JP2012035672A - Caliper braking device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a caliper braking device which can secure heat resistance of a piston, an elastic membrane, and the like.SOLUTION: In a vehicular caliper braking device, a disk 6 rotated together with a wheel 5 are sandwiched to give a frictional force. The piston 65 presses a brake block 7 into the disk 6 in such a way that the elastic membrane 50 is expanded by fluid pressure led by an elastic membrane chamber 63 when braking. The piston 65 is configured to make a contact area of a piston press surface 65a contacting the brake block 7 form smaller than a press area of the piston rear surface 65b pressed by the elastic membrane 50.

Description

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

  Generally, a hydraulic brake of a railway vehicle is equipped with an air-oil converter that converts air pressure supplied from an air pressure source to oil pressure, and a caliper brake device is operated by the oil pressure supplied from the air-oil converter via a hydraulic pipe. It is like that.

  Patent Documents 1 and 2 disclose a hydraulic caliper brake device for a railway vehicle that operates by hydraulic pressure.

  In recent years, it has been desired to install a pneumatic caliper brake device that is operated by a pneumatic pressure supplied from a pneumatic pressure source on a railway vehicle, and to eliminate the above-described air-oil converter and hydraulic piping.

The pneumatic brake device disclosed in Patent Document 3 includes an elastic film that defines a driving pressure chamber, and a piston that is interposed between the elastic film and the brake, and is guided to the driving pressure chamber during braking. The elastic film expands due to the air pressure, and the piston presses the brake against the disc.
JP-A-8-226469 JP-A-8-226471 JP 2009-162245 A

  However, in the pneumatic brake device disclosed in Patent Document 3, the piston has an elliptical piston pressing surface that presses the back surface of the restrictor in a wide range, and the piston pressing surface that abuts the restrictor is in contact with the piston. Since the contact area is large, the frictional heat generated in the restrictor tends to be transmitted from the restrictor to the piston, elastic membrane, etc. via the piston pressing surface, and it is difficult to ensure the heat resistance of the piston, elastic membrane, etc. It was.

  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 that can ensure heat resistance of a piston, an elastic film, and the like.

  The present invention relates to a caliper brake device for a vehicle that applies a frictional force across a disk that rotates with a wheel, a caliper body that is supported by a vehicle body, a brake member that slidably contacts the disk and applies a frictional force, An actuator that presses the brake against the disc. The actuator includes an elastic film attached to the caliper body, a drive pressure chamber defined by the elastic film and supplied with fluid pressure during braking, and the elastic film and the control film. A piston interposed between the wheels, and the elastic film expands due to the fluid pressure guided to the driving pressure chamber during braking so that the piston presses the brake against the disc, and the piston contacts the brake The contact area of the piston pressing surface was formed smaller than the pressing area of the piston back surface pressed against the elastic membrane.

  According to the present invention, the piston is reduced in the contact area of the piston pressing surface that is in contact with the control against the pressing area of the back surface of the piston that is pressed by the elastic film, so that the frictional heat generated in the control is elastic with the piston. Transmission to the membrane is suppressed, and heat resistance of the elastic membrane, piston, etc. is sufficiently ensured.

The top view of the caliper brake device which shows embodiment of this invention. Similarly, a longitudinal sectional view of a caliper brake device. The side view of a caliper brake device. Similarly, (a) is a side view of the piston, and (b) is a cross-sectional view taken along line CC. The side view of the piston which shows other embodiment. The side view of the piston which shows other embodiment.

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

  1 to 3 are three views 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, and H is the center line of the wheel 5 orthogonal to the rotation center axis O. In FIGS. 1 and 3, reference numeral 20 denotes a support frame fixed on a carriage (vehicle body) (not shown) of the railway vehicle, and reference numeral 10 denotes a caliper body supported by the support frame 20.

  As shown in FIG. 3, the caliper body 10 is floatingly supported on the support frame 20 by the 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 its upper and lower ends are prevented from coming off by engaging with an anchor pin 43 provided on the anchor block 48 and fixed to the left caliper arm 12 (see FIG. 1).

  As shown in FIG. 3, 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.

  As shown in FIG. 2, the restrictor 7 includes a lining 9 as a friction material in 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 formed in a disk shape, and is coupled to the lining back plate 19 via a rivet 17. A disc spring (not shown) is interposed between the lining 9 and the lining back plate 19.

