WO2015019747A1 - Dispositif de frein à friction - Google Patents

Dispositif de frein à friction Download PDF

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Publication number
WO2015019747A1
WO2015019747A1 PCT/JP2014/067392 JP2014067392W WO2015019747A1 WO 2015019747 A1 WO2015019747 A1 WO 2015019747A1 JP 2014067392 W JP2014067392 W JP 2014067392W WO 2015019747 A1 WO2015019747 A1 WO 2015019747A1
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WO
WIPO (PCT)
Prior art keywords
friction
pressing
members
rotational
rotation axis
Prior art date
Application number
PCT/JP2014/067392
Other languages
English (en)
Japanese (ja)
Inventor
磯野　宏
Original Assignee
トヨタ自動車株式会社
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 トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
Priority to JP2015530752A priority Critical patent/JP6160696B2/ja
Publication of WO2015019747A1 publication Critical patent/WO2015019747A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • 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
    • F16D55/04—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 moving discs or pads away from one another against radial walls of drums or cylinders
    • F16D55/14—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 moving discs or pads away from one another against radial walls of drums or cylinders with self-tightening action, e.g. by means of coacting helical surfaces or balls and inclined surfaces
    • 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
    • F16D51/00—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like
    • 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
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/22—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for pressing members apart, e.g. for drum 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/20—Electric or magnetic using electromagnets
    • 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
    • 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
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement
    • F16D2125/50—Rotating members in mutual engagement with parallel non-stationary axes, e.g. planetary gearing
    • 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
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/08—Self-amplifying or de-amplifying mechanisms

