WO2017069234A1 - Frein de véhicules - Google Patents

Frein de véhicules Download PDF

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Publication number
WO2017069234A1
WO2017069234A1 PCT/JP2016/081247 JP2016081247W WO2017069234A1 WO 2017069234 A1 WO2017069234 A1 WO 2017069234A1 JP 2016081247 W JP2016081247 W JP 2016081247W WO 2017069234 A1 WO2017069234 A1 WO 2017069234A1
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WO
WIPO (PCT)
Prior art keywords
linear motion
brake
elastic member
rotating member
gear
Prior art date
Application number
PCT/JP2016/081247
Other languages
English (en)
Japanese (ja)
Inventor
悠貴郎 玉田
崇 近田
陽成 佐々木
明大 岩田
善隆 石丸
Original Assignee
株式会社アドヴィックス
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2016195045A external-priority patent/JP6361715B2/ja
Application filed by 株式会社アドヴィックス filed Critical 株式会社アドヴィックス
Priority to DE112016004838.6T priority Critical patent/DE112016004838B4/de
Priority to CN201680056329.7A priority patent/CN108138880B/zh
Publication of WO2017069234A1 publication Critical patent/WO2017069234A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • 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
    • F16D51/46—Self-tightening brakes with pivoted brake shoes, i.e. the braked member increases the braking action
    • F16D51/48—Self-tightening brakes with pivoted brake shoes, i.e. the braked member increases the braking action with two linked or directly-interacting brake shoes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/22—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for pressing members apart, e.g. for drum brakes

Definitions

  • This disclosure relates to a vehicle brake.
  • Patent Document 1 a vehicle brake that obtains a braking state by converting the rotation of a motor into a linear motion of a cable in a motion conversion mechanism and moving a brake shoe with the linearly moving cable.
  • the disc spring is compressed between the rotating member of the motion conversion mechanism and the housing, so that the rotational load of the motor is increased.
  • the control device can detect, for example, that the linear motion member and the cable are at a predetermined position, for example, the boundary position of the movable range, by the drive current corresponding to the rotational load of the motor.
  • one of the objects of the present invention is to obtain a vehicular brake with less inconvenience, for example, having a new configuration relating to an elastic member.
  • the vehicle brake according to the present disclosure includes, for example, an operation member that moves a braking member to brake a wheel, a motor, a rotation member that is rotated by the motor, and a linear motion that accompanies the rotation of the rotation member.
  • the vehicle brake has a configuration in which the first elastic member is elastically compressed between the rotating member and the linear motion member. Therefore, for example, a housing is used to reduce the degree of freedom in layout of parts including other parts due to the restriction of the position of the first elastic member or to increase the rigidity for receiving the compression reaction force of the first elastic member. It is possible to avoid a disadvantageous phenomenon caused by the configuration in which the first elastic member is compressed between the rotating member and the housing, such as locally increasing the thickness of the first member.
  • the first elastic member is provided so as to surround the linear motion member.
  • the linearity member and the first elastic member can be arranged relatively close to each other, so that the density of parts is likely to increase. Therefore, for example, the vehicle brake device may be configured to be smaller.
  • the first elastic member is a coil spring.
  • the coil spring is easier to handle than the leaf spring, so that the labor and cost of manufacturing the vehicle brake are easily reduced.
  • the vehicle brake includes, for example, a housing that houses at least the rotating member and the first elastic member, a thrust surface provided on the housing or a member supported by the housing, and the rotating member. A pressing member that presses against the thrust surface.
  • the pressing member is a helical gear that meshes with the rotating member and presses the rotating member against the thrust surface.
  • the pressing member is a second elastic member provided separately from the first elastic member.
  • the pressing member can be realized by a relatively simple configuration having a helical gear or a second elastic member.
  • the vehicle brake is, for example, between a first end portion of the first elastic member and a second end portion provided on the rotating member and supporting the first elastic member.
  • a sliding member is provided.
  • the vehicle brake slides with at least one of the first end of the first elastic member and the second end facing the first elastic member with the other, for example.
  • a sliding portion and a facing portion which is located radially outward of the sliding portion and faces the other with a gap are provided.
  • FIG. 1 is an exemplary and schematic rear view of a vehicle brake according to an embodiment from the rear of the vehicle.
  • FIG. 2 is an exemplary schematic side view of the vehicle brake according to the embodiment from the outside in the vehicle width direction.
  • FIG. 3 is an exemplary schematic side view of the operation of the braking member by the vehicle brake moving mechanism of the embodiment, and is a diagram in a non-braking state.
  • FIG. 4 is an exemplary and schematic side view of the operation of the braking member by the vehicle brake moving mechanism of the embodiment, and is a diagram in a braking state.
  • FIG. 5 is an exemplary and schematic cross-sectional view of the drive mechanism included in the vehicle brake of the first embodiment, and is a view in a non-braking state.
  • FIG. 6 is an exemplary schematic sectional view of a drive mechanism included in the vehicle brake according to the first embodiment, and is a diagram in a braking state.