  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 step portions 43b. An engagement hole 8 a that engages with the annular step 43 b is formed at the upper end of the guide plate 8. An engaging recess 8b that engages with the annular step 43b is formed at the lower end of the guide plate 8 (see FIG. 2).

  The upper and lower ends of the guide plate 8 are supported so as to be able to move forward and backward with respect to the disk 6 by engaging the upper and lower ends of the guide plate 8 with the annular stepped portions 43 b of the anchor pins 43, and the upper and lower ends of the lining back plate 19 are supported by the anchor pins. By engaging with 43, the braking reaction force is supported.

  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).

  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 8 c of the guide plate 8. Next, the lower adjuster 41 is attached to the caliper arm 12, the guide plate 8 is engaged with and supported by the anchor pin 43, and the lining back plate 19 is engaged with the anchor pin 43 to prevent the restrictor 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.

  The adjuster 41 is provided with a return spring 44 that urges the restrictor 7 away from the disk 6 via the anchor pin 43, and a gap adjusting mechanism 45 that adjusts the gap between the restrictor 7 and the disk 6 to be substantially constant when the brake is released. 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 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 membrane 50 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 a storage wall 12b formed on the caliper arm 12, an elastic film 50 attached to the storage wall 12b, a cover 61 fastened to the storage wall 12b, a storage wall 12b, the elastic film 50, and the cover. And a drive pressure chamber 63 defined between 61 and a piston 65 interposed between the elastic membrane 50 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 50 a of the elastic film 50 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 50 is formed of a resin elastic material. The elastic film 50 is not limited to a resin elastic material, and a bellows may be formed using a composite of reinforcing materials such as carbon fiber and 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 50 includes a peripheral edge part 50 a sandwiched between the mounting seat 12 a and the cover 61, a bellows part 50 b that expands and contracts along the housing wall 12 b, and a pressing film part 50 c that faces the control ring 7.

  A piston 65 is interposed between the pressing film portion 50 c of the elastic film 50 and the brake 7. The elastic film 50 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 shown in FIG. 2 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 50 is stretched along the substantially oval piston 65 and the housing wall 12b, the elastic film 50 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.

  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 transmits the movement of the elastic film 50 to the brake 7.

  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.

  4A is a side view of the piston 65 viewed from the disk 6 side, and FIG. 4B is a cross-sectional view taken along line CC of FIG. 4A.

  The piston 65 has a piston pressing surface 65a that contacts the guide plate 8, a piston back surface 65b that contacts the pressing film portion 50c of the elastic film 50, and a piston side surface 65c that faces the housing wall 12b.

  The piston 65 has a back surface 65b formed in a substantially oval shape, and a piston side surface 65c formed in a substantially long cylindrical surface shape.

  The piston 65 is formed with concave concave piston heat insulating recesses 67, 68, and 69 at a portion facing the guide plate 8, so that the contact area of the piston pressing surface 65 a that contacts the guide plate 8 is the elastic film 50. It is formed to be smaller than the pressing area of the piston back surface 65b pressed against the surface.

  As shown in FIG. 4A, the control wheel 7 is provided with a plurality of linings 9 arranged in two rows. Each lining 9 is arranged so as to be aligned along the disk 6 of the wheel 5.

  On the side surface shown in FIG. 4 (a) (as viewed from the direction of the rotation axis O of the disk 6), the restrictor 7 has sliding contact areas C1 and C2 in which the lining 9 slides (slidably contacts) the disk 6. The lining 9 has non-sliding contact areas D1, D2, and D3 where the disk 6 does not slide. The non-sliding contact region D2, the sliding contact region C1, the non-sliding contact region D1, the slidable contact region C2, and the non-sliding contact region D3 each extend in a strip shape along the disk 6, and the outer periphery from the inner peripheral side in the radial direction of the wheel 5 It is lined up to the side.

  The central piston heat-insulating recess 67 is formed on the side surface shown in FIG. 4A (as viewed from the direction of the rotation axis O of the disk 6) and is located in a region including the non-sliding contact region D1 of the brake 7. The

  The piston heat insulating recess 67 is formed in a groove shape having two recess side surfaces 67a and 67b. One recess side surface 67 a is formed along the inner circumferential row of the linings 9. The other concave side surface 67 b is formed along the outer peripheral row of the lining 9. Thus, the piston heat insulating recess 67 is formed along the non-sliding contact region D <b> 1 facing the central annular portion of the disk 6.

