JP5484979B2 - Caliper brake device - Google Patents

Description

  The present invention relates to a caliper brake device that applies a frictional force across a disk that rotates with a wheel.

  A hard rubber for vibration absorption is usually interposed between the vehicle body (trolley) and the axle of a railway vehicle. When an external force is applied to the vehicle by cornering, for example, the hard rubber shrinks, thereby May tilt slightly against the wheel disc.

  Further, in the conventional caliper brake device, the caliper body may bend away from the disk of the wheel by a braking reaction force that presses the brake against the disk during braking. Further, the disk may be thermally deformed and tilted during braking.

In Patent Document 1, as a hydraulic cylinder that presses a brake against a disc, a proximal-side piston that protrudes from a caliper body by operating hydraulic pressure, and a distal-end side that is rotatably supported by this proximal-side piston via a spherical bearing There is disclosed a piston that is provided with a piston, and the tip side piston rotates at the time of braking to keep the restrictor parallel to the rotating surface of the disk, thereby preventing uneven wear of the restrictor.
Japanese Patent Laid-Open No. 10-267058

However, in such a conventional caliper brake device, comprising: a guide plate for supporting the brake shoe, and anchor pins which retractably supports the guide plate to the disk on key Yaripa body, the posture of the brake shoe Since it is constrained via the guide plate and the anchor pin, the friction surface of the brake can follow the rotating surface of the disc when the disc of the wheel is tilted or the caliper body is bent. This may not be possible and may cause uneven wear of the brake.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a caliper brake device in which the friction surface of the brake member follows the rotating surface of the disk during braking, and the uneven wear of the brake member can be suppressed. To do.

The present invention is a caliper brake device for a vehicle that applies a frictional force across a disk that rotates with a wheel, a brake member that slides on the disk to apply a frictional force, a guide plate that supports the braker, An actuator that presses the brake against the disc via the guide plate, a caliper body supported by the vehicle body, and a guide plate that is supported by the caliper body so as to be able to advance and retreat with respect to the disc, and is arranged to sandwich the actuator 2 The anchor pin and a rotation support mechanism that supports the guide plate so as to be rotatable around at least two axes with respect to the anchor pin are provided.

  According to the present invention, the guide plate rotates with respect to the anchor pin via the rotation support mechanism so as to follow the disk inclination generated during turning and the caliper body bending generated during braking. The surface slides in parallel with the rotating surface of the disk, the surface pressure of the brake against the disk is kept uniform, the braking force is increased, and uneven wear of the brake is suppressed.

It is a top view of a caliper brake device showing an embodiment of the present invention. It is a longitudinal cross-sectional view of a caliper brake device similarly. It is a side view of a caliper brake device. It is a longitudinal cross-sectional view of an anchor pin, a guide plate, etc. similarly. Similarly, it is a cross-sectional view of an anchor pin and a guide plate. Similarly, (a) is a cross-sectional view of the anchor pin, (b) is a cross-sectional view showing the upper end portion of the guide plate, and (c) is a cross-sectional view showing a state where the anchor pin is engaged with the guide plate.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

1-3 is a three-view drawing of the caliper brake device 1 showing an embodiment of the present invention. FIG. 3 is a side view of the caliper brake device 1 as viewed from the right side of the vehicle. 1 is a plan view seen from the direction of arrow B in FIG. FIG. 2 is a longitudinal sectional view taken along line AA of FIG. It is assumed that three axes X, Y, and Z orthogonal to each other are set, the X axis extends in the horizontal horizontal direction, the Y axis extends in the vertical direction, and the Z axis extends in the horizontal front-rear direction.

  As shown in FIG. 1, the caliper brake device 1 mounted on a railway vehicle sandwiches the disk 6 of the wheel 5 between the left and right control members 7 and brakes the rotation of the wheel 5.

In FIG. 2, O is the rotation center axis of the wheel 5, H is the center line of the wheel 5 orthogonal to the rotation center axis O, and in FIG. 1, 20 is fixed on a carriage (vehicle body) (not shown) of the railway vehicle. Reference numeral 10 denotes a caliper body supported by the support frame 20.