  • 7 is a sectional view taken along line VII-VII in FIG.
  • FIG. 8 is an exemplary schematic sectional view of a drive mechanism included in the vehicle brake of the second embodiment.
  • FIG. 9 is an exemplary and schematic cross-sectional view of a drive mechanism included in a vehicle brake according to a modification of the first embodiment.
  • FIG. 10 is an exemplary and schematic cross-sectional view of a drive mechanism included in the vehicle brake of the third embodiment, and is a diagram in a non-braking state.
  • FIG. 11 is an enlarged view of a part of FIG. FIG.
  • FIG. 12 is an exemplary schematic cross-sectional view of a part of a drive mechanism included in a vehicle brake according to a modification of the third embodiment.
  • FIG. 13 is an exemplary schematic cross-sectional view of a part of a drive mechanism included in a vehicle brake according to a modified example different from FIG. 12 of the third embodiment.
  • FIG. 14 is an exemplary schematic cross-sectional view of a part of a drive mechanism included in a vehicle brake according to a modified example different from FIGS. 12 and 13 of the third embodiment.
  • FIG. 15 is an exemplary schematic cross-sectional view of a part of a drive mechanism included in a vehicle brake according to a modified example different from FIGS. 12 to 14 of the third embodiment.
  • FIG. 12 is an exemplary schematic cross-sectional view of a part of a drive mechanism included in a vehicle brake according to a modified example different from FIGS. 12 to 14 of the third embodiment.
  • FIG. 16 is an exemplary schematic cross-sectional view of a part of a drive mechanism included in a vehicle brake according to a modified example different from FIGS. 12 to 15 of the third embodiment.
  • FIG. 17 is an exemplary schematic graph showing the correlation between R and the relative value Tl / Tt.
  • FIG. 18 is an exemplary schematic graph showing the correlation between ⁇ e and the relative value Tl / Tt.
  • the front in the vehicle front-rear direction is indicated by an arrow X
  • the outer side in the vehicle width direction (axle direction) is indicated by an arrow Y
  • the upper side in the vehicle vertical direction is indicated by an arrow Z.
  • the brake device 2 which is an example of a vehicle brake is applied to the left rear wheel (non-drive wheel) will be exemplified, but the present invention can be similarly applied to other wheels. It is.
  • FIG. 1 is a rear view of the brake device 2 from the rear of the vehicle.
  • FIG. 2 is a side view of the brake device 2 from the outside in the vehicle width direction.
  • FIG. 3 is a side view showing the operation of the brake shoe 3 (braking member) by the moving mechanism 8 of the brake device 2 and is a view in a non-braking state.
  • FIG. 4 is a side view showing the operation of the brake shoe 3 by the moving mechanism 8 of the brake device 2 and is a diagram in a braking state.
  • the brake device 2 is accommodated inside the peripheral wall 1 a of the cylindrical wheel 1.
  • the brake device 2 is a so-called drum brake.
  • the brake device 2 includes two brake shoes 3 that are separated from each other in the front-rear direction.
  • the two brake shoes 3 extend in an arc shape along the inner peripheral surface 4 a of the cylindrical drum 4.
  • the drum 4 rotates integrally with the wheel 1 around the rotation center C along the vehicle width direction (Y direction).
  • the brake device 2 moves the two brake shoes 3 so as to contact the inner peripheral surface 4 a of the cylindrical drum 4.
  • the brake shoe 3 is an example of a braking member.
  • the brake device 2 includes a wheel cylinder 51 (see FIG. 2) that operates by hydraulic pressure, and a motor 120 (see FIG. 5) that operates by energization as actuators that move the brake shoes 3.
  • a wheel cylinder 51 (see FIG. 2) that operates by hydraulic pressure
  • a motor 120 (see FIG. 5) that operates by energization as actuators that move the brake shoes 3.
  • Each of the wheel cylinder 51 and the motor 120 can move the two brake shoes 3.
  • the wheel cylinder 51 is used, for example, for braking while traveling, and the motor 120 is used, for example, for braking during parking. That is, the brake device 2 is an example of an electric parking brake.
  • the motor 120 may be used for braking during traveling.
  • the brake device 2 includes a disc-shaped back plate 6 as shown in FIGS.
  • the back plate 6 is provided in a posture intersecting with the rotation center C. That is, the back plate 6 extends substantially along the direction intersecting the rotation center C, specifically, substantially along the direction orthogonal to the rotation center C.
  • the components of the brake device 2 are provided on both the outer side and the inner side of the back plate 6 in the vehicle width direction.
  • the back plate 6 supports each component of the brake device 2 directly or indirectly. That is, the back plate 6 is an example of a support member.
  • the back plate 6 is connected to a connection member (not shown) with the vehicle body.
  • the connection member is, for example, a part of the suspension (for example, an arm, a link, an attachment member, etc.).
  • the opening 6b provided in the back plate 6 shown in FIG. 2 is used for coupling with the connection member.
