WO2013157646A1 - 摩擦ブレーキ装置 - Google Patents
摩擦ブレーキ装置 Download PDFInfo
- Publication number
- WO2013157646A1 WO2013157646A1 PCT/JP2013/061683 JP2013061683W WO2013157646A1 WO 2013157646 A1 WO2013157646 A1 WO 2013157646A1 JP 2013061683 W JP2013061683 W JP 2013061683W WO 2013157646 A1 WO2013157646 A1 WO 2013157646A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- friction
- rotation axis
- pressing
- force
- members
- Prior art date
Links
Images
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
-
- 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
- F16D51/02—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as one or more circumferential band
- F16D51/04—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as one or more circumferential band mechanically actuated
-
- 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
- F16D55/225—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 the braking members being brake pads
-
- 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
-
- 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
-
- 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
- F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc 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
- F16D65/14—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
- F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
- F16D65/186—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with full-face force-applying member, e.g. annular
-
- 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
- F16D2121/14—Mechanical
-
- 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
- F16D2125/38—Helical cams, Ball-rotating ramps with plural cam or ball-ramp mechanisms arranged concentrically with the brake rotor axis
-
- 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
- F16D2125/58—Mechanical mechanisms transmitting linear movement
- F16D2125/66—Wedges
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.
- a pair of friction members are pressed against both sides of the disc portion of the brake rotor by a pressing device, and a braking force is generated by frictional contact between them.
- the pair of friction members are supported on both sides of the brake rotor by calipers that partially cross the outer periphery of the brake rotor, and the pressing device is also supported by the calipers.
- the friction brake device there is a brake device that presses the friction member against the brake rotor and generates a rust action by using the rotational torque received by the friction member from the brake rotor, thereby increasing the pressing force.
- Patent Document 2 describes a friction brake device having a self-boosting mechanism that generates a wedge action. According to this type of friction brake device, 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 pair of friction members extend only in a limited range in the circumferential direction of the entire circumference of the brake rotor, and the region where the pair of friction members press and The frictional contact area is only a small part of the entire circumference of the brake rotor. Therefore, at the time of operation of the friction brake device, the region where the compression load due to the pressing force of the pair of friction members acts periodically moves in the circumferential direction as the brake rotor rotates.
- the pressing device is a general hydraulic cylinder-piston device
- the piston vibrates and the cylinder chamber pressure vibrates.
- the pressing device is an electromagnetic actuator
- the control current vibrates due to the vibration change of the counter electromotive force. Therefore, the braking torque applied to the brake rotor by the pair of friction members periodically varies, and as a result, brake vibration such as flutter, brake pedal vibration, and vehicle body vibration is likely to occur.
- the reaction force of the pressing force by the pressing device acts on the caliper. If the caliper is deformed by the reaction force acting in this way, the braking force cannot be generated effectively. Therefore, the caliper must have the strength and size to suppress the deformation. Therefore, in order to generate a high braking force, an increase in the size of the caliper is unavoidable, and this problem cannot be solved even by the structure described in Patent Document 1.
- the member that supports the reaction force of the pressing force is configured independently of the pressing device.
- the structure of the brake device is inevitable.
- the application of the pressing force by the pressing device and the increase of the pressing force due to the wedge action are performed only on one side of the brake rotor, so the braking force cannot be made sufficiently high.
- the main object of the present invention is to generate a high braking force while suppressing an increase in the size and complexity of the brake device, and to generate brake vibration and squeal as compared with a conventional friction brake device. It is to provide a difficult friction brake device.
- the first and second disk parts extending in an annular shape around the rotation axis in a state of being spaced apart from each other along the rotation axis, and the outer circumferences of the first and second disk parts
- a brake rotor having a connecting part for connecting the parts integrally, and first and second friction members extending annularly around the rotation axis between the first and second disk parts,
- the first and second friction members are supported by the stationary member so that they can be displaced relative to the first and second disk portions along the rotation axis and the rotation around the rotation axis is limited.
- Friction brake device disposed between the first and second friction members, pressing the first and second friction members against the first and second disc parts, respectively, and one friction member The reaction force received by one disk part through the other friction member Friction brake device is provided having a pressing device for transmitting to the disc portion.
- the first and second friction members extend in an annular shape around the rotation axis similarly to the first and second disk portions, and the first and second friction members are formed by the pressing device. Each is pressed against the first and second disk portions. As a result, the first and second friction members are always in frictional contact with the first and second disk portions over the entire circumference around the rotation axis.
- the region where the pressing force of each friction member acts when the friction brake device is operated is local as in the case of the conventional disk type friction brake device, and periodically moves in the circumferential direction as the brake rotor rotates. This can be effectively prevented.
- the first and second friction members are supported by the stationary member so as to be relatively displaceable with respect to the first and second disk portions along the rotation axis, and are frictionally applied to the disk portions and the entire circumference. In the state of contact, each is pressed against the corresponding disk portion.
- the brake rotor has the first and second disk parts spaced apart from each other along the rotation axis and integrally connected by the connection part at the outer peripheral part, and the first and second disk parts are interposed between them.
- First and second friction members are disposed. The first and second friction members are pressed against the corresponding disk portion by a pressing device disposed therebetween, and the reaction force received by one friction member from the one disk portion is the other friction member. To the other disk part.
- a caliper that supports the pair of friction members and the pressing device on both sides of the disk and carries the reaction force of the pressing force of the pressing device is unnecessary, and it is not necessary to increase the rigidity of the caliper.
- the rigidity of the rotating member is higher than that of a caliper that extends only in an arc shape around the rotation axis. can do.
- the pressing device is disposed between the first and second disk portions together with the first and second friction members, compared to the case where the two pressing devices are disposed on both sides of the disk, The structure of piping and the like necessary for driving the pressing device can be simplified. Further, the pressing device is disposed between the first and second friction members, and the reaction force received by one friction member from one disk portion is transmitted to the other disk portion via the other friction member. The reaction force can be used effectively to increase the pressing force.
- the rigidity of rotating members is increased while suppressing the increase in size, complexity of the structure, and cost increase, thereby improving the rigidity and durability of the friction brake device. And a high braking force can be generated.
- the pressing device is configured to apply the pressing and reaction force of the first and second friction members at a plurality of positions spaced from each other in the circumferential direction around the rotation axis. It may be configured to communicate.
- the pressing of the first and second friction members by the pressing device and the transmission of the reaction force are performed at a plurality of positions spaced from each other in the circumferential direction around the rotation axis. Therefore, compared to the case where the pressing of the friction member and the transmission of the reaction force are performed only in a small part of the entire circumference around the rotation axis, the number of areas for the transmission of the pressing and the reaction force is increased.
- the region can be dispersed in the circumferential direction, thereby reducing the pressure caused by the pressure applied to the disk portion. Therefore, the wear of the disk portion can be reduced and the durability of the friction brake device can be improved as compared with the conventional disk type friction brake device.
- the pressure due to the pressure received by each part of the disk part causes the rotation of the disk part. Accordingly, it is possible to reduce the possibility of periodic fluctuations. Therefore, this also makes it possible to reduce the possibility of occurrence of brake vibration and brake squeal as compared with the conventional disk-type friction brake device.
- the first friction member is supported by the stationary member so as to be rotatable relative to the second friction member around the rotation axis, and the second friction member is supported.
- the member is supported non-rotatably around the rotation axis by a stationary member, and the pressing device rotates with a pressing force control mechanism that controls at least the force that presses the first friction member against the first disk portion.
- a plurality of force transmission mechanisms that are arranged apart from each other around the axis and transmit force between the first and second friction members.
- the force transmission mechanism includes the first and second force transmission mechanisms.
- Rotational torque about the rotational axis is transmitted between the friction members of the first and second friction members, and the rotational torque is generated by utilizing the wedge action generated by the relative rotational displacement of the first and second friction members about the rotational axis.
- Separate the first and second friction members along the axis of rotation. Converts the direction of the force to, may be configured to transmit mutually between the reaction force of the first and second friction members each friction member receives.
- the first friction member is supported by the stationary member so as to be rotatable relative to the second friction member around the rotation axis, and the second friction member is rotated by the stationary member. It is supported non-rotatably around.
- the force which presses at least a 1st friction member with respect to a 1st disc part is controlled by the pressing force control mechanism of a pressing device. Therefore, when at least the first friction member is pressed against the first disk portion and the first friction member makes frictional contact with the first disk portion, the first friction member generates a rotational torque from the first disk portion. Receiving and rotating about the rotation axis relative to the second friction member.
- the rotational torque transmitted from the first friction member to the second friction member by the force transmission mechanism is supported by the stationary member.
- the force transmission mechanism converts the force due to the rotational torque into a force in the direction of separating the first and second friction members along the rotation axis by utilizing the wedge action, and the reaction force received by each friction member. Is transmitted between the first and second friction members.
- the force transmission mechanisms are arranged in a state of being spaced apart from each other around the rotation axis.