  The caliper body 10 is floatingly supported on the support frame 20 by upper and lower slide pins 31 and 32 so as to be slidable in the X-axis direction.

  The caliper body 10 includes left and right caliper arms 12 that extend so as to straddle the disc 6 of the wheel 5, and a yoke portion 13 that connects the left and right caliper arms 12.

  Anchor blocks 48 are fastened to the upper and lower ends of the left caliper arm 12 via bolts 42 (see FIG. 1). A support rail (not shown) is integrally formed with the left caliper arm 12. A dovetail groove is formed in the support rail, and a lining back plate (not shown) of the left restrictor 7 is inserted into the dovetail groove. The restrictor 7 is inserted into the support rail, and the upper and lower ends thereof are prevented from being detached by engaging with the anchor pins 43 of the anchor block 48, and are fixed to the left caliper arm 12.

  Adjusters 41 are fastened to the upper and lower ends of the right caliper arm 12 via bolts 42, respectively. The upper and lower adjusters 41 include anchor pins 43 that protrude in the X-axis direction. The both ends of the restrictor 7 and its guide plate (support plate) 8 are supported via the upper and lower anchor pins 43.

  The anchor pin 43 is formed in a columnar shape, and is slidably fitted into a through hole formed in the caliper arm 12 via a guide sleeve 39. Thereby, the anchor pin 43 is supported by the caliper arm 12 so as to move in a direction parallel to the rotation center axis O of the disk 6.

  The brake 7 includes a lining 9 as a friction material that comes into sliding contact with the disk 6 and a metal lining back plate 19 to which a back portion of the lining 9 is attached.

  The lining 9 is coupled to the lining back plate 19 via rivets. The lining 9 has a friction surface 9 a that is in sliding contact with the disk 6.

  The guide plate 8 is formed with a dovetail groove 8c extending in the Y-axis direction, and the edge portion 19a of the lining back plate 19 of the control wheel 7 is inserted into the dovetail groove 8c. As a result, the lining back plate 19 of the restrictor 7 is supported by the caliper arm 12 via the guide plate 8.

  The upper and lower anchor pins 43 are respectively formed with annular grooves 43b. An engagement hole 8 a that engages with the annular groove 43 b is formed in the upper end portion of the guide plate 8. At the lower end of the guide plate 8, an engaging recess (half moon groove) 8b that engages with the annular groove 43b is formed (see FIG. 2).

  The upper and lower ends of the guide plate 8 are supported so as to be able to advance and retreat with respect to the disk 6 by engaging the upper and lower ends of the guide plate 8 with the annular grooves 43 b of the anchor pins 43, and the upper and lower ends of the lining back plate 19 are supported on the anchor pins 43. The braking reaction force is supported by engaging with.

  The adjuster 41 is provided with a rubber boot 46 covering the exposed portion of the anchor pin 43, and is protected from dust by the boot 46 (see FIG. 2).

  As shown in FIG. 4, the annular groove 43 b of the anchor pin 43 is defined between the annular step portion 43 d, the annular bottom surface 43 e, and the ring 52. The ring 52 is fitted into an annular groove 43 f formed in the anchor pin 43. A disc-shaped plate 53 is interposed between the ring 52 and the boot 46 so that the boot 46 does not interfere with the guide plate 8.

  When replacing the restrictor 7, first, the lower adjuster 41 is removed from the caliper arm 12, and the anchor pin 43 is disengaged from the lining back plate 19 of the restrictor 7. Next, the restrictor 7 is extracted downward along the dovetail groove 8 c of the guide plate 8. Next, a new restrictor 7 is inserted into the dovetail groove 8c of the guide plate 8 (see FIG. 5). Next, the lower adjuster 41 is attached to the caliper arm 12, the guide plate 8 is supported by the anchor pin 43 being engaged, and the lining back plate 19 is engaged with the anchor pin 43 to prevent the brake ring 7 from coming off. Is done. In this way, the work of attaching and detaching the control member 7 is performed through the guide plate 8.

