WO2012049745A1 - Dispositif à cylindre et dispositif de frein à disque pour véhicule ferroviaire - Google Patents

Dispositif à cylindre et dispositif de frein à disque pour véhicule ferroviaire Download PDF

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Publication number
WO2012049745A1
WO2012049745A1 PCT/JP2010/067968 JP2010067968W WO2012049745A1 WO 2012049745 A1 WO2012049745 A1 WO 2012049745A1 JP 2010067968 W JP2010067968 W JP 2010067968W WO 2012049745 A1 WO2012049745 A1 WO 2012049745A1
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WO
WIPO (PCT)
Prior art keywords
rod
receiving member
piston
cylinder
rotating member
Prior art date
Application number
PCT/JP2010/067968
Other languages
English (en)
Japanese (ja)
Inventor
智也 大野
洋一郎 小澤
丈一 中村
Original Assignee
ナブテスコ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ナブテスコ株式会社 filed Critical ナブテスコ株式会社
Priority to PCT/JP2010/067968 priority Critical patent/WO2012049745A1/fr
Publication of WO2012049745A1 publication Critical patent/WO2012049745A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/2245—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members in which the common actuating member acts on two levers carrying the braking members, e.g. tong-type brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure
    • F16D2121/06—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure for releasing a normally applied brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/36—Helical cams, Ball-rotating ramps

Definitions

  • the present invention relates to a cylinder device capable of moving a rod by fluid pressure, and a railway vehicle disc brake device using the cylinder device.
  • the thing of patent documents 1 is known as a disc brake device for rail vehicles using a cylinder device.
  • the rod is advanced from the cylinder device by air pressure, and a pair of brake levers each provided with one end side are driven on the rod side and the cylindrical member side of the cylinder, and the pair of brake levers A braking force is applied by sandwiching the wheels with a control provided at the end.
  • the thing of patent document 2 is known as a cylinder apparatus.
  • a rod push bar
  • the piston is urged and the piston and the rod are advanced.
  • the length of the brake is determined so that a necessary braking force is generated.
  • the length of the brake lever becomes long, so that there is a problem that the entire disc brake device becomes large.
  • the diameter of the cylinder is determined so as to obtain a desired output.
  • the necessary brake force is generated by adjusting the cylinder diameter.
  • the cylinder device becomes large, resulting in a problem that the entire disc brake device becomes large.
  • the present invention provides a compact cylinder device capable of increasing the urging force by a rod without significantly increasing the size of the device, and a railway vehicle using the cylinder device.
  • An object is to provide a disc brake device.
  • a first feature of the cylinder device is that a cylinder body formed hollow inside, a rod disposed in the cylinder body so as to be movable forward and backward in the axial direction with respect to the cylinder body, and the cylinder body
  • the piston is provided so as to surround the axis of the rod, and is movable in parallel with the forward / backward direction of the rod, and moves in the retracting direction of the rod by fluid pressure, and the piston retracts the rod
  • a force-increasing mechanism that increases the force generated in the piston and acts on the rod so that the rod moves in the advancing direction when moving in the direction.
  • the piston is provided so as to surround the axis of the rod, the range occupied by the piston and the rod in the axial direction of the rod can be reduced. Therefore, for example, by arranging the force-increasing mechanism in a space that can be secured by arranging the piston and the rod as described above, the force that can be applied to the outside from the rod without increasing the size of the cylinder device. Can be bigger. That is, the force that can be applied to the outside from the rod can be increased without excessively increasing the cylinder diameter.
  • a second feature of the cylinder device according to the present invention is that the force-increasing mechanism is inclined with respect to the moving direction of the piston so that the inclined surface provided on the piston and the piston in the retracting direction are A rotating member that is urged by the inclined surface when it moves and rotates in one direction around the axis of the rod, and the rod has an axis of the rod with respect to the cylinder body. It is provided so as not to rotate in the center, and moves in the advance direction as the rotating member rotates in the one direction.
  • the force generated by the piston in the retracting direction can be efficiently converted into the force generated by the rod in the advancing direction.
  • a third feature of the cylinder device includes a first receiving member fixed to the rod, and the rotating member is arranged in the direction parallel to the axial direction of the rod. And a first inclined groove that is inclined in the rotation direction of the rotating member is formed on a surface of the rotating member that faces the first receiving member.
  • the first inclined groove Is provided with a first rolling member that can roll along the inner surface of the first inclined groove, and the first rolling member is sandwiched between the first receiving member and the rotating member. It is supported in the state.
  • the force generated by the piston in the retracting direction of the rod is increased in two stages and converted into the force generated by the rod in the advancing direction. be able to. Further, in order to increase the force, an inclined groove that is inclined in the rotating direction of the rotating member is used, and an excessively large space is not used. Accordingly, it is possible to increase the degree of freedom of arrangement of other mechanisms in the cylinder device while exhibiting a larger boosting function.
  • a fourth feature of the cylinder device according to the present invention is that a plurality of the first inclined grooves and the first rolling members are provided so as to be positioned on a circle around the axis of the rod. It is that.
  • the fifth feature of the cylinder device according to the present invention is that the first rolling member is a sphere.
  • the 6th characteristic in the cylinder apparatus which concerns on this invention was fixed with respect to the said cylinder main body so that the surface on the opposite side to the surface which opposes the said 1st receiving member in the said rotation member may be opposed.