- the rotational force received by the first friction member from the first disk portion is effectively utilized to apply the force that presses the first and second friction members against the first and second disk portions, respectively.
- the force can be increased over the entire circumference.
- the force for pressing the first and second friction members against the first and second disk portions is increased over the entire circumference around the rotation axis. be able to. Therefore, the braking force generated by the brake device can be increased without increasing the force with which the pressing device presses at least the first friction member against the first disk portion.
- the pressing force control mechanism includes a solenoid supported by the first friction member and extending in an annular shape around the rotation axis, and the solenoid is electrically attached.
- the force for pressing the first friction member against the first disk portion may be controlled by the electromagnetic force generated by being biased.
- produces is controlled by controlling the control current with respect to a solenoid,
- the force which presses a 1st friction member with respect to a 1st disc part can be controlled. it can. Therefore, the friction brake device of the present invention can be applied to a by-wire type brake device.
- the solenoid is supported by the first friction member and extends in an annular shape around the rotation axis. Therefore, for example, the structure of the brake device can be simplified as compared with the case where a plurality of solenoids are provided apart from each other around the rotation axis, and the entire circumference around the rotation axis is uniform.
- the first friction member can be pressed against the first disk portion.
- the pressing force control mechanism includes a cylinder-piston device that is supported by the second friction member and extends in an annular shape around the rotation axis.
- the apparatus has a cylinder chamber and a piston that engages the first friction member at the tip, and the first and second friction members are moved to the first and second discs by increasing or decreasing the pressure in the cylinder chamber, respectively. You may comprise so that the force pressed against a part may be controlled.
- the friction brake device of the present invention can be applied to a pressure control type brake device such as a hydraulic type.
- the cylinder-piston device is supported by the second friction member and extends in an annular shape around the rotation axis. Therefore, for example, the structure of the brake device can be simplified and the entire circumference around the rotation axis can be simplified as compared with the case where a plurality of cylinder-piston devices are provided apart from each other around the rotation axis.
- the first friction member can be uniformly pressed against the first disk portion.
- the cylinder-piston device is supported by a second friction member that is supported by a stationary member so as not to rotate about the rotation axis. Therefore, the structure of the brake device can be simplified as compared with the case where the cylinder-piston device is supported by the first friction member supported rotatably around the rotation axis by the stationary member.
- the pressing device may be configured to perform the pressing of the first and second friction members and the transmission of the reaction force on the entire circumference around the rotation axis.
- the pressing of the first and second friction members by the pressing device and the transmission of the reaction force are performed all around the rotation axis. Therefore, compared to the case where the pressing of the friction member and the transmission of the reaction force are performed only in a small part of the entire circumference around the rotation axis, the area of the area where the pressing and the reaction force is transmitted is increased. Thus, it is possible to reduce the pressure due to the pressure received by the disk portion. Therefore, the wear of the disk portion can be reduced and the durability of the friction brake device can be improved as compared with the conventional disk type friction brake device.
- the pressure due to the pressure received by each part of the disk part causes the rotation of the disk part. Accordingly, it is possible to reduce the possibility of periodic fluctuations. Therefore, this also makes it possible to reduce the possibility of occurrence of brake vibration and brake squeal as compared with the conventional disk-type friction brake device.
- the pressing device includes a piston-cylinder device that is supported by one of the first and second friction members and extends annularly around the rotation axis,
- the piston-cylinder device has a cylinder chamber and a piston that engages the other of the first and second friction members at the tip, and the first and second friction members are adjusted by increasing or decreasing the pressure in the cylinder chamber.
- Each may be configured to press against the first and second disk portions.
- the first and second friction members can be simultaneously pressed against the first and second disk portions by the piston-cylinder device with the same pressing force, and the reaction caused by the pressing can be performed.
- the force can be transmitted via a piston-cylinder device. Further, by controlling the pressure in the cylinder chamber, it is possible to simultaneously control the pressing force when the first and second friction members are pressed against the first and second disk portions, respectively.
- the radial ranges of the regions where the first and second friction members are in frictional contact with the first and second disk portions, respectively, are configured to be the same. It's okay.
- the radial range of the region where the first and second friction members respectively press the first and second disk portions and the region receiving the reaction force are the same. Therefore, compared with the case where these are different from each other, the internal stress of the brake device can be reduced, thereby improving the durability of the brake device. Further, the braking torque applied by the first and second friction members to the first and second disk portions and the radial range in which the reaction torque acts are the same. Therefore, also by this, the internal stress of the brake device can be reduced and the durability of the brake device can be improved.
- the force transmission mechanism includes first and second opposing surfaces provided on the first and second friction members, respectively, facing each other,
- the second facing surface has a region inclined in the same direction with respect to a virtual plane perpendicular to the rotation axis, and the first and second facing surfaces cooperate with each other between the first and second friction members.
- the wedge action can be exerted by the cooperation of the first and second opposing surfaces. it can. Therefore, the rotational torque can be reliably converted into a force in the direction of separating the first and second friction members along the rotation axis, and the reaction force received by each friction member can be converted into the first and second friction members. Can be reliably transmitted to each other.
- the first friction member is supported by the stationary member via the second friction member so as to be rotatable relative to the second friction member around the rotation axis. It may be.
- the pressure in the cylinder chamber may be controlled via an internal passage provided in the stationary member.
- the force transmission mechanism is provided on the first and second friction members, respectively, and the first and second opposing surfaces facing each other, and the rolling mechanism disposed between the opposing surfaces.
- a rotating body, and transmission of rotational torque, conversion of force, and transmission of reaction force may be performed between the inclined regions of the first and second opposing surfaces via the rolling body.
- the connecting portion is formed integrally with one of the first and second disk portions, and the other of the first and second disk portions is integrated with the connecting portion by a connecting device that can be disconnected. May be linked together.
- the brake rotor may cooperate with the non-rotating member to define a sealed space that accommodates the first and second friction members and the pressing device.
- the sealed space may be filled with a lubricating liquid.
- the first and second friction members are positioned at a standard position with respect to each other, and the force transmission mechanism is the first and second friction members. A force in a direction to separate the second friction material may not be generated.
- the force transmission mechanism separates the first and second friction members as the relative rotational displacement of the first and second friction members by the rotational torque increases with reference to the standard position. It is possible to increase the power of.
- the first and second opposing surfaces have a region where the inclination angle with respect to the virtual plane is zero, and when the force controlled by the pressing force control mechanism is zero, the inclination angle is zero.
- the first and second friction members may be positioned at the standard position by facing each other in the direction along the rotation axis.
- the first and second opposing surfaces on both sides of the region where the inclination angle is 0 may be inclined in directions opposite to each other with respect to the virtual plane.
- the brake device is a brake device for a vehicle, and the connecting portion is formed integrally with one of the first and second disc portions, and the brake device is configured to be a wheel at the one disc portion. It may be connected to the rim portion.
- 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 the 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. It is a fragmentary sectional view which cuts and shows 2nd embodiment of the friction brake device by this invention comprised as a hydraulic brake device for vehicles by the cut surface which passes along a rotating shaft.
- FIG. 10 is an enlarged partial sectional view taken along line XI-XI in FIG. 9. It is explanatory drawing which shows the principle of the increase of the pressing force in the friction brake device by this invention. 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 cut surface 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.
- a first friction engagement portion 14A that functions as a first friction engagement member is integrally formed on a side surface of the disk portion 20A of the first pressing member 14 that faces the first friction surface 20S.
- the first friction engagement portion 14 ⁇ / b> A extends around the rotation axis 18 in the form of an annulus 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.
- a second frictional engagement portion 16A that functions as a second frictional engagement member is integrally formed on the side surface of the annular plate-shaped portion 16X opposite to the first pressing member 14.
- the second friction engagement portion 16A extends around the rotation axis 18 in the shape of a ring band around the rotation axis 18 in a state of facing the second friction surface 22S.
- the first pressing member 14 and the second pressing member 16 are manufactured by, for example, a powder sintering method, so that the first friction engagement portion 14A and the second friction engagement portion 16A are respectively the first friction engagement portion 16A.
- the pressing member 14 and the second pressing member 16 may be formed integrally.
- the friction engagement portions 14A and 16A may be formed by attaching an annular belt-like friction material to the side surface of the disc portion by bonding or other means.
- the friction engagement portions 14A and 16A are made of the same friction material, they may be made of different friction materials.
- the friction material may be any friction material excellent in durability, but is preferably a ceramic friction material particularly excellent in heat resistance.
- 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.
- the first pressing member 14 and the second pressing member 16 are positioned at the standard positions shown in FIG.
- the distance between the surface of the first friction engagement portion 14A and the surface of the second friction engagement portion 16A in the direction along the rotation axis 18 is minimized. No force is generated to separate the two pressing members. Therefore, the first friction engagement portion 14A and the second friction engagement portion 16A do not substantially frictionally engage with the disk portion 20A and the friction surfaces 20S and 22S of the sub-rotor 22, respectively.