  • the brake device 2 can be used for both driving wheels and non-driving wheels.
  • an axle shaft (not shown) passes through an opening 6c provided in the back plate 6 shown in FIG.
  • the wheel cylinder 51 and the brake shoe 3 shown in FIG. 2 are arranged on the outer side of the back plate 6 in the vehicle width direction.
  • the brake shoe 3 is movably supported on the back plate 6.
  • the lower end 3a of the brake shoe 3 is supported by the back plate 6 (see FIG. 2) so as to be rotatable around the rotation center C11.
  • the rotation center C11 is substantially parallel to the rotation center C of the wheel 1.
  • the wheel cylinder 51 is supported by the upper end portion of the back plate 6.
  • the wheel cylinder 51 has two movable parts (pistons) (not shown) that can project in the vehicle front-rear direction (left-right direction in FIG. 2).
  • the wheel cylinder 51 causes the two movable parts to protrude in response to the pressurization.
  • the two projecting movable parts push the upper end 3b of the brake shoe 3, respectively.
  • the two brake shoes 3 rotate around the rotation center C11 (see FIGS. 3 and 4) and move so that the upper end parts 3b are separated from each other in the vehicle front-rear direction.
  • the two brake shoes 3 move outward in the radial direction of the rotation center C of the wheel 1.
  • a belt-like lining 31 along the cylindrical surface is provided on the outer periphery of each brake shoe 3. Therefore, the lining 31 and the inner peripheral surface 4a of the drum 4 come into contact with each other as shown in FIG.
  • the brake device 2 includes a return member 32.
  • the return member 32 moves from the position where the two brake shoes 3 come into contact with the inner peripheral surface 4a of the drum 4 (braking position Pb, see FIG. 4).
  • the drum 4 is moved to a position (non-braking position Pn, initial position, see FIG. 3) that does not contact the inner peripheral surface 4a of the drum 4.
  • the return member 32 is an elastic member such as a coil spring, for example, and gives each brake shoe 3 a force in a direction approaching the other brake shoe 3, that is, a force in a direction away from the inner peripheral surface 4 a of the drum 4. .
  • the brake device 2 includes a moving mechanism 8 shown in FIGS.
  • the moving mechanism 8 moves the two brake shoes 3 from the non-braking position Pn to the braking position Pb based on the operation of the driving mechanism 100 including the motor 120 (see FIG. 5).
  • the moving mechanism 8 is provided outside the back plate 6 in the vehicle width direction.
  • the moving mechanism 8 includes a lever 81, a cable 82, and a strut 83.
  • the lever 81 is located between one of the two brake shoes 3, for example, the left brake shoe 3 ⁇ / b> L in FIGS. 3 and 4, and the back plate 6. It is provided so as to overlap in the axial direction.
  • the lever 81 is supported by the brake shoe 3L so as to be rotatable around the rotation center C12.
  • the rotation center C12 is located at the end of the brake shoe 3L on the side away from the rotation center C11 (upper side in FIGS. 3 and 4), and is substantially parallel to the rotation center C11.
  • the cable 82 moves the lower end portion 81a of the lever 81 on the side farther from the rotation center C12, for example, in a direction approaching the right brake shoe 3R in FIGS.
  • the cable 82 moves substantially along the back plate 6.
  • the strut 83 is interposed between the lever 81 and the brake shoe 3R different from the brake shoe 3L on which the lever 81 is supported, and stretches between the lever 81 and the other brake shoe 3R.
  • the connection position P1 between the lever 81 and the strut 83 is set between the rotation center C12 and the connection position P2 between the cable 82 and the lever 81.
  • the cable 82 is an example of an operating member that moves the brake shoe 3.
  • connection position P2 between the cable 82 and the lever 81 corresponds to the power point
  • the rotation center C12 corresponds to the fulcrum
  • the connection position P1 between the lever 81 and the strut 83 corresponds to the action point.
  • the brake shoe 3R is in contact with the inner peripheral surface 4a and the lever 81 moves to the right in FIG. 4, that is, in the direction in which the strut 83 pushes the brake shoe 3R (arrow b)
  • the strut 83 is stretched.
  • the lever 81 rotates in the direction opposite to the direction in which the lever 81 moves, that is, counterclockwise in FIGS.
  • connection position P1 with the strut 83 serves as a fulcrum.
  • the brake shoe 3L rotates around the rotation center C11 from the non-braking position Pn (FIG. 3) and moves to the braking position Pb (FIG. 4) in contact with the inner peripheral surface 4a of the drum 4.
  • the brake shoes 3L and 3R are both moved from the non-braking position Pn (FIG. 3) to the braking position Pb (FIG. 4) by the operation of the moving mechanism 8.
  • the connection position P1 between the lever 81 and the strut 83 serves as a fulcrum.
  • the amount of movement of the brake shoes 3L, 3R is very small, for example, 1 mm or less.
  • FIG. 5 is a cross-sectional view of the drive mechanism 100 in a non-braking state.