Definitions

  • the present invention relates to a friction brake device, and more particularly to a friction brake device that generates a frictional force by pressing a friction member against a brake rotor.
  • Patent Document 1 describes a friction brake device having a self-boosting mechanism that generates a wedge action.
  • the braking force generated by the brake device without increasing the pressing force of the pressing device that presses the friction member, compared to a brake device that does not increase the pressing force due to the wedge action. Can be high.
  • the conventional friction brake device that generates the wedge action has room for improvement in sufficiently increasing the braking force.
  • the present invention has been made in view of the above-described problems in a conventional friction brake device that generates a wedge action.
  • the main problem of the present invention is that the friction member is caused to perform a motion other than relative rotation around the rotation axis with respect to the brake rotor, and the friction member is sufficiently pressed by the pressing force increased by the wedge action. It is to generate a high frictional force.
  • a brake rotor having a friction surface extending perpendicularly to a rotation axis and rotating around the rotation axis, a rotary friction member rotatable around a rotation axis parallel to the rotation axis, and a press And a pressing device that presses the rotating friction member against the friction surface by pressing the member against the rotating friction member.
  • the brake rotor, the rotating friction member, and the pressing member use the rotating friction member as a planetary gear.
  • a pressing force intensifying mechanism is provided between the supported non-rotating member, and the pressing force intensifying mechanism generates a relative rotational torque around the rotation axis between the pressing member and the non-rotating member.
  • the brake rotor, the rotating friction member, and the pressing member constitute a planetary gear mechanism using the rotating friction member as a planetary gear
  • the rotating friction member rotates while rotating around a rotation axis parallel to the rotation axis. Revolve around. Therefore, the rotating friction member frictionally engages the friction surface and the pressing member to generate a frictional force due to both revolution and rotation.
  • the pressing force between the rotating friction member, the friction surface, and the pressing member is a pressing force increased by a pressing force increasing mechanism.
  • the braking force can be sufficiently increased as compared with the conventional wedge-acting friction brake device in which the friction member does not move other than relative rotation around the rotation axis with respect to the brake rotor. .
  • the friction surface includes first and second friction surfaces spaced apart from each other along the rotation axis
  • the rotation friction member includes the first and second friction surfaces, respectively.
  • First and second rotating friction members supported to be frictionally engageable with the friction surface, and the pressing member presses the first and second rotating friction members against the first and second friction surfaces, respectively.
  • 1st and 2nd press member Comprising: The 1st and 2nd press member supported so that a displacement along a rotating shaft is included, and one of the 1st and 2nd press members respond
  • the brake rotor, the first and second rotating friction members, and the first and second pressing members are respectively First and second planetary gears using planetary gears as the first and second rotating friction members
  • the first and second friction surfaces are opposed to each other, and at least a part of the first and second rotating friction members, the first and second pressing members, and the pressing force control mechanism are It may be configured to be disposed between the first friction surface and the second friction surface.
  • the first and second rotating friction members are pressed in the opposite directions by the first and second pressing members between the first friction surface and the second friction surface. Are pressed against the first and second friction surfaces, respectively. Since there are two types of rotary friction members, the first and the second, as compared with the case where only one type of rotary friction member exists as in the friction brake device described in Patent Document 1, for example, there is a control. Power can be increased.
  • the reaction force of the pressing by the first and second pressing members can be transmitted to the other pressing member, it is not necessary to provide another member for receiving the reaction force of the pressing. Therefore, for example, the structure of the friction brake device can be simplified as compared with a case where another member that receives the reaction force of the pressing like the friction brake device described in Patent Document 1 is required.
  • the first pressing member is supported by the stationary member so as to be rotatable around the rotation axis and displaceable along the rotation axis
  • the second pressing member is The stationary member is supported so as to be non-rotatable around the rotation axis and displaceable along the rotation axis.
  • the second pressing member and the stationary member constitute a non-rotating member
  • the pressing force control mechanism includes at least the first pressing mechanism.
  • the pressing member may be configured to control a force that presses the first rotating friction member against the first friction surface.
  • the first rotating friction member when the first rotating friction member is pressed against the first friction surface by the first pressing member, the first rotating friction member is frictionally engaged with the first friction surface.
  • the first pressing member is also frictionally engaged. Therefore, the first pressing member is rotated around the rotation axis by dragging with the friction force between the first pressing friction member and the first pressing member relative to the second pressing member. It can be rotated around the axis of rotation. Accordingly, the relative rotational torque between the first pressing member and the second pressing member which is a part of the non-rotating member is converted into a pressing force by the pressing force intensifying mechanism, thereby the first and second rotations. The pressing force with which the friction member is pressed against the first and second friction surfaces is increased.
  • the pressing force increasing mechanism transmits the rotational torque around the rotation axis between the first and second pressing members, and the first and second pressing members are The rotational torque is converted into a force in the direction of separating the first and second pressing members along the rotational axis by utilizing the wedge action generated by the relative rotational displacement around the rotational axis.
  • a force transmission mechanism for transmitting a reaction force between the first and second pressing members to each other between the first and second pressing members, and a non-rotation around the rotation axis.
  • a supported rotational torque carrying member that receives the rotational torque transmitted from one of the first and second pressing members to the other of the first and second pressing members via the other pressing member. And is configured to have a member Good.
  • the rotational torque is converted into a force in the direction of separating the first and second pressing members along the rotational axis, and the conversion is performed.
  • the pressing force can be increased by the force.
  • the force transmission mechanism includes first and second opposing surfaces that are provided on the first and second pressing members, respectively, and face each other in a direction along the rotation axis.
  • the first and second opposing surfaces have inclined regions that are inclined in the same direction with respect to a virtual plane perpendicular to the rotation axis, and rotational torque is generated by the cooperation of the inclined regions of the first and second opposing surfaces.
  • the rotation torque may be transmitted in the circumferential direction around the rotation axis, and the rotation torque may be converted into a force parallel to the rotation axis and separating the first and second pressing members.
  • the rotation torque can be reliably transmitted in the circumferential direction around the rotation axis by the cooperation of the inclined regions of the first and second opposing surfaces, and the rotation torque is parallel to the rotation axis.
  • the force can be reliably converted into a force in a direction in which the first and second pressing members are separated.
  • the first and second pressing members can press the first and second rotating friction members against the first and second friction surfaces, respectively, with the pressing force increased by the conversion.
  • the friction surface includes first and second friction surfaces spaced apart from each other along the rotation axis
  • the rotation friction member includes the first and second friction surfaces, respectively.
  • First and second rotating friction members supported to be frictionally engageable with the friction surface, and the pressing member presses the first and second rotating friction members against the first and second friction surfaces, respectively.