- 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 first friction engagement portion 14A is frictionally engaged with the first friction surface 20S of the disk portion 20A. Therefore, the solenoid 34 functions as a part of a pressing device that cooperates with the first pressing member 14 and the disk portion 20A to press the first pressing member 14 against the disk portion 20A. 14 functions as a first friction member that frictionally engages with the disk portion 20A.
- the first pressing member 14 is rotated around the rotation axis 18 by the frictional force between the first friction engagement portion 14A and the friction surface 20S of the disk portion 20A. Is rotated around the rotation axis 18 relative to the second pressing member 16.
- the first pressing member 14 and the second pressing member 16 are relatively rotated and displaced in opposite directions as shown in FIG. 4, so that the cam surfaces 14Z and 16Z at the position of the ball 38 are close to each other. try to.
- 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 first friction engagement portion 14A and the second friction engagement portion 16A are pressed against the friction surfaces 20S and 22S of the disc portion 20A and the sub-disc 22 by the action of the force transmission mechanism 46, respectively, thereby corresponding. Frictionally engages the friction surface.
- the second pressing member 16 functions as a second friction member that frictionally engages with the sub-disk 22 in cooperation with the first pressing member 14 and the force transmission mechanism 46.
- the solenoid 34, the first pressing member 14, the second pressing member 16, and the force transmission mechanism 46 cooperate with each other so that the first pressing member 14 and the second pressing member 16 are respectively connected to the disk portion 20A and the sub-unit. It functions as a pressing device that presses against the disk 22.
- 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 rotational torque is proportional to the attractive force generated by 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 rotational torque. Therefore, the pressing force exerted by the first pressing member 14 and the second pressing member 16 on the disc portion 20A and the sub-disc 22 is proportional to the braking operation amount of 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 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 in a radial cut surface passing through the rotation axis 18.
- the pressing members 14, 16 and the like are disposed between the disk portion 20A and the sub-rotor 22, and press the friction engagement portions 14A, 16A and the like in a direction away from each other. Further, the frictional engagement portions 14A and 16A of the pressing members 14 and 16 always make frictional contact with the friction surfaces 20S and 22S of the disc portion 20A and the sub-disc 22 over the entire circumference around the rotation axis 18, respectively.
- the braking torque applied to the brake rotor 12 by the pair of friction engagement members may periodically vary as compared with a conventional friction brake device in which pressing and friction contact are performed only on a small part of the entire circumference. Can be reduced. Accordingly, it is possible to effectively reduce the possibility of occurrence of brake vibration such as flutter, brake pedal vibration, and vehicle body vibration due to periodic fluctuations in the braking torque.
- the brake rotor is locally and periodically deformed and the pressing force against the brake rotor is periodically changed as compared with a conventional friction brake device in which pressing and frictional contact are performed only in a small part of the entire circumference. It is possible to reduce the possibility of fluctuations, thereby effectively reducing the possibility of vibration of the brake rotor, abnormal wear, and occurrence of brake squeal. These functions and effects can be similarly obtained in other embodiments described later.
- the pressing members 14, 16 and the like are disposed between the disk portion 20A and the sub-rotor 22, and the pressing members 14, 16 are separated from the disk portion 20A and the sub-rotor 22, respectively. Pressed in the direction.
- 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. Therefore, the braking force can be efficiently generated by the friction force between the friction engagement portions 14A and 16A and the friction surfaces 20S and 22S by effectively utilizing the reaction force.
- a caliper that extends across both sides of the brake rotor and supports the friction member and the pressing device and supports the reaction force of the pressing force of the pressing device as in the conventional disc brake device is unnecessary, and the rigidity of the caliper is reduced. It is not necessary to make it higher.
- 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. Accordingly, the reaction force generated by pressing the frictional engagement member against the friction surface by the pressing member simplifies the structure as compared with a brake device supported by a member different from the pressing member. The enlargement of the brake device can be avoided.
- 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 transmission 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.
- FIG. 5 is a partial cross-sectional view showing a second embodiment of the friction brake device according to the present invention configured as a hydraulic vehicle brake device, cut along a cut surface passing through the rotation axis, and FIG. It is the partial front view which looked at 2nd embodiment from the right side of FIG. 5 is a cross-sectional view taken along line VV in FIG. 5 and 6, the same members as those shown in FIGS. 1 and 2 are denoted by the same reference numerals as those shown in FIGS.
- the inner peripheral portion of the sub-rotor 22 is not engaged with the wheel support member 28 and is directed radially outward from the wheel support member 28 along the rotation axis 18 toward the disk portion 20A. It has a cylindrical portion 22A that extends. The tip of the cylindrical portion 22 ⁇ / b> A is spaced apart from the second pressing member 16.
- the second pressing member 16 has a cylindrical hole 50 having a step on the first pressing member 14 side, and the cylindrical hole 50 extends around the rotation axis 18 over the entire circumference and along the rotation axis 18. It is extended.
- the first pressing member 14 has a cylindrical portion 52 on the inner peripheral portion, and the cylindrical portion 52 extends around the rotation axis 18 over the entire circumference and extends along the rotation axis 18.
- the cylindrical portion 52 is fitted to a cylindrical outer surface 50 ⁇ / b> A on the radially inner side of the cylindrical hole 50 so as to be capable of relative rotation around the rotation axis 18 and relative displacement along the rotation axis 18.
- a cylindrical body 54 is substantially closely fitted to the cylindrical outer surface 50B on the radially outer side of the cylindrical hole 50, and the cylindrical body 54 extends around the rotation axis 18 and rotates around it. It extends along the axis 18.
- a cylindrical piston 56 is disposed between the cylindrical body 54 and the cylindrical inner surface 50 ⁇ / b> C of the cylindrical hole 50. The piston 56 also extends around the rotation axis 18 over the entire circumference and the rotation axis 18. Extends along.
- the piston 56 is substantially closely fitted to the cylindrical body 54 and the cylindrical inner surface 50C so as to be displaceable along the rotational axis 18 relative to the cylindrical body 54 and the second pressing member 16.
- the space between the cylindrical outer surface 50B on the radially outer side and the cylindrical body 54 is sealed with an O-ring seal 58. Further, the cylindrical body 54 and the cylindrical inner surface 50C and the piston 56 are sealed by O-ring seals 60 and 62, respectively. Therefore, the second pressing member 16, the cylindrical body 54, and the piston 56 form a hydraulic piston-cylinder device 66 having a cylinder chamber 64 that extends around the rotation axis 18 over the entire circumference.
- the second pressing member 16 is provided with a port 68 that is connected to a master cylinder (not shown).
- the port 68 communicates with an annular passage 70 extending around the rotation axis 18 around the rotation axis 18 inside the second pressing member 16, and the annular passage 70 has a diameter inside the second pressing member 16.
- the cylinder chamber 64 is connected in communication with a plurality of radial passages 72 extending in the direction. Therefore, the master cylinder pressure is introduced into the cylinder chamber 64 via the port 68, the annular passage 70, and the radial passage 72.
- the piston-cylinder device 66 causes the first pressing member 14 and the second pressing member 16 to move in the opposite directions with respect to the disk portion 20A and the sub disk 22, respectively, with a pressing force corresponding to the master cylinder pressure. It functions as a part of the pressing device for pressing. These pressing forces correspond to the pressure in the cylinder chamber 64, and hence the master cylinder pressure, and therefore correspond to the braking operation amount of the driver.
- a force transmission mechanism 46 having the same structure as the force transmission mechanism 46 of the first embodiment is provided.
- the force transmission mechanism 46 is arranged radially outside the piston-cylinder device 66, but may be arranged radially inside the piston-cylinder device 66. Further, other points of the second embodiment are formed in the same manner as the first embodiment described above.
- the first pressing member 14 is pressed against the disk portion 20A by the pressing force of the piston-cylinder device 66, and receives the rotational torque from the disk portion 20A when frictionally engaged with the first friction surface 20S of the disk portion 20A.
- the second pressing member 16 is pressed against the sub-disk 22 by the pressing force of the piston-cylinder device 66 and frictionally engages with the second friction surface 22S of the sub-disk 22, the rotational torque from the sub-disk 22 is increased.
- the first pressing member 14 Since the first pressing member 14 is supported by the second pressing member 16 so as to be rotatable around the rotation axis 18, the first pressing member 14 rotates around the rotation axis 18.
- the second pressing member 16 is relatively displaceable along the rotation axis 18, but is supported so as not to be relatively rotatable around the rotation axis 18. Does not rotate around 18. Therefore, the first pressing member 14 and the second pressing member 16 rotate relative to each other.
- a part of the rotational torque transmitted to the first pressing member 14 rotates the first pressing member 14 and the second pressing member 16 by the force transmission mechanism 46. It is converted into a force that urges away from each other along the axis 18. Thereby, the force which presses the 1st press member 14 and the 2nd press member 16 with respect to the disc part 20A and the sub disc 22 is increased. Further, the force that the first pressing member 14 and the second pressing member 16 receive from the disk portion 20A and the sub disk 22 as the reaction force of the pressing force is transmitted to the other pressing member, and as an effective pressing force. Works.
