45 by the extension operation of the screws 57 and 57. Press outwards against it.
- the brake shoes 40, 40 swing outwardly about the anchor pins 44, 44, respectively, and the linings 43, 43 are pressed against the inner peripheral surface of the opposing brake drum 31.
- the rotation of 31 is braked. As a result, a predetermined braking action is obtained for the wheel that rotates integrally with the brake drum 31.
- the expander 5 includes a housing 51 that forms a pair of cylinder parts 51b and 51b that form a wedge receiving part 51a in the center and communicate with the wedge receiving part 51a from both sides.
- a wedge 52 that is removably attached to the wedge accommodating portion 51a, and a sleeve assembly 53 that is fitted in the cylinder portions 51b and 51b and is slidably disposed in the direction of the axis X (hereinafter also referred to as “axis direction”).
- 53, and a screw 57 that is screwed in the axial direction with the sleeve assembly 53 and extends outward from the side of the housing 51.
- a boot 59 for preventing dust from entering the cylinder portion 51b is attached to the opening end of the cylinder portion 51b in the expander 5.
- the expander 5 is configured symmetrically.
- the inner side of the housing 51 in the axial direction (wedge housing) with reference to the orientation of the expander 5 shown in FIGS.
- the portion 51a side is referred to as "one end side”
- the outer side of the housing 51 in the axial direction (brake shoe 40 side)
- FIG. 3 shows the state of the expander 5 when the brake is operated.
- the wedge 52 is formed in a shaft shape, and is attached to the housing 51 so as to be insertable / removable in a direction orthogonal to the axial direction (hereinafter also referred to as “axial orthogonal direction”) by operation of a diaphragm of a chamber (not shown).
- axial orthogonal direction a direction orthogonal to the axial direction
- FIG. 2 when the brake is not operated (when the brake is released), the wedge 52 is pulled out from the wedge housing portion 51a by the urging force of the wedge spring 52a.
- the wedge 52 moves in the wedge accommodating portion 51a in the direction orthogonal to the axis (downward in FIG. 3) against the urging force of the wedge spring 52a, as shown in FIG. The state is inserted into 51a.
- the insertion end portion 52b which is the end portion on the side inserted into the wedge accommodating portion 51a, is formed in a wedge shape that is pointed toward the tip, and has inclined surfaces 52c and 52c on both sides in the axial direction.
- the wedge 52 is provided with a roller holder 52e that supports the pair of rollers 52f.
- the pair of rollers 52f is provided so as to be rotatable with respect to the roller holder 52e and movable in a direction (axial direction) close to and away from each other.
- the roller holding body 52e is provided so as to freely reciprocate along the direction orthogonal to the axis, and is always urged to the outside of the housing 51 (upward in FIG. 2) together with the wedge 52 by the wedge spring 52a. .
- the roller holder 52 e cooperates with the wedge 52 to convert the linear motion of the wedge 52 in the direction perpendicular to the axis to the linear motion of the sleeve assembly 53 in the axial direction.
- the sleeve assembly 53 has a main body portion 54a having an outer diameter slightly smaller than the inner diameter of the cylinder portion 51b on one end side in the axial direction, and on the other end side in the axial direction.
- a tappet 54 having a cylindrical portion 54b having a smaller outer diameter than the main body portion 54a, and a cylindrical shape having the same outer diameter as that of the main body portion 54a of the tappet 54, with respect to the cylindrical portion 54b of the tappet 54 at one end side in the axial direction.
- the wrap spring 61 is supported between the sleeves 55 in a horizontal posture.
- the tappet 54 is formed in a stepped cylindrical shape from a main body portion 54a and a cylindrical portion 54b having different outer diameters.
- the main body portion 54a has an inclined surface 54c that is substantially parallel to the inclined surface 52a of the wedge 52.
- the portion 54b has a cylindrical spring mounting hole 54s that opens to the other end side.
- the cylindrical portion 54b is provided with a ring mounting groove 54r along the entire outer peripheral surface.
- the tappet 54 is fitted and inserted into the innermost part of the cylinder portion 51b communicating with the wedge accommodating portion 51a, and the inclined surface 54c is brought into contact with the peripheral surface of the roller 52f.
- the wedge 52 is inserted and withdrawn via the roller 52f. It slides in the axial direction in the cylinder portion 51b.
- the sleeve 55 is formed in a hollow, substantially cylindrical shape having a through hole 55a extending along the axial direction.