  • a second receiving member is provided, and a second inclined groove that is inclined in a rotating direction of the rotating member is formed on a surface of the rotating member facing the second receiving member, and the second inclined groove is formed in the second inclined groove.
  • the stroke of the rod can be increased without excessively increasing the size of the cylinder device.
  • a seventh feature of the cylinder device according to the present invention is that a receiving member fixed to the rod is provided, and the rotating member is provided to be screwed into a screw thread formed on an outer peripheral surface of the receiving member.
  • the receiving member is configured to move in the advance direction when the rotating member rotates in the one direction.
  • the force generated by the piston in the retracting direction of the rod is increased in two stages. Can be converted into force generated in the advancing direction. Further, in order to increase the force, the screw shape of the rotating member and the receiving member is used, and an excessively large space is not used. Accordingly, it is possible to increase the degree of freedom of arrangement of other mechanisms in the cylinder device while exhibiting a larger boosting function.
  • a feature of the disc brake device for a railway vehicle according to the present invention is that a brake pad is provided at one end, a pair of caliper levers that can rotate around a fulcrum, and the rod at the other end of the one caliper lever.
  • the pair of brake pads are moved closer to each other. Is rotating.
  • the braking force of the railway vehicle disc brake device can be increased, and the device can be made compact.
  • the urging force by the rod can be increased without increasing the size of the cylinder device.
  • FIG. 1 is a side view showing a railway vehicle disc brake device according to an embodiment of the present invention.
  • FIG. 2 is a top view of the railway vehicle disc brake device shown in FIG. 1.
  • FIG. 2 is an S1-S1 cross-sectional view of the cylinder device shown in FIG. The perspective view which shows the piston shown in FIG. The figure which looked at the piston shown in FIG. 4 from the inclined surface side in the axial direction of a rod.
  • FIG. 6 is an S2-S2 cross-sectional view of the piston shown in FIG. The figure which looked at the main body side receiving member shown in FIG. 3 from the rotation member side in the axial direction of a rod.
  • FIG. 8 is an S3-S3 cross-sectional view of the main body side receiving member shown in FIG. 7.
  • FIG. 11 is an S4-S4 sectional view of the rotating member shown in FIG.
  • FIG. 13 is an S5-S5 cross-sectional view of the rod side receiving member shown in FIG.
  • FIG. 1 is a side view showing a railway vehicle disc brake device 1 according to an embodiment of the present invention.
  • FIG. 2 is a top view of the railway vehicle disc brake device 1 shown in FIG.
  • this railway vehicle disc brake device 1 includes a caliper body 11 attached to a vehicle body 100, and a working fluid is supplied to a cylinder device 2 mounted on the caliper body 11.
  • a working fluid is supplied to a cylinder device 2 mounted on the caliper body 11.
  • the pair of brake levers 12 and 12 are operated, and a pair of brake pads 13 and 13 (control members) attached to the distal ends of the brake levers 12 and 12 are used as wheels 14 of the railway vehicle. Is used to generate a braking force.
  • the caliper body 11 includes a coupling member 16 (coupling portion) and a pair of brake levers 12 and 12.
  • the coupling member 16 is installed so as to be swingable via a swing pin 16a with respect to a bracket 100a fixed to the vehicle main body 100 (the bottom surface of the carriage or the like).
  • the swing pin 16a extends substantially parallel to the traveling direction of the vehicle.
  • a pair of brake levers 12 and 12 are installed so as to be swingable with respect to the coupling member 16 via a pair of fulcrum pins 12a.
  • the fulcrum pin 12a is installed so as to extend in a direction perpendicular to the axial direction of the swing pin 16a.
  • maintains the brake pad 13 is attached to the brake lever 12 through the support pin 15a extended in parallel with the fulcrum pin 12a on one end side on both sides of the fulcrum pin 12a.
  • a brake pad 13 is attached to the back plate 15 by an attachment member (not shown) so as to face the braking surface 14 a of the wheel 14.
  • the cylinder device 2 is attached to the other end side of the brake lever 12 (the side opposite to the brake pad 13) via a cylinder support pin 12b.
  • the cylinder device 2 is installed between a pair of brake levers 12 and 12, and a cylinder body 20 is attached to one brake lever 12.
  • a block 33 whose center is fixed to the rod 30 (see FIG. 3) are rotatably attached to the other brake lever 12 via a cylinder support pin 12b.
  • the rod 30 is a rod-like member extending in parallel with the advancing / retreating direction, and is held by a rod-side receiving member 70 described later.
  • the cylinder device 2 can cause the rod 30 to project or retract from the cylinder body 20, and the vicinity of the ends of the pair of brake levers 12 and 12 (near the cylinder support pins 12 b) can be separated from each other. , Can be driven close to each other. As a result, the pair of brake levers 12 and 12 can be operated with the fulcrum pin 12 a as a support shaft, and the wheel 14 can be sandwiched between the brake pads 13.
  • FIG. 3 is a sectional view taken along line S1-S1 of the cylinder device 2 shown in FIG. However, a part of the cylinder body 20 and the piston 40 has a cross section including the guide shaft 24.
  • the advancing direction of the rod 30 is indicated by an arrow X1
  • the retracting direction of the rod 30 is indicated by an arrow X2.
  • the advancing direction of the rod 30 is referred to as “advancing direction X1”
  • the retracting direction of the rod 30 is referred to as “retracting direction X2”.
  • the cylinder device 2 includes a cylinder body 20 that forms an internal space.
  • the cylinder body 20 includes a first casing portion 21 and a second casing portion 22.