- the piston-cylinder device 66 cooperates with the first pressing member 14 and the second pressing member 16, and these pressing members are respectively connected to the disk portion 20A and the disk portion 20A. It functions as a pressing device that presses against the sub-disk 22.
- the first pressing member 14 and the second pressing member 16 are the first and second friction members that frictionally engage with the disk portion 20A and the sub disk 22, respectively. Function as.
- the pressing force generated by the piston-cylinder device 66 is proportional to the amount of braking operation by the driver, and the pressing force increased by the force transmission mechanism 46 is proportional to the pressing force generated by the piston-cylinder device 66. To do. Therefore, the pressing force that presses the first pressing member 14 and the second pressing member 16 against the disc portion 20A and the sub disc 22 is proportional to the amount of braking operation by the driver.
- the piston-cylinder device 66 pushes both of the pressing members 14 and 16 against the disk portion 20A and the sub disk 22 in the opposite directions, respectively.
- the same operation as in the embodiment can be obtained. Therefore, the same effect as the case of the first embodiment can be obtained.
- the cylinder chamber 64 of the piston-cylinder device 66 is formed on the side of the second pressing member 16 that does not rotate relative to the wheel support member 28 that is a stationary member. . Therefore, the structure of the brake device 10 can be simplified as compared with the case where the cylinder chamber is formed on the side of the first pressing member 14 that rotates relative to the wheel support member 28. . This also applies to the third embodiment described later.
- FIG. 7 is a partial cross-sectional view showing a third embodiment of the friction brake device according to the present invention configured as a hydraulic vehicle brake device, cut along a cutting plane passing through the rotation axis.
- the same members as those shown in FIGS. 5 and 6 are denoted by the same reference numerals as those shown in these drawings.
- This third embodiment is a modification of the above-described third embodiment, and in this embodiment, the force transmission mechanism 46 is not provided. Further, the piston-cylinder device 66 is arranged on the outer side in the radial direction than the piston-cylinder device of the third embodiment. Furthermore, the inner surface of the cylindrical portion 52 of the first pressing member 14 and the cylindrical outer surface 50A of the second pressing member 16 have key grooves extending along the rotation axis 18, and these key grooves have A key 74 is inserted. Accordingly, the first pressing member 14 can be displaced relative to the second pressing member 16 along the rotation axis 18, but is relatively positioned relative to the second pressing member 16 around the rotation axis 18. It cannot be rotated. Other points of this embodiment are the same as those of the third embodiment described above.
- FIG. 8 is a partial cross-sectional view showing a fourth embodiment of the friction brake device according to the present invention configured as a hydraulic vehicular brake device, cut along a cut surface passing through the rotation axis.
- the same members as those shown in FIGS. 5 to 7 are denoted by the same reference numerals as those shown in these drawings.
- the fourth embodiment is another modification of the third embodiment described above, and the force transmission mechanism 46 is not provided in this embodiment.
- an intermediate member 82 that extends annularly around the rotation axis 18 over the entire circumference is disposed between the first pressing member 14 and the second pressing member 16.
- the intermediate member 82 is rigidly connected to the sleeve portion 28A of the wheel support member 28 by the key 36 at the inner peripheral portion 82X.
- the intermediate member 82 has cylindrical portions 82 ⁇ / b> A and 82 ⁇ / b> B protruding on both sides along the rotation axis 18, and these cylindrical portions extend around the rotation axis 18 in an annular shape over the entire circumference.
- the circular plate-shaped first pressing member 14 and the second pressing member 16 are fitted in the cylindrical portions 82A and 82B, respectively.
- the cylindrical outer surfaces of the cylindrical portions 82A and 82B and the cylindrical inner surfaces of the pressing members 14 and 16 are provided with spline teeth extending along the rotation axis 18 and meshing with each other. . Therefore, the first pressing member 14 and the second pressing member 16 can be displaced relative to the intermediate member 82 along the rotation axis 18, but are relatively relative to the intermediate member 82 around the rotation axis 18. Is supported by the intermediate member 82 so as not to rotate.
- cylinders 84 and 86 are disposed between the first pressing member 14 and the second pressing member 16, and these cylinders are relative to the intermediate member 82 along the rotation axis 18.
- the intermediate member 82 is fitted to a cylindrical outer peripheral surface 82C so as to be displaceable.
- the cylindrical body 84 positioned on the first pressing member 14 side has a small diameter portion 84A on the second pressing member 16 side, and the cylindrical body 86 positioned on the second pressing member 16 side is A cylindrical hole 86A is provided on the pressing member 14 side.
- the small diameter portion 84A is fitted in the cylindrical hole 86A so that the cylindrical bodies 84 and 86 can be relatively displaced along the rotation axis 18.
- the outer peripheral surface 82C of the intermediate member 82 and the cylindrical bodies 84 and 86 are sealed by O-ring seals 88 and 90, respectively.
- the cylindrical body 84 and the cylindrical body 8486 are sealed with an O-ring seal 92.
- the cylindrical bodies 84 and 86 cooperate with the intermediate member 82 to form a piston-cylinder device 66 having a cylinder chamber 64 extending annularly around the intermediate member 82, and the cylinder chamber 64 is the intermediate member 82.
- the outer peripheral surface 82C communicates with a radial passage 72 extending in the radial direction.
- Other points of this embodiment are the same as those of the third embodiment described above.
- the piston-cylinder device 66 is configured to connect both the first pressing member 14 and the second pressing member 16 to the disk portion 20A and the sub disk 22 respectively. Against each other. These pressing forces correspond to the pressure in the cylinder chamber 64, and hence the master cylinder pressure, and therefore correspond to the braking operation amount of the driver.
- the force transmission mechanism 46 is not provided, the rotational torque received by the first pressing member 14 and the second pressing member 16 from the disk portion 20A and the sub disk 22 respectively is along the rotation axis 18.
- the pressing force is not increased by being converted into the force.
- reaction forces received by the first pressing member 14 and the second pressing member 16 from the disk portion 20A and the sub disk 22 are transmitted to the other pressing member via the piston-cylinder device 66, respectively.
- the same effects as in the first embodiment are obtained except that the pressing force is not increased by the wedge action of the force transmission mechanism 46. Obtainable. Since the pressing force can be increased by the transmission of the reaction force performed through the piston-cylinder device 66, the braking force is higher than that of a conventional brake device in which the pressing force is not increased by the reaction force. Can be generated.
- FIG. 9 is a partial cross-sectional view showing a fifth embodiment of the friction brake device according to the present invention configured as an electromagnetic vehicle brake device, cut along a cut surface passing through the rotation axis
- FIG. FIG. 11 is a partial front view of the fifth embodiment as viewed from the right side of FIG. 12, and FIG. 11 is an enlarged partial sectional view taken along line XI-XI of FIG. 9 is a cross-sectional view taken along the line IX-IX in FIG. 9 to 11, the same members as those shown in FIGS. 1 and 2 are denoted by the same reference numerals as those shown in these drawings.
- an intermediate member 102 extending annularly around the rotation axis 18 is disposed between the first pressing member 14 and the second pressing member 16. Yes.
- the intermediate member 102 is rigidly connected to the sleeve portion 28A of the wheel support member 28 by the key 36 at the inner peripheral portion 102X.
- the intermediate member 102 has a cylindrical outer surface 102 ⁇ / b> A aligned with the rotation axis 18, the first pressing member 14 can be relatively rotated by the cylindrical outer surface 102 ⁇ / b> A, and is relatively along the rotation axis 18. It is movably supported. Further, the intermediate member 102 is spaced from the second pressing member 16 in a direction along the rotation axis 18.
- the intermediate member 102 has an annular plate-like portion 102Y in a region radially outward from the outer surface 102A.
- the annular plate-like portion 102Y is evenly distributed in the circumferential direction by a partition 104A.
- 16 arc holes 104 spaced apart from each other are provided.
- Each arc hole 104 extends along the rotation axis 18 through the annular plate-like portion 102 ⁇ / b> Y, and extends in an arc around the rotation axis 18.
- a radially inner surface and a radially outer surface of the circular arc hole 104 have a cylindrical shape extending along the rotation axis 18.
- a first wedge member 96 is disposed adjacent to the first pressing member 14, and a second wedge member 98 is disposed adjacent to the second pressing member 16.
- the wedge members 96 and 98 extend in an arc shape around the rotation axis 18 and are fitted into the corresponding arc holes 104.
- the circumferential lengths of the wedge members 96 and 98 are shorter than the circumferential length of the arc hole 104.
- the radius of the cylindrical outer surface of each wedge member is slightly smaller than the radius of the cylindrical inner surface of the arc hole 104, and the radius of the cylindrical inner surface of each wedge member is the radius of the cylindrical outer surface of the arc hole 104. Slightly larger than.