  • FIG. 6 is a cross-sectional view of the driving mechanism 100 in a braking state.
  • the drive mechanism 100 shown in FIGS. 1, 5 and 6 moves the two brake shoes 3 from the non-braking position Pn to the braking position Pb via the moving mechanism 8 described above.
  • the drive mechanism 100 is positioned inward in the vehicle width direction of the back plate 6 and is fixed to the back plate 6.
  • the cable 82 shown in FIGS. 2 to 4 passes through an opening (not shown) provided in the back plate 6.
  • the drive mechanism 100 includes a housing 110, a motor 120, a speed reduction mechanism 130, and a motion conversion mechanism 140.
  • the housing 110 supports the motor 120, the speed reduction mechanism 130, and the motion conversion mechanism 140.
  • the housing 110 includes a plurality of members. The plurality of members are coupled and integrated by a coupling tool (not shown) such as a screw.
  • a housing chamber R surrounded by a wall 111 is provided in the housing 110.
  • the motor 120, the speed reduction mechanism 130, and the motion conversion mechanism 140 are accommodated in the accommodation chamber R and covered with the wall portion 111.
  • the housing 110 may be referred to as a base, a support member, a casing, or the like.
  • the structure of the housing 110 is not limited to what was illustrated here.
  • the motor 120 is an example of an actuator, and includes a case 121 and a housing component housed in the case 121.
  • the housing components include, for example, a stator, a rotor, a coil, and a magnet (not shown) in addition to the shaft 122.
  • the shaft 122 protrudes from the case 121 in the D1 direction (rightward in FIG. 5) along the first rotation center Ax1 of the motor 120.
  • the motor 120 is driven by driving power based on the control signal, and rotates the shaft 122.
  • the shaft 122 may be referred to as an output shaft.
  • the right side in FIG. 5 is referred to as the front in the D1 direction
  • the left side in FIG. 5 is referred to as the rear in the D1 direction or the opposite direction to the D1 direction.
  • the speed reduction mechanism 130 includes a plurality of gears that are rotatably supported by the housing 110.
  • the plurality of gears are, for example, a first gear 131, a second gear 132, and a third gear 133.
  • Deceleration mechanism 130 can be referred to as a rotation transmission mechanism.
  • the first gear 131 rotates integrally with the shaft 122 of the motor 120.
  • the first gear 131 can be referred to as a drive gear.
  • the second gear 132 rotates around the second rotation center Ax2 parallel to the first rotation center Ax1.
  • the second gear 132 includes an input gear 132a and an output gear 132b.
  • the input gear 132a meshes with the first gear 131.
  • the number of teeth of the input gear 132a is larger than the number of teeth of the first gear 131. Therefore, the second gear 132 is decelerated to a lower rotational speed than the first gear 131.
  • the output gear 132b is located behind the input gear 132a in the direction D1 (leftward in FIG. 5).
  • the second gear 132 can be referred to as an idler gear.
  • the third gear 133 rotates around the third rotation center Ax3 parallel to the first rotation center Ax1.
  • the third gear 133 meshes with the output gear 132b of the second gear 132.
  • the number of teeth of the third gear 133 is larger than the number of teeth of the output gear 132b. Therefore, the third gear 133 is decelerated to a lower rotational speed than the second gear 132.
  • the third gear 133 can be referred to as a driven gear. Note that the configuration of the speed reduction mechanism 130 is not limited to that illustrated here.
  • the speed reduction mechanism 130 may be a rotation transmission mechanism other than a gear mechanism, such as a rotation transmission mechanism using a belt, a pulley, or the like.
  • the motion conversion mechanism 140 includes a rotating member 141 and a linearly moving member 142.
  • the rotating member 141 rotates around the third rotation center Ax3.
  • the rotating member 141 has a small diameter portion 141a and a large diameter portion 141b having a larger outer diameter than the small diameter portion 141a.
  • the small diameter portion 141a is a portion located in the direction opposite to the D1 direction in the rotating member 141, and is configured in a cylindrical shape.
  • the large diameter portion 141b is a portion of the rotating member 141 that is positioned in the D1 direction.
  • the large diameter portion 141b has a bottom wall portion 141b1 and a side wall portion 141b2.
  • the bottom wall portion 141b1 projects in the radial direction from the end portion of the small diameter portion 141a in the D1 direction, and is configured in an annular shape and a plate shape.
  • the side wall 141b2 extends in the direction D1 from the peripheral edge of the bottom wall 141b1, and is configured in a cylindrical shape.
  • the side wall part 141b2 may be referred to as a peripheral wall part or a cylindrical wall part.
  • the large-diameter portion 141b is provided with a concave portion 141b3 that is open toward the D1 direction.
  • the teeth of the third gear 133 are provided on the side wall 141b2 of the large diameter portion 141b. That is, the rotating member 141 is also the third gear 133.
  • the part where the teeth of the third gear 133 are provided is an example of a driven part.