  • the first casing portion 21 has a bottomed substantially cup shape.
  • the second casing part 22 is fixed with bolts or the like so as to close the open side of the first casing part 21.
  • An insertion hole 22 a for inserting the rod 30 is formed in the second casing portion 22.
  • the cylindrical part 23 extended in the 1st casing part 21 side coaxially with the said insertion hole 22a is formed.
  • a step portion 23 a is formed on the inner peripheral surface of the cylindrical portion 23.
  • the stepped portion 23a is formed such that the inner diameter of the cylindrical portion 23 is larger on the proximal end side (end portion side in the retracting direction) of the rod 30 than on the distal end side (end portion side in the advance direction) of the rod 30. ing. Moreover, the outer peripheral surface of the cylindrical part 23 is extended with the same diameter in parallel with the advancing / retreating direction.
  • FIG. 4 is a perspective view showing the piston 40 shown in FIG. 5 is a view of the piston 40 shown in FIG. 4 as viewed from the inclined surface 42a side in a direction parallel to the central axis C of the rod 30.
  • FIG. 6 is a cross-sectional view of the piston shown in FIG. 5 taken along the line S2-S2.
  • a piston 40 is provided around the cylindrical portion 23 inside the cylinder body 20.
  • the piston 40 includes a disc-shaped portion 41 having a through hole 41a formed at the center, and a pair of discs extending from the disc-shaped portion 41 in parallel with the central axis C direction of the rod 30. And a plate-like portion 42.
  • the piston 40 is disposed between the outer peripheral surface of the cylindrical portion 23 and the inner peripheral surface of the second casing portion 22 by inserting the cylindrical portion 23 through the through hole 41a. That is, the piston 40 is arranged so as to divide the space between the outer peripheral surface of the cylindrical portion 23 and the inner peripheral surface of the second casing portion 22 into two.
  • the piston 40 is airtightly fitted to the outer peripheral surface of the cylindrical portion 23, is airtightly fitted to the inner peripheral surface of the second casing portion 22, and is slidable in parallel with the forward / backward direction of the rod 30. .
  • the central axis of the piston 40 (the outer periphery of the piston and the central axis of the through hole 41a) is positioned in the same straight line as the central axis C of the rod 30.
  • the space on the tip side of the rod 30 partitioned by the piston 40 is a pressure chamber 43, and a compressed air supply / exhaust port (not shown) communicates with the pressure chamber 43.
  • the cylinder body 20 is provided with a pair of guide shafts 24 (see FIG. 14) for guiding the piston 40 in parallel with the advancing / retreating direction of the rod 30.
  • a guide hole 41 b through which the guide shaft 24 passes is formed in the disc-shaped portion 41 of the piston 40.
  • the piston 40 is in contact with the portion that contacts the outer peripheral surface of the cylindrical portion 23 and the inner peripheral surface of the second casing portion 22.
  • Packing 44, 45, 46 is attached to the portion and the portion that contacts the guide shaft 24.
  • a spring 25 is disposed around the guide shaft 24.
  • the spring 25 is disposed between the piston 40 and the first casing portion 21 and urges the piston 40 toward the advance direction X1.
  • the plate-like portion 42 of the piston 40 has an inclined surface 42 a that is inclined in the direction around the central axis C of the rod 30.
  • the angle P1-C-P2 ( ⁇ Is an angle of about 54 °.
  • the pair of inclined surfaces 42 a are provided at positions shifted from each other by 180 ° in the direction around the central axis C of the rod 30.
  • the roller 63 of the rotation member 60 mentioned later is provided so that it may contact
  • FIG. 7 is a view of the main body side receiving member 50 shown in FIG. 3 as viewed from the rotating member 60 side in a direction parallel to the central axis C of the rod 30.
  • FIG. 8 is a cross-sectional view of the main body side receiving member 50 shown in FIG. 7 taken along line S3-S3.
  • 9 is a cross-sectional view of the main body side receiving member 50 shown in FIG. 7 cut along the center line in the width direction of the groove 53 (that is, the circle ⁇ shown in FIG. 7).
  • a main body side receiving member 50 is fixed to the bottom surface of the first casing portion 21 with a bolt.
  • the main body side receiving member 50 includes a flange portion 51 in which a through hole 51 a is formed in the center portion, and a surface that contacts the bottom surface of the first casing portion 21 in the flange portion 51.
  • four column portions 52 protruding from the opposite surface.
  • the four column parts 52 are arranged close to the opening edge part of the through hole 51a, and are arranged so that the intervals between the adjacent column parts 52 are equal in the circumferential direction.
  • the column part 52 has an inner circular arc surface 52a formed by extending the inner peripheral surface of the through hole 51a and a radially outer side formed so as to have the same central axis as the through hole 51a.
  • the outer arc surface 52b faces and the planar side surface 52c that connects both ends of the inner arc surface 52a and the outer arc surface 52b in the circumferential direction and extends in parallel with the advancing and retreating direction of the rod 30 is provided.
  • a plurality of grooves 53 arranged in the circumferential direction are formed in the vicinity of the outer periphery of the surface on which the pillar portion 52 of the flange portion 51 is provided.
  • ten grooves 53 are formed in the flange portion 51 side by side in the circumferential direction.
  • the groove 53 is formed so that the width becomes narrower and the depth becomes shallower in the counterclockwise direction when viewed from the side of the surface on which the groove 53 is formed (that is, the rotating member 60 side).