  As shown in FIG. 2, the adjuster 41 adjusts the clearance between the restrictor 7 and the disk 6 to be substantially constant when the brake is released, and the return spring 44 that urges the restrictor 7 away from the disk 6 via the anchor pin 43. A gap adjusting mechanism 45 is provided. When the brake is released, the brake 7 is separated from the disk 6 by the urging force of the return spring 44, and the gap W with the disk 6 is adjusted to be substantially constant by the gap adjusting mechanism 45. The gap adjusting mechanism 45 may be abolished.

  4 and 5 are a longitudinal sectional view and a transverse sectional view of the anchor pin 43, the guide plate 8, and the like. The anchor pin 43 shown in FIGS. 4 and 5 has a solid structure in which the gap adjusting mechanism 45 is eliminated.

  A hard rubber for vibration absorption is interposed between the carriage (vehicle body) and the shaft of the wheel 5. For example, when an external force is applied to the vehicle due to cornering or the like, the hard rubber is contracted, so that the center axis Oa of the anchor pin 43 is inclined about 1 degree with respect to the rotation axis Od of the disk 6 in the longitudinal sectional view shown in FIG. .

  Further, when the caliper arm 12 of the caliper body 10 is bent away from the disk 6 of the wheel 5 during braking, which will be described later, the center axis Oa of the anchor pin 43 is the rotation axis of the disk 6 in the cross-sectional view shown in FIG. Tilt about 1 degree with respect to Od.

  In response to this, a rotation support mechanism 50 that rotatably supports the guide plate 8 on the anchor pin 43 is provided. The guide plate 8 rotates with respect to the anchor pin 43 via the rotation support mechanism 50 following the inclination of the disc 6 with respect to the carriage and the bending of the caliper arm 12 at the time of braking, so that the friction surface 9a of the restrictor 7 is moved. The disk 6 is configured to slide in parallel with the rotating surface 6a of the disk 6 so that the surface pressure of the friction surface 9a with respect to the disk 6 is kept uniform, increasing the braking force and suppressing uneven wear of the brake 7.

As shown in FIGS. 2 and 4, the pivot support mechanism 50 is formed with a spherical step 43d defining the annular groove 43b on the upper anchor pin 43, and also defining the annular groove 43b. A gap 51 is formed between the annular bottom surface 43 e and the ring 52 formed and the engagement hole 8 a of the guide plate 8 . Similarly, as shown in FIG. 2, together with the annular step portion 43d defining an annular groove 43b is formed in a spherical shape on the anchor pin 43 of the lower portion, the engagement recess 8b of the annular groove 43b and the guide plate 8 A gap 51 is formed between the two.

  FIG. 6A is a cross-sectional view of the anchor pin 43. The annular step 43d of the anchor pin 43 is formed in a spherical shape with the center of friction G and the radius of curvature R.

In FIG. 6A, 9a is the position of the friction surface when the lining 9 is not used (when new). Friction surface 9a is lining 9 are retracted along with the proceeds wear. 9a 'is the position of the friction surfaces in by the thickness of advanced state of 1/2 of the effective friction耗代H which wear has been set to the lining 9 of the lining 9.

Friction center point G, the friction surface 9a of only the thickness of advanced state of 1/2 of the wear effective friction耗代H lining 9 'is set as a point which intersects the central axis Oa of the anchor pin 43 .

  FIG. 6B is a cross-sectional view showing the upper end portion of the guide plate 8. As described above, the engagement hole 8 a that engages with the annular groove 43 b of the anchor pin 43 is formed in the upper end portion of the guide plate 8. The engagement hole 8 a is defined by an abutting portion 8 d that abuts on the annular step portion 43 d of the anchor pin 43. The contact portion 8d is formed in a spherical shape with the center of friction G as the center and the radius of curvature as R, similar to the annular step portion 43d of the anchor pin 43.