- the through hole 55a is formed in order from the one end side in the axial direction to the same hole diameter as the cylindrical hole 55b that opens to one end side and fits the cylindrical portion 54b of the tappet 54 and the spring mounting hole 54s of the tappet 54.
- the spring mounting hole 55s and the female screw portion 55c that opens to the other end side and is screwed into the screw 57 are coaxially connected to each other.
- a second ring mounting groove 55r is formed in the cylindrical hole 55b of the sleeve 55 along the entire inner peripheral surface.
- a ring mounting groove 54r cut along the outer peripheral surface of the cylindrical portion 54b and an inner peripheral surface of the cylindrical hole 55b are cut.
- the provided ring mounting groove 55r is aligned, and an integral gap for mounting the circlip 56 is formed between the fitting surfaces of the tappet 54 and the sleeve 55.
- a spring mounting hole 54 s opened on the other end side of the cylindrical portion 54 b and a spring mounting opened on one end side of the sleeve 55.
- the holes 55s are aligned with each other, so that an integral space for disposing the lap spring 61 is formed inside the tappet 54 and the sleeve 55.
- the circlip 56 is formed of a steel wire material that has been subjected to heat treatment such as quenching / tempering or austempering, and has a C shape (circular ring shape) in which a part of the ring is cut out, and is elastically deformed in the direction of diameter reduction. Formed possible.
- the circlip 56 is disposed in the ring mounting grooves 54r and 55r that are aligned and integrated with each other between the fitting surfaces of the tappet 54 and the sleeve 55, so that the tappet 54 and the sleeve 55 are moved in the axial direction. It is linked so that it cannot leave.
- the wrap spring 61 is a compression coil spring obtained by, for example, winding a circular cross-section wire into a coil and cutting the spring material into a predetermined length. Both ends of the lap spring 61 are flat surfaces which are subjected to end processing such as grinding and polishing after cutting.
- the lap spring 61 has an outer peripheral surface on one end engaged with an inner peripheral surface of the spring mounting hole 54s of the tappet 54, and an outer peripheral surface on the other end engaged with an inner peripheral surface of the spring mounting groove 55s. Attached in an elastically compressed state.
- the wrap spring 61 has a one-way clutch function, and in the direction of diameter reduction in which the outer diameter of the coil is reduced (for example, right rotation when the winding direction of the coil is right-handed), In the diameter-enlarging direction (same left-hand rotation) in which relative rotation is allowed and the coil outer diameter expands, the outer peripheral surface bites into the tappet 54 and the sleeve 55 and integrates them to prevent this relative rotation.
- the lap spring 61 is elastically deformed in a state where a predetermined load (set load) is generated by being compressed and deformed in the spring mounting holes 54s and 55s that are integrated with each other.
- a predetermined load set load
- the wrap spring 61 urges the tappet 54 and the sleeve 55 to separate in the axial direction, whereby the circlip 56 attached as a retaining stopper in the axial direction of the sleeve 55 with respect to the tappet 54 is attached to the tappet 54 and the sleeve. 55 in contact with the opposite direction in the axial direction.
- the circlip 56 is such that the outer surface 56a on one end side is pressed against the inner surface 55r1 on one end side of the ring mounting groove 55r of the sleeve 55 as shown in FIG.
- the outer surface 56b on the other end side contacts the inner surface 54r1 on the other end side of the ring mounting groove 54r of the tappet 54 in a pressed state. Therefore, in order to rotate the sleeve 55 relative to the tappet 54 about the axis, a rotational force (rotational torque) that resists the frictional resistance between the circlip 56 and the tappet 54 and the sleeve 55 is required.
- the frictional resistance can be arbitrarily set according to the set load of the lap spring 61.
- the set load can be arbitrarily set by changing the spring constant or set length (shrink amount) of the lap spring 61.
- the screw 57 is formed in a rod shape extending in the axial direction and has a male threaded portion 57a on the outer peripheral surface.
- the male threaded portion 57a is screwed into the female threaded portion 55c of the sleeve 55 and extends outward from the side of the housing 51. It is provided to do.
- an adjustment dial portion 57b is provided on the other end side in the axial direction of the screw 57.
- a clip 58 is locked to the adjustment dial portion 57b so as to be rotatable around the screwing shaft of the screw 57.
- the clip 58 is engaged with the web portion 41 of the brake shoe 40.
- the screw 57 is connected to the brake shoe 40 via a clip 58 that is provided to sandwich the adjustment dial portion 57b.
- a helical helical spline 55d is formed on the outer peripheral surface of the other end side of the sleeve 55.
- the helical spline 55d has a predetermined backlash (for example, about 3 mm).