  • the inner surface of the groove 53 has a shape that allows the steel ball 54 to roll in the circumferential direction while being in surface contact.
  • steel balls 54 are arranged in the plurality of grooves 53, respectively.
  • the radius of the steel ball 54 is larger than the depth at the deepest position of the groove 53.
  • the plurality of grooves 53 when viewed from a direction parallel to the central axis C of the rod 30, the plurality of grooves 53 have an angle ⁇ ⁇ b> 1 (the deepest portion of one groove 53 is A ⁇ b> 1, and adjacent grooves 53 in the circumferential direction. Are arranged in the circumferential direction at intervals such that the angle A1-O-A2) is about 36 degrees, where A2 is the deepest portion of the flange portion 51 and O is the central axis of the flange portion 51.
  • the central axis O of the flange portion 51 is arranged in the same straight line as the central axis C of the rod 30.
  • the plurality of grooves 53 are arranged with no gap therebetween.
  • the center position of the steel ball 54 when the steel ball 54 disposed in the groove 53 is located at the deepest portion is B1 (in this embodiment).
  • the center position of the steel ball 54 when the steel ball 54 is located at the tip of the groove 53 is B2, the angle of the angle B1-O-B2 (angle ⁇ 2 in FIG. 7) ) Is about 22.5 degrees.
  • “when the steel ball 54 is located at the tip of the groove 53” means that the steel ball 54 is in contact with the tip P3 of the linear slope in the groove 53 in the cross section shown in FIG. The time when the tangent of the steel ball 54 coincides with the inclined surface 53 a of the groove 53.
  • FIG. 10 is a view of the rotating member 60 shown in FIG. 3 as viewed from the main body side receiving member 50 side in a direction parallel to the central axis C of the rod 30.
  • FIG. 11 is a sectional view taken along the line S4-S4 of the rotating member 60 shown in FIG.
  • the steel balls 54 are respectively disposed in the plurality of grooves 53 formed in the main body side receiving member 50.
  • the rotation member 60 is installed so that the said steel ball 54 may be pinched
  • the rotating member 60 includes a disc-shaped main body 61 having a through hole 61 a formed in the center, a shaft 62 protruding from the outer peripheral surface of the main body 61, and the shaft 62. And a roller 63 provided to be rotatable around. A pair of the shaft 62 and the roller 63 is provided at a 180-degree symmetrical position on the outer periphery of the main body 61.
  • the rotary member 60 has a groove 64 having the same shape as the groove 53 formed in the main body side receiving member 50 on the surface facing the main body side receiving member 50.
  • the groove 64 has a narrow width and a shallow depth in the counterclockwise direction when viewed from the side of the surface on which the groove 64 is formed (that is, the main body side receiving member 50 side). It is formed to become. Further, as shown in FIG. 10, when the plurality of grooves 64 are viewed from a direction parallel to the central axis C of the rod 30, the angle ⁇ ⁇ b> 1 ′ (the deepest portion of one groove 64 is A ⁇ b> 1 ′ in the circumferential direction).
  • the adjacent grooves 64 are arranged in the circumferential direction at intervals such that the deepest portion of the adjacent groove 64 is A2 ′ and the angle A1′-O′-A2 ′ when the central axis of the main body 61 is O ′ is approximately 36 degrees. It is out.
  • the central axis O ′ of the rotating member 60 is arranged in the same straight line as the central axis C of the rod 30.
  • the plurality of grooves 64 are arranged with no gap therebetween.
  • B1 ′ this embodiment.
  • the center position of the steel ball 54 when the steel ball 54 is located at the tip of the groove 64 is B2 ', the angle B1'-O'-B2' (An angle ⁇ 2 ′ in FIG. 10) is about 22.5 degrees.
  • the rotating member 60 is formed so as to be symmetrical with respect to a plane perpendicular to the central axis O ′ of the main body 61. That is, the rotation member 60 is formed on the surface opposite to the surface facing the main body side receiving member 50 side (that is, the surface facing the rod side receiving member 70 side) on the surface facing the main body side receiving member 50 side.
  • a plurality of grooves 65 having a shape corresponding to the plurality of grooves 64 (grooves whose width decreases in the clockwise direction and whose depth decreases) are formed.
  • (Rod side receiving member) 12 is a view of the rod-side receiving member 70 shown in FIG. 3 as viewed from the rotating member 60 side in a direction parallel to the central axis C of the rod 30.
  • FIG. 13 is a cross-sectional view taken along line S5-S5 of the rod side receiving member 70 shown in FIG.
  • steel balls 55 are respectively disposed in a plurality of grooves formed on the surface of the rotating member 60 facing the side opposite to the main body side receiving member 50 side.
  • the size of the steel ball 55 is the same as that of the steel ball 54 provided between the main body side receiving member 50 and the rotating member 60.
  • the rod-side receiving member 70 includes a cylindrical portion 71, a flange portion 72 provided at an axial end portion (base end) of the cylindrical portion 71, and a flange portion 72.
  • a cylindrical portion 71 is provided with a cross-shaped portion 73 protruding from a surface opposite to the cylindrical portion 71.
  • the rod 30 is arrange
  • the rod 30 is moved relative to the rod side receiving member 70 in a direction parallel to the central axis C of the rod 30 (advancing and retracting direction) by the regulating members 81 and 82 arranged at the tip of the cylindrical portion 71. It is comprised so that it may restrain.
  • a through hole 71b that penetrates in the radial direction is formed in the intermediate portion in the axial direction of the cylindrical portion 71, and protrudes in the radial direction from the outer periphery of the rod 30 to the through hole 71b as shown in FIG.