  As shown in FIG. 2, an engagement recess 8 b that engages with the annular groove 43 b is formed at the lower end of the guide plate 8. The engaging recess 8 b is defined by a contact portion 8 e that contacts the annular step portion 43 d of the anchor pin 43. The contact portion 8e is formed in a spherical shape having the friction center point G as the center and the radius of curvature as R, similarly to the contact portion 8d.

  As a result, the contact portions 8 d and 8 e of the guide plate 8 are in sliding contact with the annular step portion 43 d of the anchor pin 43 in a planar shape, and the guide plate 8 rotates around the friction center point G.

  Not limited to this, one of the contact portions 8d and 8e of the guide plate 8 and the annular step portion 43d of the anchor pin 43 is formed in a spherical shape, and the other is formed in a tapered shape (conical surface shape). May be.

  In FIG. 6C, the dimension D is an opening diameter of the engagement hole 8 a of the guide plate 8. The opening diameter D is formed larger at a predetermined ratio with respect to the diameter P of the annular bottom surface 43e of the anchor pin 43. As a result, a gap 51 having a predetermined dimension is defined between the engagement hole 8 a of the guide plate 8 and the annular bottom surface 43 e of the anchor pin 43.

  Thereby, when the anchor pin 43 rotates with respect to the guide plate 8, the engagement hole 8a of the guide plate 8 and the annular bottom surface 43e of the anchor pin 43 do not interfere with each other.

  The right caliper arm 12 is provided with an actuator 60 that presses the brake 7 against the disk 6 via the guide plate 8. The actuator 60 is disposed between the adjusters 41.

  In the actuator 60, the elastic film 75 presses the brake 7 through the piston 65 by the pressurized air (gas) supplied to the driving pressure chamber 63 from an air pressure source mounted on the railway vehicle.

  The actuator 60 includes an accommodation wall 12b formed on the caliper arm 12, an elastic film 75 attached to the accommodation wall 12b, a cover 61 fastened to the accommodation wall 12b, an accommodation wall 12b, this elastic film 75, and this cover. And a drive pressure chamber 63 defined between 61 and a piston 65 interposed between the elastic membrane 75 and the brake 7.

  The caliper arm 12 has an annular mounting seat 12a that extends around the opening edge of the receiving wall 12b. A plurality of screw holes are formed in the mounting seat 12a with a predetermined interval, and the cover 61 is fastened via bolts 62 that are screwed into the screw holes. A peripheral edge 76 of the elastic film 75 is sandwiched between the mounting seat 12 a and the cover 61.

  As shown in FIG. 2, the cover 61 is formed in a dish shape in which a portion defining the driving pressure chamber 63 is recessed in a concave shape.

  The elastic film 75 is formed of a resin elastic material. The elastic film 75 may be formed with a bellows using a resin elastic material combined with a reinforcing material such as carbon fiber or Kevlar fiber. The elastic film may be formed by using a bellows made of a thin metal plate, a rubber tube, or a diaphragm.

  The elastic film 75 includes a peripheral edge portion 76 sandwiched between the mounting seat 12 a and the cover 61, a bellows portion 77 that expands and contracts along the housing wall 12 b, and a pressing film portion 79 that faces the control ring 7.

  A piston 65 is interposed between the pressing film portion 79 of the elastic film 75 and the brake 7. The elastic film 75 presses the control member 7 in the X-axis direction via the piston 65 by the air pressure guided to the drive pressure chamber 63, and presses the control member 7 against the disk 6.

  As shown in FIG. 3, the cross-sectional shapes of the piston 65 and the driving pressure chamber 63 are substantially oval. The housing wall 12 b is formed in a long cylindrical surface shape that penetrates the caliper arm 12. The mounting seat 12a (see FIG. 2) also has a substantially oval inner shape and outer shape. The cover 61 has a substantially oval outer shape similar to the mounting seat 12a.

  Since the elastic film 75 is stretched along the substantially oval piston 65 and the housing wall 12b, the elastic film 75 does not have a bent portion, so that sufficient durability is ensured.

  However, the present invention is not limited to this, and the cross-sectional shapes of the piston 65 and the accommodating wall 12b may be configured to be elliptical or other shapes.