- the drive ring 62 is engaged.
- the drive ring 62 has a conical surface 62a that abuts an inclined surface 51c formed at the outer end of the cylinder portion 51b.
- the drive ring 62 biases the drive ring 62 toward one end in the axial direction, and the inclined surface 51c and A predetermined frictional resistance is applied between the conical surfaces 62a.
- the expander 5 having such a configuration includes a gap adjusting mechanism 6 that automatically closes a gap (shoe clearance) between the lining 43 and the brake drum 31 to adjust to a predetermined gap when the lining 43 is worn.
- the gap adjusting mechanism 6 includes a tappet 54, a sleeve 55, a circlip 56, a screw 57, a clip 58, a lap spring 61, a drive ring 62, a drive spring 63, and the like.
- the operation of a diaphragm causes the wedge 52 to be inserted into the wedge accommodating portion 51a against the urging force of the wedge spring 52a (the bottom of FIGS. 2 and 3).
- This pressing force is converted into a pressing force in the axial direction through the rollers 52f and 52f by the wedge action between the inclined surfaces 52c and 52c of the wedge 52 extending in parallel and the inclined surfaces 54c and 54c of the tappet 54, and the sleeve assembly 53 Is transmitted to.
- the tappet 54 and the sleeve 55 move in the cylinder portion 51b from one end side to the other end side in the axial direction in an integrated state.
- the helical spline 55d of the sleeve 55 and the drive ring 62 are meshed with a predetermined play in the axial direction. If the amount of movement of the sleeve 55 due to the brake operation is within the range, the sleeve 55 moves directly along the axial direction in the cylinder portion 51b without rotating the drive ring 62. At this time, the drive ring 62 is held in a state where the conical surface 62 a is in contact with the inclined surface 51 c of the housing 51 by the urging force of the drive spring 63.
- the screw 57 screwed into the sleeve 55 is locked to the brake shoe 40 by a clip 58, and the sleeve 55 does not rotate relative to the sleeve 55 due to the frictional resistance of the clip 58 and the frictional resistance on the thread surface. Directly move in the axial direction in cooperation.
- the pair of brake shoes 40, 40 swings outward about the anchor pins 44, 44 by the overhang of the screws 57, 57 in the axial direction, and the lining 43 presses against the inner peripheral surface of the brake drum 31. Then, the rotation of the brake drum 31 is braked by the friction between them.
- the wedge 52 moves in the removal direction (upward direction in FIGS. 3 and 4) from the wedge accommodating portion 51a by the urging force of the wedge spring 52a.
- the screw 57 and the sleeve assembly 53 are moved in the cylinder 51b from the other end side in the axial direction to the one end side by the action of the return spring 45 straddled between the brake shoes 40, 40, and inward in the axial direction.
- the amount of movement of the sleeve 55 is within the range, the sleeve 55 moves linearly along the axial direction in the cylinder portion 51b without rotating in the same manner as when overhanging.
- the sleeve 56 moves toward the one end side in the axial direction in the cylinder portion 51b without receiving resistance with respect to the amount corresponding to the backlash between the helical spline 55d and the drive ring 62.
- the amount of movement of the sleeve 56 exceeds the amount equivalent to the backlash, the helical spline 55d comes into contact with the meshing surface on the other end side of the drive ring 62 and is prevented from moving in the axial direction.
- the rotation of the drive ring 62 is restricted as described above and cannot be freely rotated.
- the lap spring 61 built in the sleeve assembly 53 restricts the rotation in the direction in which the sleeve 55 is rotated along the meshing surface on one end side of the drive ring 62 (for example, left rotation)
- the sleeve 55 is formed to allow rotation in a direction (for example, right rotation) in which the sleeve 55 is rotated along the engagement surface on the other end side of the drive ring 62. Therefore, this time, the sleeve 55 is rotated along the engagement surface on the other end side of the drive ring 62.
- the screw 57 receives the frictional resistance from the clip 58 that is locked to the brake shoe 40 and restricted in rotation. Since this frictional resistance is larger than the frictional resistance at the screw surfaces of the screw 57 and the sleeve 55, the screw 57 does not rotate together with the sleeve 55. Therefore, the sleeve 55 rotates independently with respect to the tappet 54 and the screw 57. As the sleeve 55 rotates, the screw 57 is fed outward in the axial direction by a feed amount corresponding to the rotation angle.
- the gap adjusting mechanism 6 when the lining 43 is worn, the sleeve 55 moves exceeding a predetermined amount (an amount corresponding to the backlash) when the brake is operated, while the sleeve 55 is moved to an excess amount when the brake is released.