  • the cylindrical portion 112 of the housing 110 is accommodated in the recess 141b3.
  • the thrust bearing 143 is positioned between the end portion 112a of the cylindrical portion 112 in the direction opposite to the D1 direction and the bottom wall portion 141b1.
  • the thrust bearing 143 receives a load in the axial direction of the third rotation center Ax3.
  • the thrust bearing 143 is a thrust roller bearing in the example of FIG. 5, but is not limited to this.
  • the large-diameter portion 141b and the rotating member 141 are rotatably supported by the housing 110 via a thrust bearing 143.
  • the small diameter portion 141 a is accommodated in the first hole 113 a of the housing 110.
  • the cross section of the first hole 113a is substantially circular.
  • the first hole 113a extends along the axial direction of the third rotation center Ax3.
  • the rotating member 141 is provided with a through hole 141c having a circular cross section that penetrates the small diameter portion 141a and the bottom wall portion 141b1.
  • a female screw part 145a is provided in the through hole 141c.
  • the linear motion member 142 extends along the third rotation center Ax3 and penetrates the rotation member 141.
  • the linear motion member 142 includes a rod-like portion 142a and a connecting portion 142b.
  • the rod-like portion 142 a is inserted into the through hole 141 c of the rotating member 141, the concave portion 141 b 3 of the large-diameter portion 141 b of the rotating member 141, and the second hole 113 b provided in the cylindrical portion 112 of the housing 110.
  • the cross section of the second hole 113b is substantially circular.
  • the second hole 113b is positioned forward in the D1 direction with respect to the first hole 113a, and extends along the axial direction of the third rotation center Ax3.
  • the rod-like portion 142a has a substantially circular cross section.
  • the rod-like portion 142 a is provided with a male screw portion 145 b that meshes with the female screw portion 145 a of the rotating member 141.
  • the connecting portion 142b is connected to the end portion 82a of the cable 82 by a connecting member 146. As shown in FIG. 7, the connecting member 146 passes through the end portion 82 a and the connecting portion 142 b of the cable 82.
  • the connecting member 146 is, for example, a pin.
  • FIG. 7 is a sectional view taken along line VII-VII in FIG.
  • a groove 113 e is provided on the inner surface of the second hole 113 b provided in the cylindrical portion 112 of the housing 110.
  • the groove 113e extends with a substantially constant width and depth along the third rotation center Ax3.
  • the groove 113e is provided at two locations across the third rotation center Ax3.
  • the end of the connecting member 146 in the longitudinal direction is inserted into the groove 113e.
  • the circumferential width of the third rotation center Ax3 of the groove 113e is set to be slightly larger than the width of the end of the connecting member 146 in the longitudinal direction.
  • connection member 146 and the circumferential surface of the groove 113e are in contact with each other, so that the rotation of the connection member 146 and thus the linear motion member 142 around the third rotation center Ax3 is limited.
  • the connecting member 146 is movable in the recess 141b3. That is, the connecting member 146 is positioned in the recess 141b3 in a state where the linear motion member 142 is positioned at the braking position Pb.
  • the surface 113d in the D1 direction of the groove 113e shown in FIG. 7 restricts the connecting member 146 from moving in the D1 direction.
  • the surface 113d can be referred to as a stopper or a position limiter.
  • bonds the linear motion member 142 and the cable 82 is not limited to the example of FIG.
  • the rotation of the shaft 122 of the motor 120 is transmitted to the rotating member 141 via the speed reduction mechanism 130, and when the rotating member 141 rotates, the female screw portion 145 a of the rotating member 141 and the male screw portion of the linear motion member 142. Due to the meshing with 145b and the limitation of the rotation of the linear motion member 142 by the housing 110 in the groove 113e, the linear motion member 142 and the non-braking position Pn (FIG. 5) are braked along the axial direction of the third rotational center Ax3. It moves between the position Pb (FIG. 6).
  • the portion of the tubular portion 112 of the housing 110 where the groove 113e is provided is an example of a rotation restricting portion that restricts the rotation of the connecting member 146 and thus the linear motion member 142 around the third rotation center Ax3.
  • the linear motion member 142 is also an example of a guide portion that guides the linear motion member 142 along the axial direction of the third rotation center Ax3.
  • a disc-shaped support member 152 is coupled to the end of the linear motion member 142 at the rear (left side in FIG. 5) in the direction D ⁇ b> 1 by a coupling tool 153 such as a screw. .
  • a coupling tool 153 such as a screw.
  • a coil spring 151 is provided between the support member 152 and the bottom wall portion 141b1 of the large diameter portion 141b.
  • the coil spring 151 is formed in a spiral shape extending along the third rotation center Ax3 so as to surround the small diameter portion 141a and the linear motion member 142.
  • the coil spring 151 is an example of a first elastic member.
  • the coil spring 151 can be referred to as a biasing member or a repulsion member.
  • the elastic member may be an elastic member other than the coil spring, such as an elastomer.