  On the side surface shown in FIG. 4A (as viewed from the direction of the rotation axis O of the disk 6), the piston heat-insulating recess 68 on the inner peripheral side is located in a region including the non-sliding contact region D2 of the brake 7. It is formed.

  The piston heat insulating recess 68 is formed in a notch shape having one recess side surface 68a. The concave side surface 68 a is formed to be curved along the inner circumferential row of the lining 9. Thus, the piston heat insulating recess 68 is formed along the non-sliding contact region D <b> 2 facing the inner peripheral annular portion of the disk 6.

  The piston heat-insulating recess 69 on the outer peripheral side is formed on the side surface shown in FIG. 4A (as viewed from the direction of the rotation axis O of the disk 6) and located in a region including the non-sliding contact region D3 of the restrictor 7. Is done.

  The piston heat insulating recess 69 is formed in a notch shape having one recess side surface 69a. The concave side surface 69 a is formed along the outer peripheral row of the lining 9. In this way, the piston heat insulating recess 69 is formed along the non-sliding contact region D <b> 3 facing the outer peripheral annular portion of the disk 6.

  The piston pressing surface 65a of the piston 65 extends on the side surface shown in FIG. 4A (as viewed from the direction of the rotational axis O of the disk 6) 2 to areas including the sliding contact areas C1 and C2 of the control 7 respectively. It is formed into two strips. As a result, as shown in FIG. 4B, the piston 65 has a piston heat-insulating recess 67, 68, 69 in a cross section in which the piston pressing surface 65 a contacting the guide plate 8 is sandwiched between the elastic film 50 and the lining 9. The movement of the elastic film 50 is efficiently transmitted to the lining 9 without being disposed.

  The piston 65 is formed by injection molding a resin. The piston heat insulating recesses 67, 68, 69 are formed by a mold used at the time of injection molding.

  However, the present invention is not limited to this, and the piston 65 may have a tapered shape in which the cross-sectional area decreases from the piston back surface 65b to the piston pressing surface 65a. In this case, the piston heat insulating recesses 67 and 69 provided on the inner and outer circumferences of the piston 65 can be eliminated.

  Further, the piston 65 is not limited to resin, and may be formed of metal or other material.

  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 50 b 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 50 expands, and the elastic film 50 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.

  Frictional heat generated in the sliding contact portion between the disk 6 and the lining 9 during braking is transmitted from the control 7 to the guide plate 8, the piston 65, and the elastic film 50. In response to this, the piston 65 reduces the contact area of the piston pressing surface 65a that contacts the guide plate 8 by the piston heat-insulating recesses 67, 68, 69. 50 is suppressed from being transmitted. Thereby, the heat resistance of the elastic film 50 and the piston 65 made of resin is sufficiently ensured.

  Not limited to this, a heat insulating plate is interposed between the piston 65 and the guide plate 8, and the heat of the control device 7 is suppressed from being transmitted to the piston 65 and the elastic film 50 by the heat insulating plate. Also good.

  On the side surface shown in FIG. 4A, the piston heat insulating recesses 67, 68 and 69 are formed so as to avoid the position facing the lining 9, and the piston pressing surface 65 a is guided at the position facing the lining 9. It arrange | positions so that the plate 8 may be contact | abutted. As a result, the rigidity of the piston 65, the guide plate 8, and the like is ensured, so that elastic deformation of the piston 65, the guide plate 8, etc. is suppressed during braking, and the mechanical efficiency at which the piston 65 transmits the movement of the elastic film 50 to the lining 9 is achieved. Is not impaired. Further, since the surface pressure of the restrictor 7 with respect to the disk 6 is made uniform, the friction coefficient of the restrictor 7 is kept high, the original braking force of the restrictor 7 is exhibited, and the restrictor 7 and the disk. By suppressing the local temperature rise of 6, it is possible to prevent uneven wear of the brake 7 and the disk 6.

  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).

  Even if the amount by which the piston 65 is pushed out by the caliper arm 12 changes as the lining 9 wears, sufficient mechanical efficiency can be obtained.

  Since the actuator 60 is operated by air pressure, an air-oil converter (hydraulic power source) and hydraulic piping mounted on the railway vehicle become unnecessary, and the railway vehicle can be reduced in weight.