  • 1st and 2nd press member Comprising: The 1st and 2nd press member supported so that a displacement along a rotating shaft is included, and one of the 1st and 2nd press members respond
  • the brake rotor, the first and second rotating friction members, and the first and second pressing members are respectively First and second planetary gears using planetary gears as the first and second rotating friction members
  • the first and second friction surfaces face in opposite directions to each other, the first and second rotating friction members, the first and second pressing members, It may be configured to be disposed on opposite sides of the first and second friction surfaces.
  • the first and second rotating friction members are respectively pressed by the first and second pressing members in directions approaching each other on both sides of the first and second friction surfaces. And pressed against the second friction surface. Since there are two types of rotary friction members, the first and the second, as compared with the case where only one type of rotary friction member exists as in the friction brake device described in Patent Document 1, for example, there is a control. Power can be increased.
  • the pressing force can be increased by effectively using the reaction force of the pressing. .
  • the first and second pressing members are supported by the caliper so as to be rotatable around the rotation axis and displaceable along the rotation axis, and the caliper is not rotated.
  • the pressing force control mechanism may be configured to control a force with which at least the first pressing member presses the first rotating friction member against the first friction surface.
  • the first rotating friction member when the first rotating friction member is pressed against the first friction surface by the first pressing member, the first rotating friction member is frictionally engaged with the first friction surface.
  • the first pressing member is also frictionally engaged. Therefore, the first pressing member is rotated around the rotation axis by dragging with the first rotational friction member, so that the first pressing member is rotated around the rotation axis relative to the caliper. Can be rotated. Therefore, the relative rotational torque between the first pressing member and the caliper which is a non-rotating member is converted into a pressing force by the pressing force intensifying mechanism, whereby the first rotating friction member is against the first friction surface.
  • the pressing force to be pressed is increased.
  • the reaction force of the increased pressing force between the first rotating friction member, the first friction surface, and the first pressing member is transmitted to the second pressing member by the caliper, and the second pressing member is The second rotating friction member is pressed against the second friction surface with a high pressing force.
  • the second rotational friction member frictionally engages with the second friction surface and also frictionally engages with the second pressing member. Therefore, the second pressing member is rotated around the rotation axis by dragging with the second rotational friction member, and thereby the second pressing member is rotated around the rotation axis relative to the caliper. Can be rotated.
  • the relative rotational torque between the second pressing member and the caliper which is a non-rotating member is converted into a pressing force by the pressing force increasing mechanism, whereby the second rotating friction member is moved against the second friction surface.
  • the pressing force to be pressed is increased.
  • the pressing force increasing mechanism transmits the rotational torque around the rotation axis between the first pressing member and the caliper, and the first pressing member is The rotational torque is converted into a force in the direction of separating the first pressing member and the caliper along the rotational axis by utilizing the wedge action generated by the relative rotational displacement around the first rotational friction member. Transmits the rotational torque around the rotation axis between the first force transmission mechanism that transmits the reaction force that presses the first friction surface from the first pressing member to the caliper, and the second pressing member and the caliper.
  • the torque bearing member may be configured to include a rotational torque transmitted from the first pressing member to the caliper and a rotational torque bearing member that receives the rotational torque transmitted from the second pressing member to the caliper.
  • the rotational torque is converted into a force in the direction in which the first and second pressing members approach each other along the rotational axis.
  • the pressing force can be increased by the force.
  • the first force transmission mechanism includes third and fourth opposing surfaces that are provided on the first pressing member and the caliper, respectively, and face each other in the direction along the rotation axis.
  • the third and fourth opposing surfaces have inclined regions that are inclined in the same direction with respect to a virtual plane perpendicular to the rotation axis, and rotate by the cooperation of the inclined regions of the third and fourth opposing surfaces.
  • the torque may be transmitted in a circumferential direction around the rotation axis, and the rotation torque may be converted into a force in a direction parallel to the rotation axis and separating the first pressing member and the caliper.
  • the rotation torque can be reliably transmitted in the circumferential direction around the rotation axis by the cooperation of the inclined regions of the third and fourth opposing surfaces, and the rotation torque is parallel to the rotation axis.
  • the force can be reliably converted into a force in a direction to separate the first pressing member and the caliper.
  • the first pressing member can press the first rotating friction member against the first friction surface with the pressing force increased by the conversion.
  • the second force transmission mechanism includes fifth and sixth opposing surfaces that are provided on the second pressing member and the caliper, respectively, and face each other in the direction along the rotation axis.
  • the fifth and sixth opposing surfaces have inclined regions inclined in the same direction with respect to a virtual plane perpendicular to the rotation axis, and are rotated by the cooperation of the inclined regions of the fifth and sixth opposing surfaces.
  • the torque may be transmitted in a circumferential direction around the rotation axis, and the rotation torque may be converted into a force parallel to the rotation axis and separating the second pressing member and the caliper.
  • the rotation torque can be reliably transmitted in the circumferential direction around the rotation axis by the cooperation of the inclined regions of the fifth and sixth opposing surfaces, and the rotation torque is parallel to the rotation axis.
  • the force can be reliably converted into a force in the direction of separating the second pressing member and the caliper.
  • the second pressing member can press the second rotating friction member against the second friction surface with the pressing force increased by the conversion.
  • FIG. 1 is a partial sectional view showing a first embodiment of a friction brake device according to the present invention configured as an electromagnetic vehicle brake device, cut along a cut surface passing through a rotation axis. It is the partial front view which looked at 1st embodiment from the right side of FIG.
  • FIG. 3 is a partial cross-sectional view taken along line III-III in FIG. It is a fragmentary sectional view showing a force transmission mechanism about the case where the 1st and 2nd press members are displaced relatively.
  • FIG. 7 is a partial cross-sectional view taken along the line VII-VII in FIG. 6. It is a fragmentary sectional view which shows one modification of the cam surface of a force transmission mechanism. It is a fragmentary sectional view which shows another modification of the cam surface of a force transmission mechanism.
  • FIG. 1 is a partial cross-sectional view showing a first embodiment of a friction brake device according to the present invention configured as an electromagnetic vehicle brake device, cut along a cutting plane passing through a rotation axis
  • FIG. 3 is a partial sectional view taken along the line III-III in FIG. 2.
  • 1 is a cross-sectional view taken along the line II of FIG.
  • reference numeral 10 denotes an entire brake device, and the brake device 10 includes a brake rotor 12, a first pressing member 14, and a second pressing member 16.
  • the brake rotor 12 rotates around a rotation axis 18 together with a wheel rotation shaft 17 (not shown).
  • the brake rotor 12 includes a main rotor 20 that is integral with the rotary shaft 17 and a sub-rotor 22 that rotates integrally with the main rotor.
  • the main rotor 20 and the first pressing member 14 are formed of a metal material having paramagnetism
  • the second pressing member 16 and the sub-rotor 22 may be formed of a metal material having no paramagnetism.
  • the main rotor 20 has a disk portion 20A and a cylindrical portion 20B that are spaced along the rotation axis 18.
  • the disk portion 20 ⁇ / b> A is integrally connected to the rotating shaft 17 at the inner peripheral portion, and extends substantially in the shape of an annular plate around the rotating axis 18 perpendicular to the rotating axis 18.