  As shown in FIG. 2, the piston 65 is connected to the guide plate 8, and is displaced in the X-axis direction together with the guide plate 8 guided through the upper and lower anchor pins 43, and the movement of the elastic film 75 is transmitted to the restrictor 7. To do.

  As coupling means for coupling the piston 65 to the guide plate 8, the piston 65 is fastened to the guide plate 8 via a plurality of bolts (not shown).

  The coupling means is not limited to this, and the piston 65 may be coupled to the guide plate 8 via a coupling member such as a key or other means.

  As shown in FIG. 3, the caliper arm 12 is provided with an inlet portion 18, and a pneumatic pipe communicating with a pneumatic source (not shown) is connected to the inlet portion 18. A switching valve operated by a controller (not shown) is provided between the air pressure source and the driving pressure chamber 63. The switching valve is held at a position for guiding atmospheric pressure to the driving pressure chamber 63 when braking is released, and is held at a position for guiding pressurized air from the air pressure source to the driving pressure chamber 63 during braking.

  Next, the operation of the caliper brake device 1 will be described.

  When the pressure guided from the inlet portion 18 to the driving pressure chamber 63 is reduced when the brake is released, the air in the driving pressure chamber 63 is discharged from the inlet portion 18, the bellows portion 77 contracts, and the control 7 is returned to the return spring 44. It is separated from the disk 6 by the biasing force. At this time, the gap W with the disk 6 is adjusted to be substantially constant by the gap adjusting mechanism 45.

  When the air pressure guided to the driving pressure chamber 63 during braking is increased, the elastic film 75 expands, and the elastic film 75 presses the brake 7 against the disk 6 via the piston 65. As a result, the braking device 7 applies a frictional force to the disk 6 and brakes the rotation of the wheels.

  Thus, since the actuator 60 is operated by the air pressure, an air-oil converter (hydraulic power source) and hydraulic piping mounted on the railway vehicle are not necessary, and the weight of the railway vehicle is reduced.

  However, the present invention is not limited thereto, and a hydraulic piston for guiding the hydraulic pressure to the driving pressure chamber may be provided as an actuator of the elastic membrane type caliper brake device. In this case, the pressure receiving area of the actuator is expanded compared to the conventional hydraulic piston type caliper brake device, so that the required pressing force can be secured with a low oil pressure, and no pressure increase by the air oil converter is required. The size of the vessel will be reduced.

  The restrictor 7 is supported so that the upper and lower ends of the guide plate 8 are engaged with anchor pins 43 protruding from the adjusters 41 so as to be able to advance and retreat relative to the disk 6, and the braking reaction force of the restrictor 7 is supported. Is done.

The piston 65 is fastened to the guide plate 8 by a plurality of bolts (not shown) and is supported by the guide plate 8 so as to be able to advance and retreat, so that the piston side surface 65c of the piston 65 is slidably contacted with the caliper body 10. There is no need to provide a guide that supports the support. As a result, the piston 65 can efficiently transmit the air pressure guided to the drive pressure chamber 63 to the guide plate 8 without causing sliding resistance with respect to the guide (caliper body 10). Then, as the wear of the lining 9 proceeds, the piston 65 is also changed quantity to be extruded to the caliper arm 12, sufficient mechanical efficiency is maintained.

  As shown in FIG. 4, in the longitudinal sectional view including the X axis and the Y axis, the center axis Oa of the anchor pin 43 is inclined about 1 degree with respect to the rotation axis Od of the disk 6 by an external force acting on the vehicle. In this case, the abutting portions 8d and 8e provided on the upper and lower sides of the guide plate 8 slide with respect to the annular step portion 43d of the upper and lower anchor pins 43, so that the guide plate 8 together with the piston 65 is Z with respect to the anchor pins 43. Rotate around the axis. As a result, the friction surface 9a of the restrictor 7 is in sliding contact with the rotating surface 6a of the disk 6 in parallel, the surface pressure of the friction surface 9a against the disk 6 is kept uniform, and the braking force is increased. Uneven wear can be suppressed.