  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.

  In the present embodiment, a caliper brake device for a vehicle that applies frictional force across a disk 6 that rotates together with a wheel 5, and is slidably contacted with the caliper main body 10 supported by a vehicle body (cart) and friction. A brake member 7 for applying force and an actuator 60 for pressing the brake member 7 against the disk 6 are provided. The actuator 60 is defined by the elastic film 50 attached to the caliper body 10 and the elastic film 50. A fluid pressure that is provided with a drive pressure chamber 63 to which fluid pressure (gas pressure) is supplied during braking and a piston 65 interposed between the elastic membrane 50 and the brake 7 and is guided to the drive pressure chamber 63 during braking. The elastic film 50 is expanded by (gas pressure) and the piston 65 presses the restrictor 7 against the disk 6. The piston 65 is a piston pressing surface 65 that abuts against the restrictor 7. Contact area is configured to be smaller than the pressing area of the piston rear 65b which is pressed into the elastic film 50.

  Based on the above configuration, the piston 65 is generated in the brake 7 because the contact area of the piston pressing surface 65a that contacts the brake 7 is reduced with respect to the pressing area of the piston back surface 65b pressed by the elastic membrane 50. The frictional heat is prevented from being transmitted to the piston 65 and the elastic film 50, and the heat resistance of the elastic film 50 and the piston 65 is sufficiently ensured.

  In this embodiment, the restrictor 7 includes a lining 9 that is in sliding contact with the disk 6, a lining back plate 19 that supports the lining 9, and a guide plate 8 that supports the lining back plate 19. The piston pressing surface 65a that presses the guide plate 8 and the piston heat insulating recesses 67, 68, and 69 that are recessed in the piston pressing surface 65a are used.

  Based on the above configuration, the piston 65 is a piston that abuts against the guide plate 8 while securing its rigidity by forming the recessed piston heat-insulating recesses 67, 68, 69 in a portion facing the guide plate 8. The contact area of the pressing surface 65a is reduced.

  In the present embodiment, the piston pressing surface 65 a is formed in a region including the sliding contact regions C 1 and C 2 where the lining 9 is in sliding contact with the disk 6 on the side surface of the brake member 7. 69, the lining 9 is formed in a region including the non-sliding regions D1, D2, and D3 where the disk 9 is not slidably contacting.

  Based on the above configuration, the piston pressing surface 65a is arranged so as to abut against the guide plate 8 at a position facing the lining 9 and press the brake 7, so that the surface pressure of the lining 9 against the disc 6 is made uniform. The friction coefficient of the lining 9 is kept high, the original braking force of the lining 9 is exhibited, and the local temperature rise of the lining 9 and the disk 6 is suppressed, so that the uneven wear of the brake 7 and the disk 6 is suppressed. Can be prevented.

  In the present embodiment, the restrictor 7 is provided with a plurality of linings 9 arranged side by side, and on the side surface of the restrictor 7, the piston pressing surface 65 a is formed in a strip shape along the row of linings 9.

  Based on the above configuration, the piston pressing surface 65a is disposed so as to contact the guide plate 8 at a position facing the plurality of linings 9, so that the surface pressure of the brake 7 against the disk 6 is made uniform, and the brake 7 And uneven wear of the disk 6 can be prevented.

  In the present embodiment, a guide plate 8 that supports the restrictor 7, an anchor pin 43 that supports the caliper body 10 so that the guide plate 8 can move forward and backward with respect to the disk 6, and a coupling means that couples the piston 65 to the guide plate 8. It was set as the structure provided with.

  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, the fluid pressure guided to the drive pressure chamber 63 is efficiently transmitted to the guide plate 8 without causing sliding resistance between the piston 65 and the caliper main body 10. As a result, the actuator 60 is reduced in size and weight, and the actuator 60 that is operated by air pressure can be interposed in a limited space of the caliper body 10.

  In the present embodiment, the caliper body 10 is provided with a pair of anchor pins 43 that support both ends of the guide plate 8 so as to be able to advance and retreat with respect to the disk 6, and the drive pressure chamber 63 is disposed between the anchor pins 43. The movement of the piston 65 and the guide plate 8 pressing the brake 7 against the disk 6 is smoothly performed through the anchor pins 43 and the pressure receiving area of the elastic membrane 50 is increased in the space between the anchor pins 43. It is possible to sufficiently ensure and apply the required pressing force to a wide range of the control device 7.