  • the coil spring 151 is sandwiched between the support member 152 integrated with the linear motion member 142 and the bottom wall portion 141b1 of the rotating member 141, and is elastically compressed. Due to the increase in the elastic compression reaction force of the coil spring 151, the force in the normal direction of the thread surface at the female screw portion 145a and the male screw portion 145b increases, so that the frictional resistance torque between the female screw portion 145a and the male screw portion 145b increases. As a result, the load torque of the motor 120 increases.
  • the control device (not shown) of the motor 120 is in a predetermined state in which the forward movement of the linear motion member 142 in the direction D1 is limited by detecting the load torque based on the drive current of the motor 120 or the like. Can be detected. That is, in the present embodiment, the motor rotation load increasing mechanism is configured mainly by the coil spring 151 as an elastic member that applies an elastic reaction force to the rotating member 141 in the axial direction.
  • the rotating member 141 and the linear motion member 142 elastically compress the coil spring 151 as the first elastic member constituting the motor rotation load increasing mechanism. Therefore, according to the present embodiment, for example, the position flexibility of the first elastic member reduces the degree of freedom in the layout of components including other components, or receives the compression reaction force of the first elastic member. Inconvenient events caused by the configuration in which the first elastic member is compressed between the rotating member 141 and the housing 110, such as locally increasing the thickness of the wall portion 111 of the housing 110 in order to increase the rigidity of the housing 110 Can be avoided.
  • the coil spring 151 is provided so as to surround the linear motion member 142, the small diameter portion 141a of the rotating member 141, and the female screw portion 145a. Therefore, according to this embodiment, for example, the linear motion member 142, the small diameter portion 141a, the female screw portion 145a, and the coil spring 151 can be arranged relatively close to each other. Therefore, for example, the density of parts in this portion tends to increase. Therefore, the drive mechanism 100 and hence the brake device 2 are easily reduced in size.
  • the labor and cost of manufacturing the first elastic member, the drive mechanism 100, and consequently the brake device 2 are more likely to be reduced.
  • the drive mechanism 100A of this embodiment shown in FIG. 8 has the same configuration as the drive mechanism 100 of the first embodiment. Therefore, also in this embodiment, the same result based on the same configuration as the first embodiment is obtained.
  • a leaf spring 151A is provided as the first elastic member.
  • the support member 152A is configured in a cup shape and includes a bottom wall portion 152a and a side wall portion 152b.
  • the bottom wall portion 152a is formed in a disc shape, and is coupled to a rear end (left side in FIG. 8) of the linear motion member 142 in the direction D1 by a coupling tool 153 such as a screw.
  • the side wall part 152b is cylindrical and extends in the direction D1 from the peripheral edge part of the bottom wall part 152a.
  • a leaf spring 151A is provided between the end portion in the D1 direction of the side wall portion 152b of the support member 152A and the bottom wall portion 141b1 of the large diameter portion 141b.
  • the side wall 152b may be provided with a slit extending in the direction opposite to the D1 direction from the end in the D1 direction, or an opening such as a through hole.
  • an effect is obtained by the configuration in which the rotating member 141 and the linear motion member 142 elastically compress the elastic member, and the elastic member is compressed between the rotating member 141 and the housing 110.
  • the inconvenient event that has been performed can be avoided.
  • the drive mechanism 100B of the modification shown in FIG. 9 has the same configuration as the drive mechanism 100 of the first embodiment. Therefore, also by this modification, the same result based on the structure similar to the said 1st Embodiment is obtained.
  • the housing 110 includes a wall portion 111 and a wall portion 114.
  • the wall 114 is detachably integrated with the wall 111.
  • the portion including the wall portion 114 can be integrated with the wall portion 111 by a coupling tool such as a screw (not shown), for example.
  • a portion including the wall portion 114 is provided with a male screw portion or a female screw portion (not shown), and is configured to be engaged with and integrated with the female screw portion or the male screw portion provided in the portion including the wall portion 111. Can be done.
  • the portion including the wall portion 111 may be referred to as a first member, a first portion, and a first divided body, and the portion including the wall portion 114 may be referred to as a second member, a second portion, and a second divided body.
  • the support member 152B coupled to the linear motion member 142 is exposed in a state where the portion including the wall portion 114 is separated from the portion including the wall portion 111.
  • the support member 152B may be provided with a fitting hole (not shown) into which a tool, a jig, or the like can be inserted, for example. Therefore, even when the rotating member 141 is locked in an emergency or the like, the operator can directly fix the rotating member 141 by inserting a tool or a jig into the fitting hole provided in the supporting member 152B.
  • the moving member 142 can be moved.
  • the support member 152B may be configured to be turned with fingers.
  • the support member 152B partially protrudes in the radial direction at a plurality of locations in the circumferential direction, and the protruding portion is formed in a groove 113e provided continuously to the wall portion 111 and the wall portion 114 of the housing 110.