  • the flange portion 72 is a portion formed so that the outer diameter is larger than the outer diameter of the cylindrical portion 71.
  • a groove 74 having the same shape as the groove 65 provided on the surface of the rotating member 60 facing the flange portion 72 is formed on the surface of the flange portion 72 facing the rotating member 60 side. That is, the groove 74 formed in the flange portion 72 becomes narrower in the clockwise direction when viewed from the side of the surface on which the groove 74 is formed (that is, the rotating member 60 side). The depth is shallow. Further, as shown in FIG.
  • the plurality of grooves 74 have an angle ⁇ 1 ′′ (the deepest portion of one groove 74 is A1 ′′ and adjacent in the circumferential direction when viewed from a direction parallel to the central axis of the rod 30.
  • the grooves 74 are arranged in the circumferential direction at intervals such that the angle A1 ′′ -O ′′ -A2 ′′) is about 36 degrees when the deepest portion of the groove 74 is A2 ′′ and the central axis of the rod side receiving member 70 is O ′′.
  • the central axis O ′′ of the rod-side receiving member 70 is arranged in the same straight line as the central axis C of the rod 30.
  • the plurality of grooves 74 are arranged without gaps.
  • the center position of the steel ball 55 when the steel ball 55 disposed in the groove 74 is located at the deepest portion is B1 ′′ (this embodiment)
  • the center position of the steel ball 55 when the steel ball 55 is located at the tip of the groove 74 is B2 ′′
  • the angle (angle ⁇ 2 ′′ in FIG. 12) is about 22.5 degrees.
  • the cross-shaped portion 73 is a portion formed to have a cross shape when viewed from a direction parallel to the central axis C of the rod 30.
  • the end surface 73 a of the cross-shaped portion 73 projecting radially outward is an arc surface having the central axis O ′′ of the main body 61 as the central axis, and the diameter thereof is the column portion 52 of the main body side receiving member 50. Is equal to the diameter of the outer arc surface 52b.
  • the cross-shaped portion 73 is slidably fitted between the four column portions 52 of the main body side receiving member 50 in parallel with the advancing / retreating direction of the rod 30.
  • the rod side receiving member 70 can move relative to the main body side receiving member 50 (that is, the cylinder main body 20) in parallel with the advancing and retreating direction of the rod 30, but the rod 30 receiving member 50 can move relative to the main body side receiving member 50.
  • the rotation around the axis is restricted by the cross-shaped portion 73 coming into contact with the column portion 52 of the main body side receiving member 50.
  • the cross-shaped portion 73 of the rod side receiving member 70 and the column portion 52 of the main body side receiving member 50 are inserted into the through hole 61a of the rotating member 60, and in the through hole 61a, The cross-shaped portion 73 and the column portion 52 are engaged as described above.
  • the rotating member 60 disposed around the cross-shaped portion 73 and the column portion 52 can rotate around the central axis C of the rod 30 with respect to the rod-side receiving member 70 and the main body-side receiving member 50.
  • the rod-side receiving member 70 is disposed so that the cylindrical portion 71 is slidable in the insertion hole 22 a (inside the cylindrical portion 23) of the second casing portion 22. Further, as shown in FIG. 3, a concave portion 72 a formed on the surface of the flange portion 72 of the rod side receiving member 70 on the cylindrical portion 71 side and a step portion formed on the inner surface of the cylindrical portion 23 of the second casing portion 22.
  • the spring 26 is disposed between the terminal 23a and the terminal 23a. The spring 26 biases the flange portion 72 of the rod side receiving member 70 in the retracting direction of the rod 30.
  • FIG. 14 is a perspective partial cross-sectional view schematically showing the inside of the cylinder device 2 shown in FIG.
  • FIG. 14A shows a state where the rod 30 is retracted into the cylinder body 20 (return position).
  • the steel ball 54 moves from the deepest part of the groove 64 to a shallower position.
  • the steel ball 54 moves along the slope in the groove 53 from the deepest part of the groove 53 of the main body side receiving member 50 toward a shallower position. Therefore, the steel ball 54 moves in the advance direction X1 relative to the main body side receiving member 50, and the rotation member 60 moves in the advance direction X1 relative to the steel ball 54. Therefore, the rotation member 60 is relatively moved with respect to the cylinder body 20 in the advancing direction X1 of the steel ball 54 with respect to the body-side receiving member 50 and the rotation with respect to the steel ball 54.
  • the member moves in the advance direction X1 by an amount corresponding to the sum of the amount of movement in the advance direction X1.
  • the relative positional relationship between the rotating member 60 and the rod-side receiving member 70 in the forward / backward direction of the rod 30 similarly changes between the rotating member 60 and the rod-side receiving member 70. That is, the rod-side receiving member 70 does not rotate around the axis of the rod 30 with respect to the main body-side receiving member 50 and can move in the advancing and retreating direction of the rod 30 with respect to the main body-side receiving member 50. Therefore, when the rotation member 60 rotates around the axis of the rod 30, it moves as follows. That is, the steel ball 55 between the rotating member 60 and the rod side receiving member 70 moves relative to the rotating member 60 in the advancing direction X1, and the rod side receiving member The member 70 moves relatively in the advance direction X1.
  • the rod-side receiving member 70 is relatively moved with respect to the rotating member 60, and the amount of movement of the steel ball 55 in the advance direction X ⁇ b> 1 with respect to the rotating member 60 and the rod side with respect to the steel ball 55.