  In the present embodiment, the elastic membrane 50 has a bellows portion 50b that expands and contracts between the caliper body 10 and the piston 65, and the caliper body 10 has an accommodation wall 12b that extends around the bellows portion 50b and extends in a cylindrical shape. The housing wall 12b restricts the bellows portion 50b of the elastic film 50 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 50 presses the brake 7 to brake 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).

  Next, another embodiment shown in FIG. 5 will be described. The restrictor 7 is provided with a plurality of linings 9 arranged along the disk 6. Each lining 9 is coupled to a lining back plate via a rivet 17.

  On the side surface shown in FIG. 5, the restrictor 7 has one sliding contact area C <b> 5 where the lining 9 is in sliding contact with the disk 6, and two non-sliding contact areas D <b> 5 and D <b> 6 where the lining 9 is not in sliding contact with the disk 6.

  The piston heat-insulating recesses 71 and 72 are formed in regions including the non-sliding contact regions D5 and D6 of the control device 7, respectively.

  The piston heat-insulating recess 71 on the inner peripheral side is formed so as to include a non-sliding contact region D <b> 5 that faces the inner peripheral portion of the disk 6. The piston heat insulating recess 71 is formed such that the recess side surface 71 a is curved along the inner peripheral portion of the lining 9.

  The piston heat-insulating recess 72 on the outer peripheral side is formed so as to include a non-sliding contact region D <b> 6 that faces the outer peripheral portion of the disk 6. The piston heat insulating recess 72 is formed such that the recess side surface 72 a is curved along the outer peripheral portion of the lining 9. Thereby, the piston pressing surface 65a is formed along the rotational circumferential direction of the disk 6 so as to avoid the inner and outer peripheral portions of the piston 65.

  The piston pressing surface 65a of the piston 65 is formed in one band shape in a region that includes the sliding contact region C5 of the brake 7. As a result, the piston 65 has a piston pressing surface 65 a that contacts the guide plate 8 disposed between the elastic film and the lining 9, and transmits the movement of the elastic film to the lining 9.

  In this way, the piston 65 reduces the contact area of the piston pressing surface 65a that abuts against the restrictor 7, so that the frictional heat generated in the restrictor 7 is suppressed from being transmitted to the piston 65 and the elastic membrane 50, and is elastic. The heat resistance of the membrane 50 and the piston 65 is sufficiently ensured.

  Next, another embodiment shown in FIGS. 6A to 6F will be described.

  In the embodiment shown in FIG. 6A, the piston heat insulating recess 73 is formed only on the inner peripheral portion of the piston 65. The piston heat insulating recess 73 is formed in a notch shape having one recess side surface 73a. The concave side surface 73a is formed to be curved along the inner peripheral portion of the lining. Thereby, the piston pressing surface 65 a is formed along the rotational circumferential direction of the disk 6 so as to avoid the inner peripheral portion of the piston 65.

  In the embodiment shown in FIG. 6B, the piston heat insulating recess 74 is formed only on the inner peripheral portion of the piston 65. The piston heat insulating recess 74 is formed in a notch shape having one recess side surface 74a. The concave side surface 74a is formed in a planar shape. Thereby, the piston pressing surface 65 a is formed along the rotational circumferential direction of the disk 6 so as to avoid the inner peripheral portion of the piston 65.

  In the embodiment shown in FIG. 6C, the piston heat insulating recess 75 is formed only on the outer peripheral portion of the piston 65. The piston heat insulating recess 75 is formed in a notch shape having one recess side surface 75a. The concave side surface 75a is formed in a planar shape. Thereby, the piston pressing surface 65 a is formed along the rotational circumferential direction of the disk 6 so as to avoid the outer peripheral portion of the piston 65.

  In the embodiment shown in FIG. 6D, piston heat-insulating concave portions 76 and 77 are formed on the inner peripheral portion and the outer peripheral portion of the piston 65, respectively. The piston heat insulating recesses 76 and 77 are formed in a notch shape having one recess side surface 76a and 77a, respectively. The concave side surfaces 76a and 77a are each formed in a planar shape. Thus, the piston pressing surface 65 a is formed along the rotational circumferential direction of the disk 6 so as to avoid the inner peripheral portion and the outer peripheral portion of the piston 65.