  • the cylindrical portion 20B is integrally connected to the outer peripheral portion of the disk portion 20A and extends in a cylindrical shape around the rotation axis 18.
  • the sub-rotor 22 extends in the shape of an annular plate around the rotation axis 18 perpendicular to the rotation axis 18, and is connected to the end of the cylindrical portion 20B opposite to the disk portion 20A by a plurality of bolts 24 at the outer periphery. Has been.
  • the disk portion 20A and the sub-rotor 22 have the same thickness, and the thickness of the cylindrical portion 20B is smaller than the thickness of the disk portion 20A and the sub-rotor 22.
  • the cylindrical portion 20 ⁇ / b> B extends in a cylindrical shape around the rotation axis 18, it has higher rigidity than the disk portion 20 ⁇ / b> A and the sub-rotor 22.
  • each of the disk portion 20A and the sub-rotor 22 extends in the shape of an annular plate around the rotation axis 18 perpendicular to the rotation axis 18, and is separated from each other along the rotation axis 18.
  • the cylindrical portion 20 ⁇ / b> B functions as a connecting portion that cooperates with the bolt 24 to integrally connect the outer peripheral portion of the disk portion 20 ⁇ / b> A and the sub-rotor 22.
  • the disk portion 20A, the cylindrical portion 20B, and the sub-rotor 22 have a U-shaped cross-sectional shape opened inward in the radial direction when viewed from a radial cut surface passing through the rotation axis 18.
  • the surfaces of the disk portion 20A and the sub-rotor 22 that face each other include a first friction surface 20S and a second friction surface 22S that extend around the rotation axis 18 in parallel to each other perpendicular to the rotation axis 18, respectively. I have decided.
  • the rotary shaft 17 is rotatably supported around the rotary axis 18 by a sleeve portion 28A of a wheel support member 28 as a stationary member via a pair of ball bearings 26.
  • a space between the pair of ball bearings 26, the rotating shaft 17, and the sleeve portion 28A is filled with a lubricant such as grease.
  • a pair of seal members 30 are arranged on both sides in the axial direction with respect to the pair of ball bearings 26, and the seal member 30 is disposed between the rotary shaft 17 and the sleeve portion 28 ⁇ / b> A so that dust and muddy water do not enter the ball bearing 26. It is sealed.
  • the disk portion 20A of the main rotor 20 is a wheel rim formed by four bolts 32 and nuts screwed to the four bolts 32 while being spaced apart from each other by 90 ° around the rotation axis 18. It is designed to be integrally connected to the part. Therefore, the rotating shaft 17 and the brake rotor 12 (the main rotor 20 and the sub-rotor 22) rotate around the rotating axis 18 together with the wheels.
  • the first pressing member 14 has an annular shape extending around the rotation axis 18 over the entire circumference.
  • the first pressing member 14 has an annular groove 14 ⁇ / b> B that extends around the rotation axis 18 over the entire circumference and opens outward in the radial direction.
  • a solenoid 34 is disposed in the annular groove 14 ⁇ / b> B, and the solenoid 34 extends annularly around the rotation axis 18.
  • energization to the solenoid 34 is controlled by an electronic control unit.
  • the driver's braking operation amount such as the depression force on the brake pedal may be detected, and the control current for the solenoid 34 may be controlled so that the current value increases as the braking operation amount increases.
  • the second pressing member 16 has an annular plate-like portion 16X and a cylindrical portion 16Y that are integral with each other.
  • the annular plate-like portion 16X extends around the rotation axis 18 over the entire circumference, and the outer peripheral portion of the annular plate-like portion 16X is separated from the first pressing member 14 in the first pressing member. 14 and the sub-rotor 22.
  • the cylindrical portion 16Y is fitted to the sleeve portion 28A of the wheel support member 28 with a slight play, and is provided on the inner surface of the cylindrical portion 16Y and the outer surface of the sleeve portion 28A and extends along the rotation axis 18.
  • a key 36 is fitted in the. Therefore, the second pressing member 16 is supported by the wheel support member 28 so as not to rotate around the rotation axis 18 and to be displaceable along the rotation axis 18.
  • the annular plate-like portion 16X has a columnar shoulder portion 16C facing radially outward on the first pressing member 14, and the first pressing member 14 is a cylinder facing the shoulder portion 16C in the radial direction.
  • the shoulder portion 14C has a shape.
  • the shoulder portions 14C and 16C have regions spaced radially from each other at eight positions equally spaced around the rotation axis 18, and a ball is interposed between the shoulder portions 14C and 16C in these regions. 38 is interposed.
  • the ball 38 is formed of a material such as a substantially rigid metal. Therefore, the first pressing member 14 is supported by the second pressing member 16 so as to be rotatable around the rotation axis 18 through the ball 38 and to be displaceable along the rotation axis 18.
  • the first pressing member 14 and the second pressing member 16 have eight cam surfaces 14Z and 16Z that can be engaged with the corresponding balls 38 on the side surfaces facing each other in the region between the shoulder portion 14C and the shoulder portion 16C. Respectively. As shown in FIG. 2, each of the cam surfaces 14 ⁇ / b> Z and 16 ⁇ / b> Z is provided at a circumferential position where the corresponding ball 38 is disposed, and extends in an arc shape with the rotation axis 18 as the center.
  • the cam surface 14 ⁇ / b> Z includes a curved portion 14 ⁇ / b> ZA that opens toward the second pressing member 16, and a planar inclined portion that extends continuously on both sides of the curved portion. 14ZB and 14ZC.
  • the inclined portions 14ZB and 14ZC are inclined with respect to a virtual plane 40 perpendicular to the rotation axis 18 so as to approach the second pressing member 16 as the distance from the curved portion 14ZA increases.
  • the cam surface 16Z has a curved portion 16ZA that opens toward the first pressing member 14, and planar inclined portions 16ZB and 16ZC that extend continuously on both sides of the curved portion. ing.
  • the inclined portions 16ZB and 16ZC are inclined with respect to the virtual plane 40 so as to approach the first pressing member 14 as the distance from the curved portion 16ZA increases.
  • the inclination angles of the inclined portion 14ZB and the like with respect to the virtual plane 40 are the same. Therefore, the inclined portions 14ZB and 16ZC and 14ZC and 16ZB facing each other in the radial direction of each ball 38 are inclined in the same direction with respect to the virtual plane 40 and extend parallel to each other.
  • the inner peripheral portion of the sub-rotor 22 is fitted to the sleeve portion 28A of the wheel support member 28 as shown in FIG.
  • a seal member 42 that extends over the entire circumference around the rotation axis 18 is disposed.
  • the main rotor 20 and the sub-rotor 22 cooperate with the rotating shaft 17, the wheel support member 28, and the seal member 42 to form a sealed space 44, and the first pressing member 14, the second pressing member 16, The solenoid 34 and the ball 38 are accommodated in the sealed space 44.
  • the sealed space 44 is filled with a lubricant. Therefore, substantially no frictional force is generated between the balls 38 and the shoulders 14C and 16C and between the balls 38 and the cam surfaces 14Z and 16Z.
  • first rotational friction members 50 are arranged between the first pressing member 14 and the disk portion 20 ⁇ / b> A of the main rotor 20. It is substantially disk-shaped around an axis 52 parallel to the rotation axis 18.
  • second rotational friction members 54 are disposed between the second pressing member 16 and the sub-rotor 22, and each rotational friction member 54 is centered on an axis 56 parallel to the rotational axis 18. It has a substantially disk shape.
  • the axes 52 and 56 are aligned with each other, and the first rotating friction member 50 and the second rotating friction member 54 are spaced 90 ° around the rotation axis 18 with respect to each other.
  • the first rotary friction member 50 has friction portions 50A and 50B on both side surfaces of the outer peripheral portion, and the friction portions 50A and 50B can be frictionally engaged with the side surfaces of the disk portion 20A and the first pressing member 14, respectively. It has become.
  • the second rotational friction member 54 has friction portions 54A and 54B on both side surfaces of the outer peripheral portion so that the friction portions 54A and 54B can be frictionally engaged with the side surfaces of the sub-rotor 22 and the second pressing member 16, respectively. It has become.
  • Each friction part extends in the form of an annular band around the axes 52 and 56 of the rotary friction members 50 and 54 in a state of protruding from the side surface of the disk-shaped main body.
  • the friction part may be formed integrally with the disk-shaped main body by manufacturing the first rotating friction member 50 and the second rotating friction member 54 by, for example, a powder sintering method.
  • the friction portion may be formed by attaching an annular belt-like friction material to the side surface of the main body by bonding or other means.