  • the receiving member 70 moves in the advance direction X1 by an amount corresponding to the sum of the amount of movement in the advance direction X1.
  • the rod 30 fixed to the rod side receiving member 70 moves the moving member 60 in the advancing direction X1 with respect to the main body side receiving member 50 and the rod side receiving member 70 with respect to the rotating member 60. It moves in the advance direction X1 so as to protrude from the cylinder body 20 by an amount corresponding to the sum of the amount of movement in the advance direction X1.
  • the stroke with respect to the cylinder main body 20 in the retracting direction X2 of the piston 40 is 1, the stroke with respect to the cylinder main body 20 in the advancing direction X1 of the rod 30 is configured to be 0.5 or less.
  • the urging force of the piston 40 can be increased to twice or more and transmitted to the rod.
  • the rod 30 is further moved in the advancing direction X1.
  • the steel balls 54 and 55 are grooves of the main body side receiving member 50, the rotating member 60, and the rod side receiving member 70. (I.e., the center position of the steel ball is B1 in FIG. 9).
  • the steel balls 54 and 55 are the main body side receiving member 50, the rotation member 60, and the rod side. It is comprised so that it may go up the slope of the groove
  • the piston 40 When the compressed air is discharged from the pressure chamber 43, the piston 40 is moved in the advancing direction X1 by the urging force of the spring 25.
  • the steel balls 54 and 55 are formed in the grooves of the rod side receiving member 70, the rotating member 60, and the main body side receiving member 50. Roll down the slope of the groove toward the deepest part of the river.
  • the rod side receiving member 70 and the rotating member 60 move relative to the cylinder body 20 in the retracting direction X2.
  • the rotating member 60 moves in the retracting direction X2 while rotating clockwise as viewed from the front end side of the rod 30 in the advancing direction.
  • the rod 30 moves relative to the cylinder body 20 in the retreat direction X2.
  • the cylinder device 2 includes the cylinder body 20 that is hollow inside, and the rod 30 that is disposed in the cylinder body 20 so as to be movable back and forth in the axial direction with respect to the cylinder body 20.
  • the piston 40 is provided so as to surround the axis of the rod 30, and is movable in parallel with the forward / backward direction of the rod 30 and moves in the retracting direction of the rod 30 by air pressure, and the piston 40
  • a force-increasing mechanism (the inclined surface 42a of the piston 40, the main body side) increases the force generated in the piston 40 and acts on the rod 30 so that the rod 30 moves in the advancing direction.
  • Receiving member 50, rotating member 60, rod side receiving member 70, and force-increasing mechanism including steel balls 54 and 55.
  • the piston 40 since the piston 40 is provided so as to surround the axis of the rod 30, the range occupied by the piston 40 and the rod 30 in the direction parallel to the central axis C of the rod 30 can be reduced. it can. Therefore, by arranging the force-increasing mechanism in a space that can be secured by arranging the piston 40 and the rod 30 as described above, the cylinder device 2 can be applied to the outside without increasing the size of the cylinder device 2. The power can be increased. For example, when generating a double braking force, the conventional configuration (a configuration in which the braking force is increased by increasing the cylinder diameter) requires the cylinder diameter to be doubled by ⁇ 2, but a double boosting mechanism is installed in the cylinder.
  • the cylinder diameter has only to be increased by an amount corresponding to the boosting mechanism, so that an excessive increase in size can be prevented.
  • the outer periphery of a cylinder body having a conventional structure that exhibits a brake output equivalent to that of the present embodiment is indicated by a two-dotted line.
  • the pressure chamber 43 can be disposed on the distal end side (near the end of the advance direction X1) of the rod 30 in the cylinder body 20. Thereby, the space on the proximal end side of the rod 30 in the cylinder body 20 (near the end in the retracting direction X2) can be used effectively.
  • the force increasing mechanism of the cylinder device 2 includes an inclined surface 42a provided in the piston 40, which is inclined with respect to the advancing / retreating direction, and is biased by the inclined surface 42a when the piston 40 moves in the retracting direction X2, And a rotation member 60 that rotates in one direction around the axis of the rod 30.
  • the rod 30 is provided so as not to rotate about the axis of the rod 30 with respect to the cylinder body 20, and moves in the advancing direction X1 as the rotating member 60 rotates in the one direction. .
  • the force generated by the piston 40 in the retreat direction X2 can be efficiently converted into the force generated by the rod 30 in the advance direction X1.
  • the cylinder device 2 includes a rod side receiving member 70 (first receiving member) fixed to the rod 30.
  • the rotating member 60 is provided so as to face the rod-side receiving member 70 in a direction parallel to the central axis C of the rod 30, and the rotating member 60 is provided on a surface facing the rod-side receiving member 70.
  • a groove 65 (inclined groove) that is inclined in the direction of rotation 60 is formed.
  • the groove 65 is provided with a steel ball 55 (rolling member) that can roll along the inner surface of the groove 65.
  • the steel ball 55 (rolling member) is supported in a state of being sandwiched between the rod side receiving member 70 and the rotating member 60.
  • the force generated by the piston 40 in the retracting direction X2 is increased in two steps by using the inclined surface 42a of the piston 40 and the groove 65 of the rotating member 60, and the rod 30 is generated in the advance direction X1. It can be converted into force. Further, in order to increase the force, the groove 65 that is inclined in the rotation direction of the rotation member 60 is used, and an excessively large space is not used. Therefore, it is possible to increase the degree of freedom of arrangement of other mechanisms in the cylinder device 2 while exhibiting a larger boosting function.