  • a guide portion including a support member 152B and a rotation limiting portion are configured. That is, of the wall portion 111 and the wall portion 114 of the housing 110, the portion provided with the groove 113e is an example of a rotation limiting portion that limits the rotation of the support member 152B and thus the linear motion member 142 around the third rotation center Ax3. It is also an example of a guide portion that guides the support member 152B and thus the linear motion member 142 along the axial direction of the third rotation center Ax3.
  • FIG. 10 is a cross-sectional view of the drive mechanism 100C in the non-braking state.
  • the drive mechanism 100C of this embodiment shown in FIG. 10 has the same configuration as the drive mechanism 100 of the first embodiment. Therefore, also in this embodiment, the same result based on the same configuration as the first embodiment is obtained.
  • the configuration of the rotating member 141 is different from that of the above-described embodiment or modification.
  • the rotating member 141 rotates around the third rotation center Ax3.
  • the rotating member 141 includes a small-diameter portion 141a, a flange 141e projecting radially outward from the small-diameter portion 141a, and a peripheral wall 141d extending in the axial direction from the flange 141e.
  • the small diameter portion 141a is configured in a cylindrical shape extending in the D1 direction, and penetrates the flange 141e in the D1 direction.
  • the flange 141e protrudes from the center position in the D1 direction of the small diameter portion 141a in a disk shape in the radial direction of the third rotation center Ax3.
  • the peripheral wall 141d extends in a cylindrical shape in the D1 direction from the outer edge of the flange 141e.
  • the small diameter portion 141a can also be referred to as a hub.
  • the flange 141e functions in the same manner as the large diameter portion 141b or the bottom wall portion 141b1.
  • the teeth of the third gear 133 are provided on the outer periphery of the peripheral wall 141d. That is, the rotating member 141 is also the third gear 133.
  • the surface pressure of the output gear 132b of the third gear 133 and the second gear 132 can be reduced.
  • the part where the teeth of the third gear 133 are provided is an example of a driven part.
  • At least the teeth or all of the first gear 131, the second gear 132, and the third gear 133 can be made of a synthetic resin material. However, the present invention is not limited to this, and at least one of the first gear 131, the second gear 132, and the third gear 133 may be partially or entirely made of a metal material.
  • the small diameter portion 141 a is inserted into a cylindrical radial bearing 144 housed at the tip of the cylindrical portion 112.
  • the small-diameter portion 141a and thus the rotating member 141 are rotatably supported by the housing 110 via a radial bearing 144.
  • the radial bearing 144 is a metal bush in the example of FIG. 5, it is not limited to this.
  • the rod-like portion 142 a is inserted into the first hole 113 a of the housing 110, the through hole 141 c of the rotating member 141, and the second hole 113 b provided in the cylindrical portion 112 of the housing 110.
  • the cross section of the second hole 113b is non-circular.
  • the cross section of the second hole 113b is formed in a long hole shape that is long in the direction orthogonal to the third rotation center Ax3 (in FIG. 5, the vertical direction of the paper surface).
  • the second hole 113b is positioned forward in the D1 direction with respect to the first hole 113a, and extends along the axial direction of the third rotation center Ax3.
  • the rod-like portion 142a has a substantially circular cross section.
  • the rod-like portion 142 a is provided with a male screw portion 145 b that meshes with the female screw portion 145 a of the rotating member 141.
  • the cylindrical portion 112 is provided with a cylindrical inner surface 113c facing the second hole 113b.
  • the cross section of the inner surface 113c has a shape along the long hole cross section of the second hole 113b.
  • the inner surface 113c has two planar guide surfaces 113ca (only one guide surface 113ca is shown in FIG. 10) extending in a direction orthogonal to the third rotation center Ax3.
  • the two guide surfaces 113ca are positioned with a space therebetween, and the linear motion member 142 is positioned between the two guide surfaces 113ca.
  • a protrusion 142c protrudes from the rod-like portion 142a of the linear motion member 142 toward the outer side in the radial direction of the third rotation center Ax3.
  • the outer periphery of the protrusion 142c is formed in a shape along the inner surface 113c.
  • a gap is provided between the protrusion 142c and the inner surface 113c, and grease is provided in the gap.
  • the rotation of the shaft 122 of the motor 120 is transmitted to the rotating member 141 via the speed reduction mechanism 130, and when the rotating member 141 rotates, the female screw portion 145 a of the rotating member 141 and the male screw portion of the linear motion member 142. Due to the meshing with 145b and the limitation of the rotation of the linear motion member 142 by the guide surface 113ca, the linear motion member 142 moves along the axial direction of the third rotation center Ax3 with the non-braking position Pn (FIG. 10) and the braking position (Not shown).
  • FIG. 11 is an enlarged view of a part of FIG.
  • the output gear 132b and the third gear 133 of the second gear 132 are configured as helical gears.
  • the output gear 132b gives an axial force directed forward or rearward in the D1 direction to the third gear 133 according to the rotation direction by means of a helical tooth.
  • the output gear 132b rotates in one rotational direction, thereby giving the rotating member 141 an axial force in the forward direction in the D1 direction.