  • the friction portions 50A, 50B and 54A, 54B are made of the same friction material, they may be made of different friction materials.
  • the first pressing member 14 and the second pressing member 16 are positioned at the standard positions shown in FIG.
  • the distance between the cam surfaces 14Z and 16Z in the direction along the rotation axis 18 is minimized, and the ball 38 separates the cam surfaces 14Z and 16Z to separate the two pressing surfaces. No force is generated to separate the members 14 and 16. Therefore, the friction portions 50A and 50B of the first rotating friction member 50 do not substantially frictionally engage with the friction surface 20S of the disk portion 20A and the outer surface of the first pressing member 14, respectively.
  • the friction portions 54 ⁇ / b> A and 54 ⁇ / b> B of the second rotational friction member 54 are not substantially frictionally engaged with the friction surface 22 ⁇ / b> S of the sub-rotor 22 and the outer surface of the second pressing member 16, respectively.
  • External gears 58 and 60 are provided on the outer peripheral portions of the main body of the first rotary friction member 50 and the second rotary friction member 54, respectively.
  • the external gears 58 and 60 are the inner periphery of the cylindrical portion 20B of the main rotor 20.
  • the inner gears 62 and 64 provided on the surface mesh with each other. Therefore, the first rotational friction member 50 and the second rotational friction member 54 are displaced relative to the cylindrical portion 20B around the rotation axis 18 so as to roll on the inner peripheral surface of the cylindrical portion 20B of the main rotor 20. Is possible.
  • the first pressing member 14 and the second pressing member 16 have shelves 66 and 68 radially inward with respect to the first rotating friction member 50 and the second rotating friction member 54, respectively.
  • External gears 70 and 72 that mesh with the external gears 58 and 60 of the first rotating friction member 50 and the second rotating friction member 54 are provided on the outer peripheral surfaces of the shelves 66 and 68, respectively.
  • the external gears 58 and 60 of the rotational friction members 50 and 54 mesh with the internal gears 62 and 64 of the cylindrical portion 20B of the main rotor 20 on the radially outer side, and the pressing members 14 and 16 on the radially inner side. Are engaged with the external gears 70 and 72, respectively.
  • the first rotational friction member 50 and the second rotational friction member 54 are planetary gear mechanisms 74 and 76 having internal gears 62 and 64 as internal gears and external gears 70 and 72 as sun gears, respectively. Function.
  • the solenoid 34 when a braking operation is performed by the driver, a control current corresponding to the braking operation amount is supplied to the solenoid 34, and the first pressing member 14 and the disk are electromagnetically generated by the solenoid 34.
  • An attractive force acts between the portion 20A. Therefore, since the first pressing member 14 is pressed against the disk portion 20A, the friction portions 50A and 50B of the first rotating friction member 50 are respectively in contact with the friction surface 20S of the disk portion 20A and the first pressing member 14. Frictionally engages the outer surface. Therefore, the solenoid 34 functions as a pressing force control mechanism that controls the pressing force that presses the first pressing member 14 against the disk portion 20A in cooperation with the first pressing member 14 and the disk portion 20A.
  • the first rotational friction member 50 If a wheel not shown in the drawing is rotating, the first rotational friction member 50 generates a rotational torque around the rotational axis 18 due to a frictional force between the friction part 50A and the friction surface 20S of the disk part 20A. Receiving and trying to rotate around the rotation axis 18 relative to the first pressing member 14. Further, the first rotating friction member 50 tries to rotate the first pressing member 14 around the rotation axis 18 by the frictional force between the friction portion 50 ⁇ / b> B and the outer surface of the first pressing member 14.
  • the first pressing member 14 is supported by the second pressing member 16 so as to be rotatable around the rotation axis 18, but the second pressing member 16 cannot rotate around the rotation axis 18. Therefore, the first pressing member 14 rotates around the rotation axis 18 relative to the second pressing member 16. As a result, the first pressing member 14 and the second pressing member 16 are displaced along the virtual plane 40 as shown in FIG. 4, so that the cam surfaces 14Z and 16Z at the position of the ball 38 try to approach each other. To do. However, since the ball 38 is not compressed and deformed, a so-called wedge effect is generated, and the first pressing member 14 and the second pressing member 16 are relatively displaced along the rotation axis 18 in a direction away from each other.
  • the ball 38 and the cam surfaces 14Z and 16Z cooperate with each other to displace the first pressing member 14 and the second pressing member 16 along the rotation axis 18 in a direction away from each other. Further, the ball 38 and the cam surfaces 14Z and 16Z cooperate with each other to transmit the rotational torque around the rotation axis 18 from the first pressing member 14 to the second pressing member 16, and to apply the rotational torque to the two pressing forces. It converts into the force which separates a member. Further, the ball 38 and the cam surfaces 14Z and 16Z transmit the reaction force generated when the friction engagement member is pressed against the friction surface by the pressing member between the two pressing members.
  • the ball 38 and the cam surfaces 14Z and 16Z transmit the rotational torque between the first pressing member 14 and the second pressing member 16, and generate a force that separates the two pressing members in the direction along the rotation axis 18.
  • a force transmission mechanism 46 that transmits reaction force is configured.
  • the force transmission mechanism 46 converts the relative rotational torque between the first pressing member 14 and the second pressing member 16 into a pressing force.
  • the first pressing member 14 and the second pressing member 16 respectively press the first rotating friction member 50 and the second rotating friction member 54 with a high pressing force, and rotate with respect to the friction surfaces 20S and 22S.
  • the friction members 50 and 54 are pressed with a high pressing force.
  • the ball 38 and the cam surfaces 14Z and 16Z also function as a positioning mechanism that cooperates with each other to position the first pressing member 14 and the second pressing member 16 at the standard position.
  • the relative rotational torque is proportional to the attractive force due to the electromagnetic force generated by the solenoid 34, and the force for separating the first pressing member 14 and the second pressing member 16 is proportional to the relative rotational torque. Therefore, the pressing force with which the first pressing member 14 and the second pressing member 16 press the rotating friction members 50 and 54 against the disk portion 20A and the sub disk 22 is proportional to the amount of braking operation by the driver.
  • the second pressing member 16 is prevented from rotating around the rotation axis 18 relative to the wheel support member 28 by the key 36 and the keyway for receiving the key 36. Therefore, the wheel support member 28 functions as a rotational torque carrying member that receives the rotational torque that the second pressing member 16 receives from the first pressing member 14.
  • the force transmission mechanism 46 transmits the rotational torque around the rotation axis 18 from the first pressing member 14 to the second pressing member 16 and the force transmitting mechanism 46. Due to the wedge action, the rotational torque is converted into a force separating the two pressing members. Further, the reaction force generated by the pressing of the pressing members 14 and 16 is transmitted to the other pressing member via the force transmission mechanism 46.
  • the force transmission mechanism 46 functions as a force-increasing mechanism in cooperation with the wheel support member 28 as a stationary member, it is possible to generate a higher braking force than when the force transmission mechanism 46 is not provided. it can.
  • the reaction force generated by pressing the friction engagement member against the friction surface by the pressing member is supported by the member different from the pressing member.
  • the structure can be simplified as compared with the brake device provided. Further, a higher braking torque can be generated as compared with the brake device described in the above-mentioned publication, in which the friction engagement member is pressed against only one friction surface of the brake disk.
  • the distance between the rotation axis 18 and the center of the ball 38 is 80 mm
  • the distance between the rotation axis 18 and the rotation axes 52 and 56 is 120 mm
  • the rotation axes 52 and 56 are in friction with each other.
  • the distance from the center of the parts 50A, 50B and 54A, 54B is 25 mm.
  • the distance from the rotation axis 18, the external gears 58 and 60 of the rotary friction members 50 and 54, and the internal gears 62 and 64 of the main rotor 20 to the meshing portion is 150 mm.