  • a plurality of grooves 65 and steel balls 55 are provided so as to be positioned on a single circle centered on the axis of the rod 30.
  • a plurality of grooves 64 and steel balls 54 are also provided so as to be positioned on one circle centered on the axis of the rod 30.
  • the force acting on one steel ball 55 can be reduced. That is, it is not necessary to excessively increase the contact area between the groove 65 of the rotating member 60 and the groove 74 of the rod side receiving member 70 in one steel ball 55 in order to suppress the surface pressure. Therefore, the steel ball 55 and the groove 65 can be reduced.
  • the steel balls 54 and the grooves 64 can be made small. As a result, the cylinder device 2 can be reduced in size.
  • a spherical steel ball 55 is used as a rolling member that can roll along the inner surfaces of the groove 65 and the groove 74.
  • a spherical steel ball 54 is used as a rolling member that can roll along the inner surfaces of the groove 64 and the groove 53.
  • the configuration using the spherical rolling member can be configured relatively inexpensively.
  • the cylinder device 2 faces the cylinder body 20 so as to face the surface of the rotating member 60 opposite to the surface facing the rod-side receiving member 70 in a direction parallel to the axial direction of the rod 30.
  • a fixed body-side receiving member 50 (second receiving member) is provided.
  • a groove 64 (second inclined groove) that is inclined in the rotation direction of the rotation member 60 is formed on the surface of the rotation member 60 that faces the body-side receiving member 50.
  • the groove 64 is provided with a steel ball 54 (second rolling member) that can roll along the inner surface of the groove 64. The steel ball 54 is supported while being sandwiched between the main body side receiving member 50 and the rotating member 60.
  • the stroke of the rod 30 can be increased without excessively increasing the size of the cylinder device 2.
  • the cylinder device 2 may be modified as shown in FIG. That is, it is possible to adopt a configuration in which the steel balls 54 and 55 are not used.
  • FIG. 15 the same members as those in FIG. In the configuration shown in FIG. 15, a thread is formed on the inner peripheral surface of the through hole 61 a ′ of the rotating member 60 ′.
  • a thread that can be screwed into the thread of the rotating member 60 ′ is formed on the outer peripheral surface of the cross-shaped portion 73 ′ of the rod-side receiving member 70 ′.
  • the said rotation member 60 ' is screwed in the screw thread formed in the outer peripheral surface of the cross-shaped part 73' in the rod side receiving member 70 ', and rotation member 60' rotates in one direction.
  • the rod-side receiving member 70 ′ moves in the advancing direction X1.
  • the column portion 52 ′ of the main body side receiving member 50 is provided at a position close to the central axis C of the rod so that the surface facing the radially outer side does not contact the thread of the rotating member 60 ′.
  • the column portion 52 ′ restricts the rotation of the rod-side receiving member 70 around the axis of the rod 30 and allows the rod-side receiving member 70 ′ to move in the advancing and retracting direction. 70 'is engaged.
  • the piston 40 is moved in the retracting direction X2 of the rod 30 by using the inclined surface 42a of the piston 40 and the screw shape of the rotating member 60 ′ (and the screw shape of the corresponding rod side receiving member 70 ′).
  • the force to be generated can be increased in two stages and converted into a force that the rod 30 generates in the advance direction X1.
  • the screw shapes of the rotating member 60 ′ and the rod side receiving member 70 ′ are used, and an excessively large space is not used. Therefore, it is possible to increase the degree of freedom of arrangement of other mechanisms in the cylinder device 2 ′ while exhibiting a larger boosting function.
  • bonded rotating member 60 'and rod side receiving member 70' using the ball screw may be sufficient.
  • the disc brake device 1 for railway vehicles uses a cylinder device 2.
  • a brake pad 13 is provided at one end, and a pair of brake levers 12 and 12 that are rotatable around a fulcrum pin 12a are provided.
  • a block 33 fixed to the tip of the rod 30 is attached to the other end (the end opposite to the brake pad 13) of one brake lever 12, and the first of the cylinder body 20 is connected to the other end of the other brake lever 12.
  • a casing portion 21 is attached.
  • the braking force of the railway vehicle disc brake device 1 can be increased, and the railway vehicle disc brake device 1 can be formed in a small size.
  • a gap adjusting mechanism 90 can be provided between the cylindrical portion 23 ′ in the cylinder body 20 ′′ and the cylindrical portion 71 ′ of the rod side receiving member 70 ′′.
  • FIG. 16 shows an enlarged view of the vicinity of the cylindrical portion 23 ′ and the cylindrical portion 71 ′ provided with the gap adjusting mechanism 90.
  • the inner peripheral surface of the cylindrical portion 23 ′ of the cylinder body is formed so as to have a predetermined gap between it and the outer peripheral surface of the cylindrical portion 71 ′.
  • a concave portion 23b continuous in the circumferential direction is formed on the rod tip side on the inner circumferential surface of the cylindrical portion 23 ′.
  • an uneven surface 75 is formed on the outer peripheral surface of the cylindrical portion 71 ′ of the rod-side receiving member 70 ′′.
  • the gap adjusting mechanism 90 includes a guide member 91 disposed between the cylindrical portion 23 ′ and the cylindrical portion 71 ′ in addition to the configuration of the cylindrical portion 23 ′ and the cylindrical portion 71 ′. Yes.