  As shown in FIG. 5, in the cross-sectional view including the X axis and the Z axis, the caliper arm 12 is bent by the braking reaction force, so that the center axis Oa of the anchor pin 43 is about 1 degree with respect to the rotation axis Od of the disk 6. When the guide plate 8 is inclined, the contact portions 8d and 8e provided on the upper and lower sides of the guide plate 8 slide with respect to the annular step portion 43d of the upper and lower anchor pins 43, so that the guide plate 8 together with the piston 65 is Y with respect to the anchor pin 43. Rotate around the axis. As a result, the friction surface 9a of the restrictor 7 is in sliding contact with the rotating surface 6a of the disk 6 in parallel, the surface pressure of the friction surface 9a against the disk 6 is kept uniform, and the braking force is increased. Uneven wear can be suppressed.

  When the guide plate 8 rotates with respect to the anchor pin 43, the piston 65 also rotates together with the guide plate 8, so that the air pressure guided to the drive pressure chamber 63 can be efficiently transmitted to the guide plate 8, and sufficient machinery can be obtained. Efficiency is maintained and braking force is not weakened.

As described above, in the present embodiment, a caliper brake device for a vehicle that applies a frictional force across the disk 6 that rotates together with the wheel 5, and includes a brake 7 that is in sliding contact with the disk 6 and applies the frictional force. The guide plate 8 that supports the control 7, the actuator 60 that presses the control 7 against the disk 6 through the guide plate 8, the caliper body 10 that is supported by the vehicle body (cart), and the caliper body 10 Two anchor pins 43 that support the guide plate 8 so as to be able to advance and retreat with respect to the disk 6 and sandwich the actuator 60, and a rotation support mechanism that supports the guide plate 8 so as to be rotatable with respect to the anchor pin 43. 50.

  Based on the above configuration, the guide plate 8 rotates with respect to the anchor pin 43 via the rotation support mechanism 50 following the inclination of the disc 6 and the caliper body 10 that occur during braking. The friction surface 9a is in sliding contact with the rotating surface 6a of the disk 6 in parallel, the surface pressure of the friction surface 9a against the disk 6 is kept uniform, the braking force is increased, and uneven wear of the brake 7 is suppressed.

  In the present embodiment, the anchor pin 43 has an annular step 43d that engages with the guide plate 8, and the rotation support mechanism 50 has a configuration in which the annular step 43d is formed in a spherical shape.

  Based on the above configuration, the guide plate 8 is rotated with respect to the anchor pin 43 while being in sliding contact with the annular step portion 43d, so that the friction surface 9a of the control 7 is in sliding contact with the rotation surface 6a of the disk 6 in parallel. Uneven wear of the restrictor 7 can be suppressed.

  In the present embodiment, the anchor pin 43 has an annular step portion 43d that engages with the guide plate 8, the guide plate 8 has contact portions 8d and 8e that contact the annular step portion 43d, and the rotation support mechanism 50 is The contact portions 8d and 8e are formed in a spherical shape.

  Based on the above configuration, the guide plate 8 rotates with respect to the anchor pin 43 while the contact portions 8d and 8e are in sliding contact with the annular step portion 43d, so that the friction surface 9a of the restrictor 7 becomes the rotation surface 6a of the disk 6. On the other hand, it is slid in parallel to suppress uneven wear of the brake 7.

  In the present embodiment, the actuator 60 includes an elastic film 75 attached to the caliper body 10, a drive pressure chamber 63 defined by the elastic film 75 and supplied with fluid pressure (gas pressure) during braking, and an elastic film 75. A piston 65 interposed between the control wheels 7 and coupling means for coupling the piston 65 to the guide plate 8 are provided. The elastic film 75 is caused by fluid pressure (gas pressure) guided to the drive pressure chamber 63 during braking. The piston 65 swells and presses the control member 7 against the disk 6.