  • the distance from the rotation axis 18, the external gears 58 and 60 of the rotational friction members 50 and 54, and the meshing portion of the pressing members 14 and 16 to the external gears 70 and 72 is 90 mm.
  • the friction coefficient of each friction contact portion is ⁇
  • the pressing force due to the electromagnetic force generated by the solenoid 34 is F1 (kgf)
  • the pressing force due to the rotation torque being converted into the pressing force by the force transmission mechanism 46 is F2 (kgf).
  • the total pressing force F of the first pressing member 14 and the second pressing member 16 that is, the pressing force F by which the pressing members 14 and 16 press the rotary friction members 50 and 54 against the disk portion 20A and the sub-rotor 22, respectively.
  • F1 must be a positive value so that the force transmission mechanism 46 does not self-lock.
  • F F1 + F2 (1)
  • Trv Braking torque Trv generated when the rotational friction members 50 and 54 are rotated around the rotation axis 18 relative to the disk portion 20A and the sub-rotor 22 while being pressed against the disk portion 20A and the sub-rotor 22 by the pressing members 14 and 16, respectively.
  • the braking torque Tc in the conventional general brake device in which the rotational friction members 50 and 54 are simply pressed against the disk portion 20A and the sub-rotor 22 by the pressing force F1 is expressed by the following equation (8).
  • the braking torque Tc is generated by rotating around the rotation axis 18 in a state where the rotating friction members 50 and 54 do not rotate but are pressed against the disk portion 20A and the sub-rotor 22 by the pressing force F1.
  • the disk portion 20A, the cylindrical portion 20B, and the sub-rotor 22 have a U-shaped cross-sectional shape that is opened inward in the radial direction when viewed in a radial cut surface passing through the rotation axis 18. There is no.
  • the pressing members 14 and 16 are disposed between the disk portion 20A and the sub-rotor 22, and press the rotational friction members 50 and 54 in a direction away from each other.
  • a caliper that extends over both sides of the brake rotor and supports the friction member and the pressing device and carries the reaction force of the pressing force of the pressing device as in the conventional disc brake device and the second embodiment described later. It is also unnecessary to increase the caliper rigidity. Further, since the disk portion 20A and the sub-rotor 22 extend around the rotation axis 18 over the entire circumference, the rigidity of the brake rotor 12 is improved as compared with a caliper that extends only in an arc around the rotation axis. Can be high.
  • the first pressing member 14 can rotate about the rotation axis 18, and the second pressing member 16 cannot rotate about the rotation axis 18.
  • both the first and second pressing members can rotate around the rotation axis 18, and the first and second pressing members can rotate more than a predetermined amount by the stationary member. It may be blocked.
  • FIG. 5 is a cross-sectional view showing a second embodiment of a friction brake device according to the present invention configured as a vehicle brake device, cut along a cutting plane passing through a rotation axis
  • FIG. 6 is a second embodiment.
  • FIG. 7 is a partial cross-sectional view taken along the line VII-VII in FIG. 5 is a cross-sectional view taken along line VV in FIG. 5 to 7, the same members as those shown in FIGS. 1 to 4 are denoted by the same reference numerals as those shown in these drawings.
  • the main rotor 20 does not have the cylindrical portion 20B and is a member different from the rotating shaft 17. Further, the disc-shaped disk portion 20 ⁇ / b> A of the main rotor 20 is integrally connected to the sub-rotor 22 by a connection portion 80 made of a fin for heat dissipation.
  • the rotating shaft 17 has a flange portion 17A at an outer end portion, and the inner peripheral portion of a rim portion 20C integrated with the disc portion 20A is connected to the flange portion 17A by four bolts 32. Therefore, although not shown in the figure, the bolt 32 and the nut screwed to the bolt 32 integrally connect the rim portion 20C together with the flange portion 17A to the disc portion of the wheel.
  • the first rotating friction member 50 and the second rotating friction member 54 are disposed on both sides of the disk portion 20A and the sub-rotor 22 so as to face the outer surfaces thereof.
  • the first pressing member 14 and the second pressing member 16 are arranged on the opposite side of the disk portion 20A and the sub-rotor 22 with respect to the first rotating friction member 50 and the second rotating friction member 54, respectively.
  • the first rotational friction member 50 and the second rotational friction member 54 are formed on the caliper via the balls 38A and 38B by a caliper 88 extending across the outer periphery of the brake rotor 12 and having a substantially U-shaped cross section. It is rotatably supported around the rotation axes 52 and 56.
  • the caliper 88 includes halves 88A and 88B integrally connected by connecting means such as bolts or welding, and the half 88B is fixed integrally to the stationary member 90 by connecting means such as bolts.
  • the balls 38A and 38B are respectively disposed between the cylindrical inner surfaces 14C and 16C of the first pressing member 14 and the second pressing member 16 and the cylindrical inner surfaces 88AC and 88BC provided on the halves 88A and 88B. It is intervened.
  • cam surfaces 88AZ and 88BZ facing the cam surfaces 14Z and 16Z in the direction along the rotation axes 52 and 56 with the balls 38A and 38B interposed therebetween are respectively provided on the inner surfaces of the half bodies 88A and 88B. Is provided.
  • the cam surfaces 88AZ and 88BZ have the same relationship with the cam surfaces 14Z and 16Z as the cam surfaces 16Z and 14Z of the first embodiment.
  • the solenoid 34 is fixed to the outer surface of the radially inner peripheral portion of the half body 88A.
  • the cam surfaces 14Z and 88AZ constitute a force transmission mechanism 46A corresponding to the force transmission mechanism 46 of the first embodiment in cooperation with the ball 38A.
  • the force transmission mechanism 46 ⁇ / b> A transmits rotational torque between the first pressing member 14 and the half body 88 ⁇ / b> A, generates a force that separates the half body 88 ⁇ / b> A in the direction along the rotational axis 18, and transmits a reaction force.
  • the cam surfaces 16Z and 88BZ together with the ball 38B constitute a force transmission mechanism 46B corresponding to the force transmission mechanism 46 of the first embodiment.
  • the force transmission mechanism 46 ⁇ / b> B transmits rotational torque between the second pressing member 16 and the half body 88 ⁇ / b> B, generates a force that separates the half body 88 ⁇ / b> B in the direction along the rotational axis 18, and transmits a reaction force.
  • These force transmission mechanisms 46A and 46B convert the relative rotational torque between the first pressing member 14 and the half body 88A and between the second pressing member 16 and the half body 88B into a pressing force, respectively. Accordingly, the first pressing member 14 and the second pressing member 16 press the first rotating friction member 50 and the second rotating friction member 54 with a high pressing force, respectively, and against the friction surfaces 20S and 22S. The rotary friction members 50 and 54 are pressed with a high pressing force.
  • the ball 38A, the cam surface 14Z, and the cam surface 88AZ also function as a positioning mechanism that cooperates with each other to position the first pressing member 14 at the standard position.
  • the ball 38B, the cam surface 16Z, and the cam surface 88BZ also function as a positioning mechanism that cooperates with each other to position the second pressing member 16 at the standard position.
  • the relative rotational torque is proportional to the attractive force due to the electromagnetic force generated by the solenoid 34, and the force that separates the first pressing member 14 and the half body 88A and the second pressing member 16 and the half body 88B are separated.
  • the force is proportional to the relative rotational torque. Therefore, the pressing force with which the first pressing member 14 and the second pressing member 16 press the rotating friction members 50 and 54 against the disk portion 20A and the sub disk 22 is proportional to the amount of braking operation by the driver.
  • the half bodies 88A and 88B are prevented from rotating around the rotation axis 18 by the stationary member 90. Therefore, the half bodies 88 ⁇ / b> A and 88 ⁇ / b> B and the stationary member 90 function as a rotational torque carrying member that receives the rotational torque received from the first pressing member 14 and the second pressing member 16.
  • the shelves 66 and 68 of the first pressing member 14 and the second pressing member 16 protrude in directions closer to each other than the main body portion of the pressing member, and are opposed to the first rotating friction member 50 and the second rotating friction member 54. It has a cylindrical shape extending around the entire circumference of the rotation axis 18 on the radially inner side.
  • the external gears 70 and 72 provided on the shelves 66 and 68 are respectively connected to the external gears 58 and 60 of the first rotational friction member 50 and the second rotational friction member 54. Meshed.