  In the embodiment shown in FIG. 6E, piston heat-insulating recesses 78 and 79 are formed in the upper and lower portions of the piston 65, respectively. The piston heat insulating recesses 78 and 79 are formed in a cutout shape having one recess side surface 78a and 79a, respectively. The concave side surfaces 78a and 79a are each formed in a planar shape. As a result, the piston pressing surface 65 a is formed in the central portion of the piston 65 along the rotational radial direction of the disk 6.

  In the embodiment shown in FIG. 6 (f), one piston heat insulating recess 80 is formed at the center of the piston 65. The piston heat insulating recess 80 is formed in a groove shape having two recess side surfaces 80a and 80b. The concave side surfaces 80a and 80b are each formed in a planar shape. Thereby, the piston pressing surface 65a is formed along the rotational radial direction of the disk 6 so as to avoid the central portion of the piston 65.

  As described above, in the embodiment shown in FIGS. 5 and 6A to 6D, the piston pressing surface 65 a is formed along the rotational circumferential direction of the disk 6 on the side surface of the brake 7. did.

  Further, in the embodiment shown in FIGS. 6E to 6F, the piston pressing surface 65 a is formed along the rotational radial direction of the disk 6 on the side surface of the brake 7.

  Based on the above configuration, the piston pressing surface 65a is disposed so as to contact the guide plate 8 at a position facing the lining 9, so that the surface pressure of the control 7 against the disc 6 is made uniform, and the control 7 and disc 6 can be prevented from occurring.

  However, the present invention is not limited to this, and the piston heat-insulating concave portion may be formed in a cross shape or another shape, for example, corresponding to the arrangement of the lining.

  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.

1 Caliper brake device
5 wheels 6 discs
7 Control wheel 8 Guide plate 9 Lining
10 Caliper body 12 Caliper arm 19 Lining back plate 20 Support frame 30, 31 Vertical slide pin 41 Adjuster
43 Ankapin
45 Gap adjustment mechanism 50 Elastic membrane 60 Actuator 63 Drive pressure chamber 65 Piston 65a Piston pressing surface 65b Piston back surface 65c Piston side surface 67-69, 71-80 Piston heat insulation recess

Claims (7)

A caliper brake device for a vehicle that applies frictional force across a disk that rotates with a wheel,
A caliper body supported by the vehicle body;
A control device that slidably contacts the disk and imparts frictional force;
An actuator that presses the control against the disc,
This actuator
An elastic membrane attached to the caliper body;
A driving pressure chamber defined by the elastic membrane and supplied with fluid pressure during braking;
A piston interposed between the elastic membrane and the control device,
The elastic membrane expands due to fluid pressure guided to the driving pressure chamber during braking, and the piston presses the brake against the disc.
The piston is
The caliper brake device is characterized in that a contact area of a piston pressing surface that is in contact with the restrictor is formed to be smaller than a pressing area of a piston back surface pressed by the elastic film. The controller is
A lining in sliding contact with the disc;
A lining backboard that supports this lining;
A guide plate for supporting the lining back plate,
The piston is
A piston pressing surface for pressing the guide plate;
The caliper brake device according to claim 1, further comprising a piston heat-insulating recess that is recessed in a concave shape with respect to the piston pressing surface. The piston pressing surface is formed in a region including a sliding contact region where the lining is in sliding contact with the disk on the side surface of the control member,
3. The caliper brake device according to claim 2, wherein the piston heat insulating recess is formed in a region including a non-sliding contact region where the lining does not contact the disk on a side surface of the control member. The control device is provided with a plurality of the linings arranged side by side,
The caliper brake device according to any one of claims 1 to 3, wherein the piston pressing surface is formed in a band shape along a row in which the linings are arranged on a side surface of the restrictor.   The caliper brake device according to any one of claims 1 to 4, wherein the piston pressing surface is formed along a rotational circumferential direction of the disk on a side surface of the restrictor.   The caliper brake device according to any one of claims 1 to 4, wherein the piston pressing surface is formed along a rotational radial direction of the disk on a side surface of the restrictor. A guide plate for supporting the restrictor;
An anchor pin for supporting the guide plate on the caliper body so as to be movable back and forth with respect to the disk;
The caliper brake device according to any one of claims 1 to 6, further comprising coupling means for coupling the piston to the guide plate.

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