- a predetermined amount an amount corresponding to the backlash
- the wrap spring 61 biases the sleeve 55 against the tappet 54 in the axial direction (the direction in which both are separated from each other), so that the lap spring 61 is mounted in the ring mounting grooves 54 r and 55 r.
- the drum brake B may be subjected to external forces that are not involved in brake operation due to vibrations received from the wheels, for example, when traveling on uneven road surfaces.
- a rotational force in a direction in which relative rotation with respect to the tappet 54 is allowed may act on the sleeve 55 regardless of the actual brake operation.
- the rotational force due to this vibration or the like is usually smaller than the rotational force due to the urging force of the return spring 45, and in this embodiment, the circlip 56 and the tappet are received by the urging force of the lap spring 61.
- 54 and the sleeve 55 are in contact with each other, so that a predetermined frictional resistance is applied to the relative rotation of the sleeve 55.
- the frictional resistance counters an unexpected rotational force due to vibration or the like.
- the relative rotation of 55 is prevented. Since the pressing force from the lap spring 61 acts on the tappet 54 and the sleeve 55, this pressing force itself also acts as a resistance against the relative rotation of the sleeve 55.
- the drum brake B can effectively operate the original adjustment function, but even if an unexpected rotational force acts on the sleeve 55, the drum brake B gives an appropriate resistance to the sleeve 55, The rotation of the sleeve 55 can be restricted. Therefore, it is possible to prevent malfunction of the gap adjusting mechanism 6 such that the sleeve 55 rotates and the shoe clearance is clogged regardless of the brake operation. Further, by preventing the gap adjusting mechanism 6 from malfunctioning, the gap between the lining 43 and the brake drum 31 can be held by an appropriate shoe clear lath, and the brake shoe can be prevented from being dragged.
- the wrap spring 61 is formed by the compression coil spring and acts as a one-way clutch that allows only relative rotation in one direction of the sleeve 55.
- a frictional resistance imparted to the relative rotation of the sleeve 55 is obtained by biasing the circlip 56 in an axial direction so that both side surfaces of the circlip 56 are elastically sandwiched between the tappet 54 and the sleeve 55.
- the friction resistance value to be applied to the relative rotation of the sleeve 55 can be arbitrarily and easily set according to the set load determined by the spring constant of the lap spring 61 and the set length (shrinkage amount). Therefore, the degree of freedom in designing the drum brake B can be improved. Without increasing the number of parts to the brake, to regulate the relative rotation of the sleeve 55 caused by vibration or the like, it is possible to reliably prevent erroneous operation of the gap adjusting mechanism 6.
- drum brake B of the present embodiment in order to prevent the gap adjusting mechanism 6 from malfunctioning, it is formed in an elliptical ring shape having a cut surface and applies tension in the major axis direction and the minor axis direction as in the prior art.
- a circlip or a wave spring see FIG. 8 that is formed in a band plate ring shape in which crests and troughs are alternately provided at a predetermined pitch in the circumferential direction and that exerts an urging force in the axial direction
- compression coil springs can be manufactured at low cost and the number of assembly steps to the housing is reduced (because assembly with an automatic machine is also possible), improving drum brake productivity and reducing production costs. Reduction can be achieved.
- the lap spring 61 of the present embodiment is formed as a compression coil spring (pitch spring) and acts as a one-way clutch that restricts rotation in one direction, and is urged in the axial direction. It works.
- the conventional lap spring 161 is formed as a torsion coil spring (contact spring), and acts only as a one-way clutch that restricts rotation in one direction. The biasing action is not performed, and the function is completely different from the lap spring 61 of the present embodiment. Therefore, the conventional gap adjustment mechanism using the lap spring 161 is different from the present embodiment in that it is necessary to separately arrange a wave spring 171 for exerting an urging force in the axial direction in addition to the lap spring 161. Is.
- drum brake B is configured as a leading trailing drum brake is illustrated, but it may be configured as a uni-servo, duo-servo, or two-leading drum brake.
- the configuration of the lap spring 61 of this embodiment is merely an example, and the coil material, cross-sectional shape, spring constant, number of turns, pitch, coil diameter, and the like can be set as appropriate.