  • a ring gear member 92 having a substantially cylindrical shape is fixed to the outer periphery of the main rotor 20, that is, the cylindrical outer peripheral surfaces of the disk portion 20 ⁇ / b> A and the sub-rotor 22 by means such as welding.
  • the ring gear member 92 extends around the rotation axis 18.
  • Ring gears 94A and 94B are provided on the inner peripheral surfaces of both ends of the ring gear member 92, and the ring gears 94A and 94B mesh with the external gears 58 and 60 of the rotary friction members 50 and 54, respectively.
  • the external gears 58 and 60 of the rotational friction members 50 and 54 mesh with the internal gears 94A and 94B of the ring gear member 92 on the radially outer side, and the external gears of the pressing members 14 and 16 on the radially inner side. Meshes with 70 and 72, respectively. Therefore, the first rotational friction member 50 and the second rotational friction member 54 are planetary gears of planetary gear mechanisms 74 and 76 in which the internal gears 94A and 94B are internal gears and the external gears 70 and 72 are sun gears, respectively. Function.
  • the solenoid 34 cooperates with the first pressing member 14 and the disk portion 20A to control the pressing force that presses the first pressing member 14 against the disk portion 20A. Functions as a pressure control mechanism.
  • the first rotational friction member 50 If a wheel not shown in the drawing is rotating, the first rotational friction member 50 generates a rotational torque around the rotational axis 18 due to a frictional force between the friction part 50A and the friction surface 20S of the disk part 20A. Receiving and trying to rotate around the rotation axis 18 relative to the first pressing member 14. Further, the first rotating friction member 50 tries to rotate the first pressing member 14 around the rotation axis 18 by the frictional force between the friction portion 50 ⁇ / b> B and the inner surface of the first pressing member 14.
  • the first pressing member 14 is supported by the half body 88A of the caliper 88 so as to be rotatable around the rotation axis 18, but the half body 88A cannot rotate around the rotation axis 18. Therefore, the first pressing member 14 rotates around the rotation axis 18 relative to the half body 88A. As a result, since the first pressing member 14 and the half body 88A are relatively displaced, a so-called wedge effect is generated as in the case of the first embodiment, and the first pressing member 14 and the half body 88A have the rotation axis. 18 are pushed in directions away from each other.
  • the half body 88 ⁇ / b> B presses the second pressing member 16 and the second rotating friction member 54 against the sub-rotor 22.
  • the second rotational friction member 54 receives rotational torque around the rotational axis 18 due to the frictional force between the friction portion 54 ⁇ / b> A and the friction surface 22 ⁇ / b> S of the sub-rotor 22, and the rotational axis 18 is relative to the second pressing member 16. Try to rotate around. Further, the second rotating friction member 54 tries to rotate the second pressing member 16 around the rotation axis 18 by the frictional force between the friction portion 54 ⁇ / b> B and the inner surface of the second pressing member 16.
  • the second pressing member 16 rotates around the rotation axis 18 relative to the half 88B.
  • a so-called wedge effect is generated as in the case of the relative displacement of the first pressing member 14 and the half body 88A. 16 and the half 88B are pressed along the rotation axis 18 in a direction away from each other.
  • the force transmission mechanism 46A transmits the rotational torque around the rotation axis 18 from the first pressing member 14 to the half body 88A, and the wedge transmission of the force transmission mechanism 46A.
  • the rotational torque is converted into a force that separates the two members.
  • the rotational torque around the rotational axis 18 is transmitted from the second pressing member 16 to the half body 88B by the force transmission mechanism 46B, and the rotational torque is applied to the two members by the wedge action of the force transmission mechanism 46B. It is converted into a force for separating.
  • the reaction force generated by the pressing of the pressing members 14 and 16 is transmitted to the other pressing member via the force transmission mechanisms 46A and 46B and the caliper 88.
  • the rotation axes 52 and 56 of the first rotational friction member 50 and the second rotational friction member 54 are not only aligned with each other, but also the force transmission mechanism 46A and It is aligned with the center of 46B balls 38A and 38B. Therefore, as compared with the case where the rotation axes 52 and 56 are not aligned with the centers of the balls 38A and 38B, the rotary friction members 50 and 54 are preferably moved by the pressing force generated by the force transmission mechanisms 46A and 46B. It is possible to press against the sub-rotor 22.
  • the force transmission mechanisms 46A and 46B of the second embodiment function in the same manner as the force transmission mechanism 46 of the first embodiment. Therefore, if the dimensions such as the distance between the rotation axis 18 and the centers of the balls 38A and 38B are the same as in the first embodiment, the braking torque servo ratio Rbt1 is the same as in the first embodiment. is there.
  • the friction portions 50A, 50B and 54A, 54B are integrated with the disc-shaped main bodies of the first rotational friction member 50 and the second rotational friction member 54, respectively. Is formed. Therefore, the number of parts can be reduced and the structure can be simplified as compared with the case where these friction parts are separate from the main bodies of the rotary friction members 50 and 54.
  • the cam surfaces 14Z and 16Z of the force transmission mechanism 46 include the curved portions 14ZA and 16ZA and the planar inclined portions 14ZB, 16ZB and 14ZC extending on both sides of the curved portion, respectively. 16ZC.
  • the cam surface of the force transmission mechanism 46 may have another shape as long as it has an inclined surface inclined in the same direction with respect to the virtual plane 40 perpendicular to the rotation axis 18.
  • the cam surface 14Z may have a mountain shape, and the cam surface 16Z may have a valley shape that receives the cam surface 14Z.
  • a rolling element such as a ball may be interposed between the cam surfaces of the first and second pressing members.
  • the inclined portions 14ZB, 16ZB and 14ZC, 16ZC extending on both sides of the curved portion are inclined so that the inclination angle with respect to the virtual plane 40 gradually decreases as the distance from the curved portion increases. May be curved.
  • the rolling element may be a cylindrical roller or a tapered roller.
  • the two members having cam surfaces facing each other rotate relative to each other around the rotation axis 18, and the rotational torque increases in the direction along the rotation axis 18 as the relative displacement amount of these members increases. It is possible to gradually increase the force component decomposed into Therefore, the brake characteristic of the brake device can be changed to a progressive brake characteristic.
  • the cam surfaces 14Z, 16Z, etc. have the curved portions 14ZA, 16ZA, etc., respectively, but the inclined portions such as the inclined portion 14ZB are not provided with the curved portions. It may consist only of parts.
  • the friction engagement portions 14A and 16A have the same size, and the first rotation friction member 50 and the second rotation friction engagement member 54 are They have the same diameter. However, they may have different sizes and diameters.
  • the friction portions on both sides of the first rotational friction member 50 and the second rotational friction engagement member 54 have the same radius around the axes 52 and 56. It is provided in the position. However, the friction portions on both sides of the rotating friction members 50 and 54 may be provided at positions having different radii.
  • the cylindrical portion 20B is formed integrally with the disc portion 20A to form the main rotor 20.
  • the cylindrical portion 20B may be formed integrally with the sub-rotor 22, and the disc portion 20A, the cylindrical portion 20B, and the sub-rotor 22 may be formed separately.
  • the main rotor 20 and the sub-rotor 22 cooperate with the rotating shaft 17, the wheel support member 28, and the seal member 42 to form the sealed space 44. It may not be formed.
  • the pressing members 14 and 16 and the rotating friction members 50 and 54 are accommodated in the sealed space 44. Therefore, compared with the case where a pressing member etc. are not accommodated in sealed space, the temperature of these members rises easily at the time of operation of brake equipment 10.
  • the friction engagement member is formed of a ceramic friction material having excellent heat resistance as described above, a decrease in braking force due to a temperature rise is small.
  • the main rotor 20 and the subrotor 22 may be provided with the fin for air cooling so that the temperature rise of those members may be suppressed.
  • the first pressing member 14 is urged against the disk portion 20A by the electromagnetic force generated by the solenoid 34.
  • the means for urging the pressing member may be modified to be hydraulic, for example.
  • the brake device of each embodiment is a brake device for vehicles, the brake device of this invention may be applied to uses other than a vehicle.