- the wedge members 96 and 98 protrude from the intermediate member 102 along the rotation axis 18 toward the first pressing member 14 and the second pressing member 16, respectively.
- the front ends of the wedge members 96 and 98 are slightly tapered, and are fitted in recesses 14G and 16G provided on the side surfaces of the first pressing member 14 and the second pressing member 16 and extending in the circumferential direction, respectively. Yes.
- the recesses 14G and 16G are sized and shaped to accept the tips of the wedge members 96 and 98 with little play. *
- the recesses 14G and 16G are respectively provided with shallow stopper portions 14GS and 16GS at circumferential positions corresponding to the partition walls 104A.
- the stopper portions 14GS and 16GS divide the recesses 14G and 16G into a plurality of regions in the circumferential direction, respectively.
- the depressions 14G and 16G are formed so that the wedge members 96 and 98 are displaced from the distal ends of the wedge members 96 and 98 even when the wedge members 96 and 98 are displaced relative to the first pressing member 14 and the second pressing member 16 along the rotation axis 18.
- the portion has a depth that does not escape from the recesses 14G and 16G.
- the wedge members 96 and 98 can be rotationally displaced around the rotational axis 18 relative to the intermediate member 102, but the rotational axis relative to the first pressing member 14 and the second pressing member 16. 18 and the wedge members 96 and 98 can be linearly displaced along the rotation axis 18 relative to the intermediate member 102, and the first pressing member 14 and the second pressing member. 16 can be linearly displaced along the rotation axis 18 relative to the rotation axis 18.
- the wedge members 96 and 98 are located at the standard positions shown in FIG. 11, and the first pressing member 14 and the second pressing member 14 respectively. It is not pressed against the member 16. Therefore, the first pressing member 14 and the second pressing member 16 do not frictionally engage with the disk portion 20A and the sub-rotor 22, respectively.
- the wedge members 96 and 98 cooperate with the arc hole 104 and the partition wall 104A between them, and thereby the force transmission mechanism in the first and second embodiments.
- the force transmission mechanism 106 which functions similarly to 46 is formed. Therefore, as in the first and second embodiments, the force transmission mechanism 106 increases the pressing force of the first pressing member 14 and the second pressing member 16 against the disk portion 20A and the sub-rotor 22, respectively. .
- the other points of the fifth embodiment are configured in the same manner as in the first embodiment.
- the partition 104A is a part of the intermediate member 102 that cannot rotate around the rotation axis 18, the wedge members 96 and 98 on the right side of the partition 104A freely move to the left as viewed in FIG. I can't. Therefore, a part of the rotational torque is converted into a force for pressing the second wedge member 98 against the second pressing member 16 and the sub-rotor 22 by the wedge action by the cooperation of the side surfaces 96B and 98B.
- the friction engagement portion 16 ⁇ / b> A of the second pressing member 16 is frictionally engaged with the sub-rotor 22. Accordingly, a braking force is generated by the friction engagement between the first friction engagement portion 14A and the disk portion 20A and the friction engagement between the friction engagement portion 16A and the sub-rotor 22.
- reaction force received when the first wedge member 96 presses the disk portion 20 ⁇ / b> A via the first pressing member 14 is transmitted to the wedge member 98.
- reaction force received when the second wedge member 98 presses the sub-rotor 22 via the second pressing member 16 is transmitted to the wedge member 96. Therefore, as in the case of the first and second embodiments, the reaction force can be effectively used to increase the pressing force, and a special member that supports the reaction force is not necessary.
- first wedge member 96 located on the left side of the partition wall 104A also receives a moving force to the left, but the movement is blocked by the partition wall 104A located on the left side thereof. Therefore, the first wedge member 96 cannot transmit the rotational torque to the corresponding second wedge member 98, and the force that presses the second wedge member 98 against the second pressing member 16 and the sub-rotor 22. Can not occur.
- the same operation can be obtained even in the situation where the disk portion 20A and the sub-rotor 22 move to the right as viewed in FIG. That is, except that the left and right directions are opposite, the wedge members 96 and 98 on the left side of the partition wall 104A are located on the right side of the partition wall 104A in a situation where the disk portion 20A and the sub-rotor 22 move to the left as viewed in FIG. It functions in the same way as some wedge members 96, 98.
- the force transmission mechanism 106 including the wedge members 96 and 98 functions in the same manner as the force transmission mechanism 46 in the first and second embodiments described above. Therefore, according to the fifth embodiment, it is possible to obtain the same operational effects as in the first and second embodiments.
- the plurality of wedge members 96, 98 are arranged in a circumferentially spaced state, and the regions pressed by the wedge members 96, 98 are also spaced apart from each other in the circumferential direction. Yes. However, the wedge members 96 and 98 do not directly frictionally engage the disk portion 20A and the subrotor 22, but press the first pressing member 14 and the second pressing member 16 against the disk portion 20A and the subrotor 22, respectively.
- the first pressing member 14 and the second pressing member 16 always frictionally engage with the disk portion 20A and the sub-rotor 22 around the entire rotation axis 18. . Accordingly, it is possible to effectively reduce the fear of abnormal wear of the friction engagement portion, brake vibration, brake squeal, and the like.
- both the first pressing member 14 and the intermediate member 102 are rigidly connected to the sleeve portion 28A of the wheel support member 28 by the key 36.
- the stopper portion 16GS is provided and the circumferential displacement of the second wedge member 98 is limited by the stopper portion, one of the first pressing member 14 and the intermediate member 102 is around the rotation axis 18. It may be rotatable. Further, when both the first pressing member 14 and the intermediate member 102 cannot rotate around the rotation axis 18, the stopper portion 16GS may be omitted.
- the friction engagement portions 14A and 16A extend around the rotation axis 18 at the same radial position around the rotation axis 18 over the entire circumference. ing. Accordingly, the reaction force caused by the friction engagement portions and the friction engagement members 54 and 60 being pressed by the pressing members 14 and 16 can be effectively transmitted to the other pressing member.
- 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, and the pressing member 14 and 16 are accommodated in the sealed space 44. Therefore, the possibility that muddy water and dust may enter the brake device 10 can be reduced, and thereby the durability of the brake device 10 can be improved. Moreover, the necessity of a cover etc. which suppress that muddy water and dust penetrate
- the sealed space 44 is filled with a lubricant. Therefore, the engaging portion of the ball 38, each friction contact portion, and the like can be lubricated with the lubricant. Therefore, the force transmission mechanisms 46 and 106 can be operated smoothly, and the pressing of the friction engagement portions 14A and the like by the pressing members 14 and 16 can be performed satisfactorily. In addition, abnormal wear at each friction contact portion can be suppressed, heat generation due to friction and brake squeal can be suppressed, and the temperature rise of the brake pad can be suppressed by cooling the lubricant with a lubricant.
- the friction engagement portions 14A and 16A pressed against the friction surfaces 20S and 22S of the disk portion 20A and the sub disk 22 are formed integrally with the pressing members 14 and 16, respectively. Yes. Therefore, the number of parts is reduced and the structure is simplified as compared with the case where the friction engagement members pressed against the friction surfaces 20S and 22S of the disk portion 20A and the sub disk 22 are separate from the pressing members 14 and 16. Can be made.
- 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 20B has a cylindrical shape extending around the rotation axis 18 over the entire circumference, and the rigidity of the cylindrical portion 20B is higher than the rigidity of the disk portion 20A and the sub-rotor 22.
- the amount by which the disk part 20A and the sub-rotor 22 are deformed away from each other when the brake device 10 is operated is reduced. be able to. Therefore, the braking action of the brake device 10 can be improved as compared with the case where the magnitude relationship of the stiffness is reversed.
- the cylindrical portion 20B is integrated with the disc portion 20A, and the cylindrical portion 20B and the disc portion 20A form the main rotor 20 to which the rim portion of the wheel is connected. Therefore, the rigidity of the brake rotor 12 is increased and the wheel portion of the wheel is increased as compared with the case where the cylindrical portion 20B forms a part of the sub-rotor 22 and the cylindrical portion 20B is connected to the substantially disk-shaped main rotor 20.
- the mounting strength of the brake device 10 to the rim portion can be increased.
- the brake device 10 can be applied to a by-wire type brake device, and according to the second to fourth embodiments, the brake device 10 is a hydraulic brake. It can be applied to the device.
- the first pressing member 14 can rotate around the rotation axis 18, and the second pressing member 16 can rotate around the rotation axis 18. Cannot rotate.
- both the first and second pressing members are rotatable around the rotation axis 18 and are more than a predetermined amount of the first and second pressing members. May be prevented by a stationary member.
- FIG. 12 is an explanatory view in which the main part of the brake device is viewed in the radial direction in order to show the principle of increasing the pressing force in the friction brake device of the present invention provided with the force transmission mechanism.
- reference numerals 110 and 112 denote a brake device and a brake rotor, respectively, which rotate around the rotation axis 118 as indicated by arrows.