- Drum brake 1 Axle (rotating member) 2 Anchor bracket (fixing member) 3 Drum unit 4 Brake shoe unit 5 Expander 6 Gap adjustment mechanism 31 Brake drum 40 Brake shoe 45 Return spring 51 Housing 52 Wedge 53 Sleeve assembly 54 Tappet (Pressing member) 55 Sleeve (Transmission member) 56 Circlip (connecting member) 57 Screw (connection member) 61 Wrap spring
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Abstract
Description
1 車軸(回転部材)
2 アンカーブラケット(固定部材)
3 ドラムユニット
4 ブレーキシューユニット
5 エキスパンダ
6 間隙調整機構
31 ブレーキドラム
40 ブレーキシュー
45 リターンスプリング
51 ハウジング
52 ウェッジ
53 スリーブアッシー
54 タペット(押圧部材)
55 スリーブ(伝達部材)
56 サークリップ(連結部材)
57 スクリュウ(接続部材)
61 ラップスプリング
Claims (1)
- 回転部材に設けられて前記回転部材とともに回転可能な円筒状のブレーキドラムと、
固定部材に揺動自在に設けられて前記ブレーキドラムの内周面に沿って配設されるブレーキシューと、
ブレーキ操作に応じて前記ブレーキシューを揺動させて前記ブレーキドラムの内周面に当接させるエキスパンダとを備えてなるドラムブレーキ装置であって、
前記エキスパンダは、ブレーキ操作に応じて軸線方向に押圧力を作用させる押圧部材と、前記押圧部材に前記軸線回りに相対回転可能に設けられて前記押圧部材からの押圧力を伝達する伝達部材と、前記伝達部材に対して前記軸線方向に螺合されるとともに前記ブレーキシューに前記軸線回りに回転不能に接続されて、前記伝達部材から伝達される押圧力により前記ブレーキシューを前記ブレーキドラムの内周面に当接させる接続部材とを有し、前記伝達部材を前記軸線回りに相対回転させて前記接続部材を前記軸線方向に繰り出させることで、前記伝達部材に対する前記接続部材の前記軸線方向の相対位置を変位させて、前記ブレーキシューと前記ブレーキドラムの内周面との間隙を調整する間隙調整機構を備えており、
前記押圧部材および前記伝達部材は、前記軸線方向に嵌合されて、互いの嵌合面の間に設けられる連結部材と軸線方向に付勢力を作用させるラップスプリングとを介して接続されており、
前記ラップスプリングは、前記軸線回りに巻回された圧縮コイルスプリングから形成されて、一端側が前記押圧部材に係止され他端側が前記伝達部材に係止されて前記押圧部材と前記伝達部材との間に圧縮状態で配設され、前記押圧部材に対する前記伝達部材の相対回転のうち、前記圧縮コイルスプリングを縮径させる前記軸線回り一方向への相対回転を許容して前記圧縮コイルスプリングを拡径させる前記軸線回り他方向への相対回転を規制し、且つ、前記押圧部材に対して前記伝達部材を軸線方向に付勢して、前記押圧部材と前記伝達部材とを前記軸線方向の相反する方向から連結部材に当接させることで、前記押圧部材に対する前記伝達部材の軸線方向への相対移動を規制するとともに、前記押圧部材に対する前記伝達部材の相対回転に摩擦抵抗を付与するよう構成したことを特徴とするドラムブレーキ装置。
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CN201480083800.2A CN107002791B (zh) | 2014-12-02 | 2014-12-02 | 鼓式制动装置 |
KR1020177017736A KR102268683B1 (ko) | 2014-12-02 | 2014-12-02 | 드럼 브레이크 장치 |
PCT/JP2014/006024 WO2016088152A1 (ja) | 2014-12-02 | 2014-12-02 | ドラムブレーキ装置 |
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JP2018119312A (ja) * | 2017-01-25 | 2018-08-02 | 三井住友建設株式会社 | 点検装置 |
CN114962495A (zh) * | 2022-05-10 | 2022-08-30 | 江苏凯迅达高铁传动技术开发有限公司 | 一种楔式制动器用轮缸润滑系统 |
WO2023223492A1 (ja) * | 2022-05-19 | 2023-11-23 | 株式会社Tbk | ドラムブレーキ装置 |
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CN114962494B (zh) * | 2022-05-10 | 2023-12-26 | 江苏凯迅达高铁传动技术开发有限公司 | 一种楔式制动器用轮缸 |
KR20240012825A (ko) | 2022-07-21 | 2024-01-30 | 에이치엘만도 주식회사 | 드럼브레이크 |
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JP6382340B2 (ja) | 2018-08-29 |
CN107002791A (zh) | 2017-08-01 |
KR20170090459A (ko) | 2017-08-07 |
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