  • the guide member 91 has a substantially cylindrical shape, and a cylindrical portion 71 ′ is inserted through the shaft hole. Protrusions 91 a and 91 b projecting from the inner peripheral surface are formed at both axial ends of the guide member 91.
  • the guide member 91 has a protrusion 91c that protrudes from the outer peripheral surface. Then, O-rings 92 and ring-shaped backup rings 93 are alternately arranged between the protrusions 91a and 91b in the axial direction.
  • each O-ring 92 is elastically deformed so as to be crushed in the axial direction, and its inner peripheral side expands to engage with the concave portion of the concave and convex surface 75.
  • the guide member 91 and the cylindrical portion 71 ′ are coupled, and the guide member 91 moves integrally with the cylindrical portion 71 ′ (that is, the rod side receiving member 70 ′′).
  • the return amount of the rod side receiving member 70 ′′ is reduced by the amount of the deviation. That is, the protrusion 91c protruding from the outer peripheral surface of the guide member 91 is the rod proximal end surface of the recess 23b. The amount of return of the guide member 91 and the rod-side receiving member 70 ′′ decreases due to contact with 23d. Thereby, from the next time, the brake can be operated with the stroke of the normal rod side receiving member 70 ′′.
  • the gap adjusting mechanism 90 is not limited to the one having the above configuration, and is not limited to the one arranged at the above position, and may be changed as appropriate.
  • the present invention can be used for a railway vehicle disk brake device that applies a braking force by sandwiching wheels.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Braking Arrangements (AREA)

Abstract

La présente invention aborde le problème consistant à réaliser un petit dispositif à cylindre capable d'accroître la force de sollicitation d'une tige et à réaliser un dispositif de frein à disque pour véhicule ferroviaire utilisant le dispositif à cylindre. Un dispositif à cylindre (2) comprend : un corps principal de cylindre (20) ; une tige (30) ; un piston (40) placé dans le corps principal de cylindre (20) de manière à entourer l'axe de la tige (30), le piston étant autorisé à se déplacer parallèlement à la direction d'avance/retrait de la tige (30), et étant mis en mouvement par une pression d'air dans le sens du retrait de la tige (30) ; et un mécanisme d'accroissement de la force, servant à accroître la force engendrée dans le piston (40) et agissant sur la tige (30) de telle sorte que la tige (30) se déplace dans la direction d'avance lorsque le piston (40) se déplace dans le sens du retrait de la tige (30) (le mécanisme d'accroissement de la force comprenant une surface inclinée (42a) du piston (40), un élément récepteur (50) situé sur le côté corps principal ; un élément rotatif (60), un élément récepteur côté tige (70) et des billes en acier (54, 55)).
PCT/JP2010/067968 2010-10-13 2010-10-13 Dispositif à cylindre et dispositif de frein à disque pour véhicule ferroviaire WO2012049745A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/067968 WO2012049745A1 (fr) 2010-10-13 2010-10-13 Dispositif à cylindre et dispositif de frein à disque pour véhicule ferroviaire

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/067968 WO2012049745A1 (fr) 2010-10-13 2010-10-13 Dispositif à cylindre et dispositif de frein à disque pour véhicule ferroviaire

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WO2012049745A1 true WO2012049745A1 (fr) 2012-04-19

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015007447A (ja) * 2013-06-25 2015-01-15 本田技研工業株式会社 ブレーキキャリパ及びそれを備える鞍乗型車両
CN113715864A (zh) * 2020-05-26 2021-11-30 纳博特斯克有限公司 制动装置

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61175330A (ja) * 1985-01-25 1986-08-07 クノル‐ブレムゼ・アクチエンゲゼルシヤフト レール車両用デイスクブレーキのためのブレーキリンク機構
JPH11173307A (ja) * 1997-12-09 1999-06-29 Ihara Science Corp 小型アクチュエータ用倍力機構
JP2002160135A (ja) * 2000-09-12 2002-06-04 Kosmek Ltd クランプ装置
JP2004270716A (ja) * 2003-03-05 2004-09-30 Ckd Corp 流体制御弁
JP2007131203A (ja) * 2005-11-11 2007-05-31 Nabtesco Corp ブレーキシリンダの隙間調整装置及びそれを備えたブレーキシリンダ
JP2009180269A (ja) * 2008-01-30 2009-08-13 Kayaba Ind Co Ltd ブレーキ装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61175330A (ja) * 1985-01-25 1986-08-07 クノル‐ブレムゼ・アクチエンゲゼルシヤフト レール車両用デイスクブレーキのためのブレーキリンク機構
JPH11173307A (ja) * 1997-12-09 1999-06-29 Ihara Science Corp 小型アクチュエータ用倍力機構
JP2002160135A (ja) * 2000-09-12 2002-06-04 Kosmek Ltd クランプ装置
JP2004270716A (ja) * 2003-03-05 2004-09-30 Ckd Corp 流体制御弁
JP2007131203A (ja) * 2005-11-11 2007-05-31 Nabtesco Corp ブレーキシリンダの隙間調整装置及びそれを備えたブレーキシリンダ
JP2009180269A (ja) * 2008-01-30 2009-08-13 Kayaba Ind Co Ltd ブレーキ装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015007447A (ja) * 2013-06-25 2015-01-15 本田技研工業株式会社 ブレーキキャリパ及びそれを備える鞍乗型車両
CN113715864A (zh) * 2020-05-26 2021-11-30 纳博特斯克有限公司 制动装置

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