- the brake rotor 112 has a first disk 112A and a second disk 112B that are spaced apart from each other along the rotational axis 118.
- a first pressing member 114A and a second pressing member 114B are arranged between the disks 112A and 112B.
- a first friction engagement member 116A is disposed between the first disk 112A and the first pressing member 114A, and the friction engagement member 116A is supported by the pressing member 114A.
- a second friction engagement member 116B is disposed between the second disk 112B and the second pressing member 114B, and the friction engagement member 116B is supported by the pressing member 114B.
- the first pressing member 114 ⁇ / b> A and the second pressing member 114 ⁇ / b> B are spaced apart from each other in the direction along the rotation axis 118, and incline in the same direction with respect to the virtual plane 115 perpendicular to the rotation axis 118 and extend parallel to each other.
- the existing inclined surfaces 114AS and 114BS are provided. The inclined surfaces 114AS and 114BS may be in contact with each other even during non-braking.
- a first stationary member 118A and a second stationary member 118B are disposed at positions spaced apart in the rotational direction around the rotation axis 118 from the first pressing member 114A and the second pressing member 114B, respectively. .
- the stationary members 118A and 118B may be in contact with the first pressing member 114A and the second pressing member 114B during non-braking.
- a first urging unit 120A and a second urging unit 120B are provided inside the first pressing member 114A and the second pressing member 114B. During braking, one of the first urging unit 120A and the second urging unit 120B applies the first pressing member 114A and the second pressing member 114B to the first disk 112A and the second disk 112B, respectively. It has come to force.
- the urging units 120A and 120B are not operated, and the friction engagement members 116A and 116B do not make frictional contact with the disks 112A and 112B, respectively. Does not occur. Further, the pressing members 114 ⁇ / b> A and 114 ⁇ / b> B do not give or receive rotational torque around the rotation axis 118 or give or receive force in the direction along the rotation axis 118.
- one of the urging units 120A and 120B is operated.
- the urging unit 120A is actuated, the first pressing member 114A is urged toward the first disk 112A, whereby the friction engagement member 116A is pressed against the disk 112A by the pressing member 114A.
- the frictional engagement member 116A is frictionally engaged with the disk 112A, rotational torque due to the frictional force between them acts on the frictional engagement member 116A and the pressing member 114A, and the pressing member 114A is displaced to the right as viewed in FIG. And engages with the pressing member 114B.
- the pressing member 114A drives the pressing member 114B in the direction in which the rotational torque acts, and the pressing member 114B contacts the stationary member 118B.
- the pressing members 114A and 114B are prevented from further rotation by the stationary member 118B, and thereby a braking force is generated by the frictional force between the frictional engagement member 116A and the disk 112A.
- the rotational torque is decomposed into a force around the rotational axis 118 and a force along the rotational axis 118. Since the force in the direction along the rotation axis 118 acts in a direction to separate the pressing members 114A and 114B from each other, the pressing member 114B presses the friction engagement member 116B against the disk 112B and frictionally engages them. Therefore, a braking force is also generated by the frictional force between the frictional engagement member 116B and the disk 112B.
- the pressing members 114A and 114B and the stationary members 118A and 118B work together to function as a force transmission mechanism.
- the second urging unit 120B When the brake rotor 112 rotates in the direction opposite to the direction of the arrow, the second urging unit 120B is activated, and the second pressing member 114B is urged against the second disk 112B, As a result, the friction member 116B is pressed against the disk 112B.
- the biasing unit that is operated according to the rotation direction of the brake rotor 112 is determined so that the rotational torque received by the pressing member when the friction engaging member frictionally engages the disk is transmitted to the other pressing member. Is done.
- any urging unit may be operated regardless of the rotation direction.
- stationary members corresponding to the stationary members 118A and 118B are provided on both sides in the circumferential direction of the pressing member 114A or 114B on which the urging unit is operated.
- 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 extending on both sides of the curved portion, respectively. 16ZB, 14ZC, and 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 side surfaces 96B and 98B of the wedge members 96 and 98 are such that the inclination angle with respect to the imaginary plane 40 gradually decreases as the trapezoidal shape moves from the upper base to the lower base. May be curved.
- the rolling element when a rolling element such as the ball 38 is interposed between the cam surfaces of the first and second pressing members, You may curve so that only an inclination angle may become small gradually as it leaves
- the rolling element may be a cylindrical roller or a tapered roller.
- the rotational torque follows the rotation axis 18.
- the component of the force resolved in the direction can be gradually increased. Therefore, the brake characteristic of the brake device can be changed to a progressive brake characteristic.
- the cam surfaces 14Z and 16Z have the curved portions 14ZA and 16ZA, respectively.
- the cam surfaces 14Z and 16Z may include only the inclined portions 14ZB, 16ZB, 14ZC, and 16ZC. Good.
- the region where the inclination angle with respect to the virtual plane 40 is 0 is a position where the inclined portions 14ZB, 16ZB and 14ZC, 16ZC intersect.
- the first and second friction engagement members are the first press member 14 and the second press member 16 as the friction engagement portions 14A and 16A, respectively.
- the first wedge member 96 and the second wedge member 98 are integrally formed.
- at least one of the first and second friction engagement members may be a member different from the corresponding pressing member or wedge member.
- the friction engagement portions 14A and 16A have the same size. However, they may have different sizes and diameters.
- the cylindrical portion 20B is formed integrally with the disk 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 form a sealed space 44 in cooperation with the rotary shaft 17, the wheel support member 28, and the seal member 42.