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

Abstract

L'invention concerne un dispositif (10) de frein à friction comprenant: un rotor (20) de frein présentant des surfaces (20S, 22S) de frottement et tournant autour d'un axe (18) de rotation; des organes tournants (50, 54) de frottement capables de tourner autour d'axes (52, 56) de rotation qui sont parallèles à l'axe de rotation susmentionné; et un dispositif (34) d'appui qui plaque des organes (14, 16) d'appui contre les organes tournants de frottement, et qui plaque les organes tournants de frottement contre les surfaces de frottement. Le rotor de frein, les organes tournants de frottement et les organes d'appui constituent des mécanismes (74, 76) à engrenages satellites qui emploient les organes tournants de frottement comme engrenages satellites. Les organes tournants de frottement interagissent par frottement avec les surfaces de frottement et les organes d'appui, et un mécanisme (46) d'amplification d'effort d'appui, qui convertit un couple de rotation relative en un effort d'appui, est disposé entre les organes d'appui et un organe non tournant (16).
PCT/JP2014/067392 2013-08-07 2014-06-30 Dispositif de frein à friction WO2015019747A1 (fr)

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PCT/JP2014/067392 WO2015019747A1 (fr) 2013-08-07 2014-06-30 Dispositif de frein à friction
PCT/JP2014/070930 WO2015020166A1 (fr) 2013-08-07 2014-08-07 Dispositif de frein à friction
PCT/JP2014/070935 WO2015020168A1 (fr) 2013-08-07 2014-08-07 Dispositif de transmission d'énergie
PCT/JP2014/070933 WO2015020167A1 (fr) 2013-08-07 2014-08-07 Dispositif de transmission de puissance

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PCT/JP2014/070933 WO2015020167A1 (fr) 2013-08-07 2014-08-07 Dispositif de transmission de puissance

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JP5754549B2 (ja) * 2012-04-07 2015-07-29 トヨタ自動車株式会社 摩擦ブレーキ装置
JP5754547B2 (ja) * 2012-04-07 2015-07-29 トヨタ自動車株式会社 摩擦ブレーキ装置
WO2013150658A1 (fr) * 2012-04-07 2013-10-10 トヨタ自動車株式会社 Dispositif de frein à friction
GB2604906B (en) * 2021-03-18 2024-05-22 Integrated Design Ltd An access control system

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JPS58146723A (ja) * 1982-02-24 1983-09-01 Shinko Electric Co Ltd セルフクランプ式高伝達容量の電磁クラツチ又は電磁ブレ−キ
JPS62126630U (fr) * 1986-01-31 1987-08-11
JP2006177532A (ja) * 2004-12-24 2006-07-06 Hitachi Ltd ディスクブレーキ
JP2008151199A (ja) * 2006-12-15 2008-07-03 Toyota Motor Corp 摩擦式伝達率可変型動力伝達装置

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JPH0178755U (fr) * 1987-11-16 1989-05-26
JP3803493B2 (ja) * 1998-06-23 2006-08-02 本田技研工業株式会社 ハイブリッド車両
JP2000016101A (ja) * 1998-06-30 2000-01-18 Honda Motor Co Ltd ハイブリッド車両
JP2000291457A (ja) * 1999-04-07 2000-10-17 Fuji Heavy Ind Ltd ハイブリッド車の制御装置
JP2013107170A (ja) * 2011-11-21 2013-06-06 Panasonic Eco Solutions Power Tools Co Ltd 変速装置
JP5754549B2 (ja) * 2012-04-07 2015-07-29 トヨタ自動車株式会社 摩擦ブレーキ装置

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Publication number Priority date Publication date Assignee Title
DE2633460A1 (de) * 1976-07-24 1978-01-26 Klaue Hermann Verstaerkungsfreie vollbelagscheibenbremse, insbesondere fuer kraftfahrzeuge
JPS58146723A (ja) * 1982-02-24 1983-09-01 Shinko Electric Co Ltd セルフクランプ式高伝達容量の電磁クラツチ又は電磁ブレ−キ
JPS62126630U (fr) * 1986-01-31 1987-08-11
JP2006177532A (ja) * 2004-12-24 2006-07-06 Hitachi Ltd ディスクブレーキ
JP2008151199A (ja) * 2006-12-15 2008-07-03 Toyota Motor Corp 摩擦式伝達率可変型動力伝達装置

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JP6160696B2 (ja) 2017-07-12
WO2015020166A1 (fr) 2015-02-12
JP6020730B2 (ja) 2016-11-02
WO2015020168A1 (fr) 2015-02-12
WO2015020167A1 (fr) 2015-02-12
JPWO2015020167A1 (ja) 2017-03-02
JPWO2015020168A1 (ja) 2017-03-02
JP6052418B2 (ja) 2016-12-27
JPWO2015020166A1 (ja) 2017-03-02
JPWO2015019747A1 (ja) 2017-03-02

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