  Based on the above configuration, the piston 65 is supported by the guide plate 8 to which the piston 65 is fastened so as to be able to advance and retreat, so there is no need to have a portion (guide) that is slidably supported by the caliper body 10. . For this reason, without causing sliding resistance between the piston 65 and the caliper body 10, even if the guide plate 8 rotates with respect to the anchor pin 43, the fluid pressure guided to the drive pressure chamber 63 is efficiently guided. 8 told.

  In the present embodiment, the elastic film 75 has a bellows portion 77 that expands and contracts between the caliper body 10 and the piston 65, and the caliper body 10 has an accommodating wall 12b that surrounds the bellows portion 77 and extends in a cylindrical shape. The accommodation wall 12b restricts the bellows portion 77 of the elastic film 75 from expanding in the direction parallel to the disk 6 (including the Y axis and Z axis) by the air pressure guided to the driving pressure chamber 63 during braking. The air flow rate required to press the brake 7 is reduced, and the responsiveness that the elastic film 75 presses the brake 7 and brakes the wheel 5 can be enhanced.

  In the present embodiment, since the caliper body 10 is slidably supported via the upper and lower slide pins 30 and 32, one of the pair of caliper arms 12 extending right across the disk 6 (right side) The actuator 60 can be provided only on the caliper arm 12), and the caliper brake device 1 can be prevented from being enlarged.

  However, the present invention is not limited to this, and the actuators 60 may be provided on both of the pair of caliper arms extending across the disk 6. In this case, the caliper body 10 does not need to be floating supported so as to be slidable in the X-axis direction, and the caliper body 10 is fixed to the carriage (vehicle body).

  Further, a structure in which the guide plate is rotatably supported by the anchor pin of the present invention may be applied to a caliper brake device that includes a hydraulic cylinder that presses the control member against the disc by operating hydraulic pressure.

  The present invention is not limited to the above-described embodiment, and it is obvious that various modifications can be made within the scope of the technical idea.

DESCRIPTION OF SYMBOLS 1 Caliper brake device 5 Wheel 6 Disc 7 Control device 8 Guide plate 8b Engagement recessed part 8d Contact part 8e Contact part 9 Lining 10 Caliper main body 12 Caliper arm 43 Anchor pin 43b Annular groove 43d Annular step part 50 Rotation support mechanism 51 Gap 63 Drive pressure chamber 65 Piston 75 Elastic membrane

Claims (6)

A caliper brake device for a vehicle that applies frictional force across a disk that rotates with a wheel,
A control device that slidably contacts the disk and imparts frictional force;
A guide plate for supporting the restrictor;
An actuator for pressing the restrictor against the disc via the guide plate;
A caliper body supported by the vehicle body;
Two anchor pins arranged to support the guide plate in the caliper body so as to be movable back and forth with respect to the disk, and to sandwich the actuator;
A caliper brake device comprising: a rotation support mechanism that supports the guide plate so as to be rotatable about at least two axes with respect to the anchor pin. The anchor pin has an annular step that engages with the guide plate;
The caliper brake device according to claim 1, wherein the rotation support mechanism has the annular step portion formed in a spherical shape.   The annular stepped portion is formed in a spherical shape centered at a point where a central axis that halves the thickness of an effective wear allowance of the control member and a central axis of the anchor pin intersect each other. The caliper brake device according to claim 2. The anchor pin has an annular step that engages with the guide plate;
The guide plate has a contact portion that contacts the annular stepped portion,
The caliper brake device according to any one of claims 1 to 3, wherein the rotation support mechanism has a spherical contact portion.   The contact portion is formed in a spherical shape centered at a point where a central axis that halves the thickness of the effective wear allowance of the brake member and a central axis of the anchor pin intersect. The caliper brake device according to claim 4. The actuator is
An elastic membrane attached to the caliper body;
A driving pressure chamber defined by the elastic membrane and supplied with fluid pressure during braking;
The piston interposed between the elastic membrane and the restrictor;
Coupling means for coupling the piston to the guide plate;
6. The structure according to claim 1, wherein the elastic film is swelled by a fluid pressure guided to the driving pressure chamber during braking, and the piston presses the control wheel against the disk. 6. Caliper brake device.

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