- the sealed space may not be formed.
- the first pressing member 14, the second pressing member 16, and the friction engagement member 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 disc portion 20A by the electromagnetic force generated by the solenoid 34.
- the means for urging the pressing member may be modified so as to be a hydraulic type similar to the second embodiment described above, 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.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
Description
従来の摩擦ブレーキ装置に於いては、一対の摩擦部材は、ブレーキロータの全周のうちのごく限られた周方向の範囲においてしか延在しておらず、一対の摩擦部材が押圧する領域及び摩擦接触する領域は、ブレーキロータの全周のごく一部でしかない。そのため、摩擦ブレーキ装置の作動時には、一対の摩擦部材の押圧力による圧縮荷重が作用する領域が、ブレーキロータの回転に伴って周方向へ周期的に移動する。
〔課題を解決するための手段及び発明の効果〕
図1は、電磁式の車両用ブレーキ装置として構成された本発明による摩擦ブレーキ装置の第一の実施形態を回転軸線を通る切断面にて切断して示す部分断面図、図2は、第一の実施形態を図1の右方より見た部分正面図、図3は、図2のIII-IIIに沿う部分断面図である。なお、図1は図2のI-Iに沿う断面図である。
図5は、油圧式の車両用ブレーキ装置として構成された本発明による摩擦ブレーキ装置の第二の実施形態を、回転軸線を通る切断面にて切断して示す部分断面図、図6は、第二の実施形態を図5の右方より見た部分正面図である。なお、図5は、図6のV-Vに沿う断面図である。また、図5及び図6において、図1及び図2に示された部材と同一の部材には図1及び図2において付された符号と同一の符号が付されている。
図7は、油圧式の車両用ブレーキ装置として構成された本発明による摩擦ブレーキ装置の第三の実施形態を、回転軸線を通る切断面にて切断して示す部分断面図である。なお、図7において、図5及び図6に示された部材と同一の部材にはこれらの図において付された符号と同一の符号が付されている。
図8は、油圧式の車両用ブレーキ装置として構成された本発明による摩擦ブレーキ装置の第四の実施形態を、回転軸線を通る切断面にて切断して示す部分断面図である。なお、図8において、図5ないし図7に示された部材と同一の部材にはこれらの図において付された符号と同一の符号が付されている。
図9は、電磁式の車両用ブレーキ装置として構成された本発明による摩擦ブレーキ装置の第五の実施形態を、回転軸線を通る切断面にて切断して示す部分断面図、図10は、第五の実施形態を図12の右方より見た部分正面図、図11は図10のXI-XIに沿う拡大部分断面図である。なお、図9は、図10のIX-IXに沿う断面図である。また、図9ないし図11において、図1及び図2に示された部材と同一の部材には、これらの図において付された符号と同一の符号が付されている。
Claims (9)
- 回転軸線に沿って互いに隔置された状態にて前記回転軸線の周りに円環状に延在する第一及び第二のディスク部と、前記第一及び第二のディスク部の外周部を一体に接続する接続部とを有するブレーキロータと、
前記第一及び第二のディスク部の間にて前記回転軸線の周りに円環状に延在する第一及び第二の摩擦部材であって、静止部材により前記回転軸線に沿って前記第一及び第二のディスク部に対し相対的に変位可能に、かつ、前記回転軸線の周りの回転が制限されるよう、支持された第一及び第二の摩擦部材と、
前記第一及び第二の摩擦部材の間に配置された押圧装置であって、前記第一及び第二のディスク部に対しそれぞれ前記第一及び第二の摩擦部材を押圧すると共に、一方の摩擦部材が一方のディスク部より受ける反力を他方の摩擦部材を介して他方のディスク部へ伝達する押圧装置と、
を有する摩擦ブレーキ装置。 - 前記押圧装置は、前記回転軸線の周り周方向に互いに隔置された複数の位置において前記第一及び第二の摩擦部材の押圧及び前記反力の伝達を行うことを特徴とする請求項1に記載の摩擦ブレーキ装置。
- 前記第一の摩擦部材は、前記静止部材により前記回転軸線の周りに前記第二の摩擦部材に対し相対的に回転可能に支持され、前記第二の摩擦部材は、前記静止部材により前記回転軸線の周りに回転不能に支持されており、
前記押圧装置は、少なくとも前記第一の摩擦部材を前記第一のディスク部に対し押圧する力を制御する押圧力制御機構と、前記回転軸線の周りに互いに隔置された状態にて配置され、前記第一及び第二の摩擦部材の間にて力を伝達する複数の力伝達機構とを含み、前記力伝達機構は、前記第一及び第二の摩擦部材の間にて前記回転軸線の周りの回転トルクを伝達し、前記第一及び第二の摩擦部材が前記回転軸線の周りに相対回転変位せしめられることにより発生するくさび作用を利用して回転トルクを前記回転軸線に沿って前記第一及び第二の摩擦部材を離間させる方向の力に変換すると共に、各摩擦部材が受ける反力を第一及び第二の摩擦部材の間に相互に伝達することを特徴とする請求項2に記載の摩擦ブレーキ装置。 - 前記押圧力制御機構は、前記第一の摩擦部材により支持され前記回転軸線の周りに円環状に延在するソレノイドを含み、前記ソレノイドが電気的に付勢されることにより発生する電磁力により前記第一の摩擦部材を前記第一のディスク部に対し押圧する力を制御することを特徴とする請求項3に記載の摩擦ブレーキ装置。
- 前記押圧力制御機構は、前記第二の摩擦部材により支持され前記回転軸線の周りに円環状に延在するピストン-シリンダ装置を含み、前記ピストン-シリンダ装置はシリンダ室と先端にて前記第一の摩擦部材に係合するピストンとを有し、前記シリンダ室内の圧力が増減されることにより前記第一及び第二の摩擦部材をそれぞれ前記第一及び第二のディスク部に対し押圧する力を制御することを特徴とする請求項3に記載の摩擦ブレーキ装置。
- 前記押圧装置は、前記回転軸線の周りの全周において前記第一及び第二の摩擦部材の押圧及び前記反力の伝達を行うことを特徴とする請求項1に記載の摩擦ブレーキ装置。
- 前記押圧装置は、前記第一及び第二の摩擦部材の一方により支持され前記回転軸線の周りに円環状に延在するピストン-シリンダ装置を含み、前記ピストン-シリンダ装置はシリンダ室と先端にて前記第一及び第二の摩擦部材の他方に係合するピストンとを有し、前記シリンダ室内の圧力が増減されることにより前記第一及び第二の摩擦部材をそれぞれ前記第一及び第二のディスク部に対し押圧することを特徴とする請求項6に記載の摩擦ブレーキ装置。
- 前記第一及び第二の摩擦部材がそれぞれ前記第一及び第二のディスク部と摩擦接触する領域の径方向の範囲は同一であることを特徴とする請求項1ないし7の何れか一つに記載の摩擦ブレーキ装置。
- 前記力伝達機構は、それぞれ前記第一及び第二の摩擦部材に設けられ互いに対向する第一及び第二の対向面を有し、
前記第一及び第二の対向面は前記回転軸線に垂直な仮想平面に対し同一の方向に傾斜する領域を有し、
前記第一及び第二の対向面の共働により、前記第一及び第二の摩擦部材の間にて前記回転軸線の周りの回転トルクを伝達し、回転トルクを前記回転軸線に沿って前記第一及び第二の摩擦部材を離間させる方向の力に変換し、各摩擦部材が受ける反力を第一及び第二の摩擦部材の間に相互に伝達する、
ことを特徴とする請求項3ないし5の何れか一つに記載の摩擦ブレーキ装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014511266A JP5846299B2 (ja) | 2012-04-20 | 2013-04-19 | 摩擦ブレーキ装置 |
US14/395,693 US20150129382A1 (en) | 2012-04-20 | 2013-04-19 | Friction brake device |
CN201380020824.9A CN104246270B (zh) | 2012-04-20 | 2013-04-19 | 摩擦制动装置 |
EP13778483.1A EP2840278A4 (en) | 2012-04-20 | 2013-04-19 | FRICTION BRAKE DEVICE |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012097111 | 2012-04-20 | ||
JP2012-097111 | 2012-04-20 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013157646A1 true WO2013157646A1 (ja) | 2013-10-24 |
Family
ID=49383592
Family Applications (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/061681 WO2013157644A1 (ja) | 2012-04-20 | 2013-04-19 | 摩擦ブレーキ装置 |
PCT/JP2013/061682 WO2013157645A1 (ja) | 2012-04-20 | 2013-04-19 | 摩擦ブレーキ装置 |
PCT/JP2013/061683 WO2013157646A1 (ja) | 2012-04-20 | 2013-04-19 | 摩擦ブレーキ装置 |
Family Applications Before (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/061681 WO2013157644A1 (ja) | 2012-04-20 | 2013-04-19 | 摩擦ブレーキ装置 |
PCT/JP2013/061682 WO2013157645A1 (ja) | 2012-04-20 | 2013-04-19 | 摩擦ブレーキ装置 |
Country Status (5)
Country | Link |
---|---|
US (3) | US20150114767A1 (ja) |
EP (3) | EP2840278A4 (ja) |
JP (3) | JP5831628B2 (ja) |
CN (3) | CN104246268A (ja) |
WO (3) | WO2013157644A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2835556A4 (en) * | 2012-04-07 | 2016-01-13 | Toyota Motor Co Ltd | FRICTION BRAKE DEVICE |
EP2835554A4 (en) * | 2012-04-07 | 2016-01-20 | Toyota Motor Co Ltd | FRICTION BRAKE DEVICE |
EP2835555A4 (en) * | 2012-04-07 | 2016-01-20 | Toyota Motor Co Ltd | FRICTION BRAKE DEVICE |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017213184A1 (ja) * | 2016-06-07 | 2017-12-14 | 株式会社アドヴィックス | ブレーキディスク |
EP3604844A1 (de) * | 2018-08-03 | 2020-02-05 | Ondal Medical Systems GmbH | Lageranordnung |
DE102018219752A1 (de) * | 2018-11-19 | 2020-05-20 | Mando Corporation | Bremsanordnung |
DE102019103831A1 (de) * | 2019-02-15 | 2020-08-20 | Bayerische Motoren Werke Aktiengesellschaft | Aktoreinheit für eine formschlüssige, schaltbare Kupplung oder eine Bremse und formschlüssige, schaltbare Kupplung oder Bremse für einen Kraftfahrzeugantriebsstrang |
US10883552B2 (en) | 2019-04-10 | 2021-01-05 | Warner Electric Technology Llc | Rotational coupling device with flux conducting bearing shield |
DE112020003109T5 (de) * | 2019-06-27 | 2022-05-05 | Alps Alpine Co., Ltd. | Betätigungsvorrichtung |
JP7136058B2 (ja) * | 2019-10-08 | 2022-09-13 | トヨタ自動車株式会社 | 電磁ブレーキ装置 |
CN111976666B (zh) * | 2020-09-01 | 2021-11-16 | 安徽斯瓦克汽车配件有限公司 | 一种摩擦式刹车装置 |
CN115126805A (zh) * | 2022-05-26 | 2022-09-30 | 华为电动技术有限公司 | 磨损补偿机构、盘式制动器和车辆 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1005382A (en) * | 1961-07-04 | 1965-09-22 | Automotive Prod Co Ltd | Improvements in and relating to disc brakes |
DE2633460A1 (de) * | 1976-07-24 | 1978-01-26 | Klaue Hermann | Verstaerkungsfreie vollbelagscheibenbremse, insbesondere fuer kraftfahrzeuge |
DE4105358A1 (de) * | 1991-02-21 | 1992-11-05 | Klaue Hermann | Elektrisch zugespannte vollbelagscheibenbremse, insbesondere fuer kraftfahrzeuge |
JPH08121509A (ja) | 1994-10-24 | 1996-05-14 | Toyota Motor Corp | ディスクブレーキ装置 |
JP2000502783A (ja) * | 1996-01-10 | 2000-03-07 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | 特に自動車用の、液圧作動式のフルライニングディスクブレーキ |
JP2004225902A (ja) | 2003-01-23 | 2004-08-12 | Robert Bosch Gmbh | 機械的な自己倍力作用を備えたディスクブレーキ |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1696879A (en) * | 1927-05-25 | 1928-12-25 | Tobias Weber | Brake for vehicles |
US2649941A (en) * | 1948-10-29 | 1953-08-25 | Doebeli Albert | Electromagnetically actuated friction coupling with servo-action |
US3570640A (en) * | 1968-09-18 | 1971-03-16 | Stewart Warner Corp | Clutch bearing assembly |
DE2343004A1 (de) * | 1972-11-17 | 1974-05-30 | Hermann Dr-Ing Klaue | Vollbelagsscheibenbremse, insbesondere fuer kraftfahrzeuge |
US4139081A (en) * | 1969-12-02 | 1979-02-13 | Hermann Klaue | Disk brake assembly for vehicle wheels |
US3752267A (en) * | 1971-12-07 | 1973-08-14 | Us Navy | Disc brake mechanism |
DE2747466C2 (de) * | 1977-10-22 | 1983-11-03 | Karl Ernst Brinkmann Industrieverwaltung, 4924 Barntrup | Nachstelleinrichtung zur Veränderung des maximal möglichen Abstandes zwischen Magnetgehäuse und Ankerscheibe bei einer Elektromagnet-Bremse |
JPS5533955A (en) * | 1978-08-31 | 1980-03-10 | Daikin Mfg Co Ltd | Brake device |
US4337855A (en) * | 1980-05-07 | 1982-07-06 | General Motors Corporation | Multiple armature ring and spring mounting arrangement for electromagnetic friction-type clutches and brakes |
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 |
US5103941A (en) * | 1991-03-28 | 1992-04-14 | The United States Of America As Represented By The Administrator Of The National Aeronautics & Space Administration | Roller locking brake |
IN190089B (ja) * | 1996-03-01 | 2003-06-07 | Eaton Corp | |
US6082504A (en) * | 1998-09-25 | 2000-07-04 | Eaton Corporation | Friction brake device utilizing dual ball ramp devices |
JP3738812B2 (ja) * | 2000-01-18 | 2006-01-25 | 株式会社Tbk | ブレーキライニング摩耗検出装置 |
FR2817218B1 (fr) * | 2000-11-28 | 2003-01-10 | Bosch Gmbh Robert | Cylindre de frein a disque avec mecanisme de frein de parc |
US6715589B2 (en) * | 2001-02-09 | 2004-04-06 | Meritor Heavy Vehicle Systems, Llc | Self-servoing disc brake rotor |
JP2006177532A (ja) * | 2004-12-24 | 2006-07-06 | Hitachi Ltd | ディスクブレーキ |
JP2007064433A (ja) * | 2005-09-01 | 2007-03-15 | Advics:Kk | ディスクブレーキ装置 |
DE102006022388A1 (de) * | 2006-05-12 | 2007-11-15 | Robert Bosch Gmbh | Betriebs- und Feststellbremse |
KR100897942B1 (ko) * | 2007-09-17 | 2009-05-18 | 현대모비스 주식회사 | 주차 제동력 고정 타입 단일 모터 전자 웨지 브레이크시스템 |
CN101550974B (zh) * | 2008-04-03 | 2011-05-04 | 北京停易制动器有限公司 | 气压柔性鼓式制动器 |
KR101098144B1 (ko) * | 2008-12-11 | 2011-12-26 | 현대모비스 주식회사 | 안전 제동 기능을 갖춘 제동 장치 |
-
2013
- 2013-04-19 US US14/395,642 patent/US20150114767A1/en not_active Abandoned
- 2013-04-19 WO PCT/JP2013/061681 patent/WO2013157644A1/ja active Application Filing
- 2013-04-19 JP JP2014511265A patent/JP5831628B2/ja active Active
- 2013-04-19 EP EP13778483.1A patent/EP2840278A4/en not_active Withdrawn
- 2013-04-19 EP EP13778816.2A patent/EP2840279A4/en not_active Withdrawn
- 2013-04-19 JP JP2014511266A patent/JP5846299B2/ja active Active
- 2013-04-19 CN CN201380020810.7A patent/CN104246268A/zh active Pending
- 2013-04-19 WO PCT/JP2013/061682 patent/WO2013157645A1/ja active Application Filing
- 2013-04-19 US US14/395,693 patent/US20150129382A1/en not_active Abandoned
- 2013-04-19 EP EP13777658.9A patent/EP2840277A4/en not_active Withdrawn
- 2013-04-19 WO PCT/JP2013/061683 patent/WO2013157646A1/ja active Application Filing
- 2013-04-19 US US14/395,647 patent/US20150075921A1/en not_active Abandoned
- 2013-04-19 CN CN201380020813.0A patent/CN104246269B/zh not_active Expired - Fee Related
- 2013-04-19 JP JP2014511264A patent/JP5831627B2/ja active Active
- 2013-04-19 CN CN201380020824.9A patent/CN104246270B/zh not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1005382A (en) * | 1961-07-04 | 1965-09-22 | Automotive Prod Co Ltd | Improvements in and relating to disc brakes |
DE2633460A1 (de) * | 1976-07-24 | 1978-01-26 | Klaue Hermann | Verstaerkungsfreie vollbelagscheibenbremse, insbesondere fuer kraftfahrzeuge |
DE4105358A1 (de) * | 1991-02-21 | 1992-11-05 | Klaue Hermann | Elektrisch zugespannte vollbelagscheibenbremse, insbesondere fuer kraftfahrzeuge |
JPH08121509A (ja) | 1994-10-24 | 1996-05-14 | Toyota Motor Corp | ディスクブレーキ装置 |
JP2000502783A (ja) * | 1996-01-10 | 2000-03-07 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | 特に自動車用の、液圧作動式のフルライニングディスクブレーキ |
JP2004225902A (ja) | 2003-01-23 | 2004-08-12 | Robert Bosch Gmbh | 機械的な自己倍力作用を備えたディスクブレーキ |
Non-Patent Citations (1)
Title |
---|
See also references of EP2840278A4 * |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2835556A4 (en) * | 2012-04-07 | 2016-01-13 | Toyota Motor Co Ltd | FRICTION BRAKE DEVICE |
EP2835554A4 (en) * | 2012-04-07 | 2016-01-20 | Toyota Motor Co Ltd | FRICTION BRAKE DEVICE |
EP2835555A4 (en) * | 2012-04-07 | 2016-01-20 | Toyota Motor Co Ltd | FRICTION BRAKE DEVICE |
US9534649B2 (en) | 2012-04-07 | 2017-01-03 | Toyota Jidosha Kabushiki Kaisha | Friction brake device |
US9605720B2 (en) | 2012-04-07 | 2017-03-28 | Toyota Jidosha Kabushiki Kaisha | Friction brake device |
Also Published As
Publication number | Publication date |
---|---|
JP5831628B2 (ja) | 2015-12-09 |
EP2840277A1 (en) | 2015-02-25 |
JP5831627B2 (ja) | 2015-12-09 |
WO2013157644A1 (ja) | 2013-10-24 |
US20150075921A1 (en) | 2015-03-19 |
US20150114767A1 (en) | 2015-04-30 |
CN104246268A (zh) | 2014-12-24 |
EP2840279A1 (en) | 2015-02-25 |
WO2013157645A1 (ja) | 2013-10-24 |
CN104246270B (zh) | 2016-10-12 |
EP2840277A4 (en) | 2016-06-08 |
EP2840279A4 (en) | 2016-06-15 |
EP2840278A4 (en) | 2016-06-15 |
JPWO2013157644A1 (ja) | 2015-12-21 |
EP2840278A1 (en) | 2015-02-25 |
JP5846299B2 (ja) | 2016-01-20 |
CN104246269B (zh) | 2016-11-02 |
JPWO2013157645A1 (ja) | 2015-12-21 |
US20150129382A1 (en) | 2015-05-14 |
CN104246270A (zh) | 2014-12-24 |
JPWO2013157646A1 (ja) | 2015-12-21 |
CN104246269A (zh) | 2014-12-24 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5846299B2 (ja) | 摩擦ブレーキ装置 | |
US5012901A (en) | Self-energizing disc brakes | |
JP5513914B2 (ja) | 電動式パーキング機構付ディスクブレーキ装置 | |
JP5754547B2 (ja) | 摩擦ブレーキ装置 | |
JP7063195B2 (ja) | 摩擦ブレーキ、車載装置 | |
JP5754549B2 (ja) | 摩擦ブレーキ装置 | |
JP6160696B2 (ja) | 摩擦ブレーキ装置 | |
JP5754548B2 (ja) | 摩擦ブレーキ装置 | |
JP5780276B2 (ja) | 摩擦ブレーキ装置 | |
WO2013150657A1 (ja) | 摩擦ブレーキ装置 | |
US7341134B2 (en) | Clutch and brake unit | |
JP4798147B2 (ja) | ブレーキ構造 | |
JP2003056611A (ja) | ディスクブレーキ装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 13778483 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2014511266 Country of ref document: JP Kind code of ref document: A |
|
REEP | Request for entry into the european phase |
Ref document number: 2013778483 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2013778483 Country of ref document: EP |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14395693 Country of ref document: US |