  • the output gear 132b presses the end surface 141e1 of the flange 141e of the rotating member 141 against the surface 143a of the thrust bearing 143, and the rotating member 141 and the thrust bearing 143 are connected to the rear end of the cylindrical portion 112 in the D1 direction. Press against 112a (end face).
  • the end surface 141e1 can be referred to as a pressed surface.
  • the output gear 132b rotates in the direction opposite to the one rotation direction (the other rotation direction), thereby giving the rotating member 141 a rear axial force in the D1 direction.
  • the output gear 132 b can press the end surface 141 d 1 of the peripheral wall 141 d of the rotating member 141 against the end surface 111 a of the housing 110.
  • the end surface 141d1 can be referred to as a pressed surface or a sliding surface.
  • the direction of the spiral of the output gear 132b is determined by the rotation of the output gear 132b when the linear motion member 142 moves from the braking position Pb (not shown) to the non-braking position Pn shown in FIG. Is set so as to give a forward axial force in the direction D1.
  • the surface 143a of the thrust bearing 143 and the end surface 111a of the housing 110 are examples of thrust surfaces
  • the thrust bearing 143 is an example of a member supported by the housing 110
  • the second gear 132 is
  • the output gear 132b is an example of a helical gear.
  • the output gear 132b presses the rotating member 141 against the surface 143a or the end surface 111a (thrust surface), thereby suppressing the change in the position and posture of the rotating member 141 and thus rotating. Sound and vibration based on changes in the position and orientation of the member 141 are unlikely to occur.
  • an annular and plate-shaped washer 154 is provided between the end surface 151a of the coil spring 151 and the end surface 141e2 of the flange 141e.
  • plating treatment such as molybdenum disulfide treatment, chromium plating treatment, nickel plating treatment, diamond-like carbon (
  • the washer 154 is an example of a sliding member. The principle of starting torque reduction by the friction coefficient will be described later.
  • a wave washer 161 or a spring washer 162 is provided as a pressing member.
  • a wave washer 161 is provided between the end surface 141d1 of the peripheral wall 141d and the end surface 111a of the housing 110, and in the modified example of FIG. 13, the wave washer 161 is a surface 143a of the thrust bearing 143. 14 and the end surface 141e1 of the flange 141e.
  • the spring washer 162 is provided between the surface 143a of the thrust bearing 143 and the end surface 141e1 of the flange 141e.
  • the wave washer 161 applies an axial force forward to the rotating member 141 in the D1 direction.
  • the wave washer 161 elastically presses the end surface 141e1 against the surface 143a of the thrust bearing 143.
  • the wave washer 161 or the spring washer 162 gives the rotating member 141 a rear axial force in the direction D1.
  • the wave washer 161 or the spring washer 162 elastically presses the end surface 141 d 1 against the end surface 111 a of the housing 110.
  • the wave washer 161 or the spring washer 162 is an example of a second elastic member.
  • a spring washer 162 can be provided instead of the wave washer 161.
  • other elastic members such as a cone spring, a coil spring, a leaf spring, and an elastomer (rubber) can be provided as a pressing member.
  • the flange 141e of the rotating member 141 has an end surface 141e2 (support surface) that contacts the end surface 151a of the coil spring 151, and a step surface 141e3 (bottom surface, concave surface) facing the end surface 151a with a gap. ) And are provided.
  • the end surface 151a and the end surface 141e2 slide, but the end surface 151a and the step surface 141e3 do not slide.
  • the end surface 151a is an example of a first end portion
  • the end surface 141e2 is an example of a sliding portion
  • the step surface 141e3 is an example of a facing portion
  • the end surface 141e2 and the step surface 141e3 are It is an example of a 2nd edge part.
  • an end surface 151 a that contacts the end surface 141 e 2 of the flange 141 e and an inclined surface 151 b that faces the end surface 141 e 2 with a gap are provided at the end of the coil spring 151.
  • the end surface 151a and the end surface 141e2 slide, but the inclined surface 151b and the end surface 141e2 do not slide.
  • the end surface 151a is an example of a sliding portion
  • the inclined surface 151b is an example of a facing portion
  • the end surface 151a and the inclined surface 151b are an example of a first end portion
  • the end surface 141e2 is It is an example of a 2nd edge part.
  • the torque Tt required to elastically compress the coil spring 151 by moving the linear motion member 142 forward in the direction D1 toward the non-braking position Pn can be expressed by the following equation (1).
  • F axial force
  • ⁇ s coefficient of friction of the threaded surface of the female threaded portion 145a and male threaded portion 145b
  • ⁇ flank angle of the threaded surface
  • p screw pitch
  • R end surface 151a of the coil spring 151 and the flange 141e
  • ⁇ e the friction coefficient of the contact portion between the end surface 151a and the end surface 141e2 of the coil spring 151.
  • the first term is the friction torque on the thread surface
  • the second term is the fastening torque
  • the third term is the friction torque between the end surface 151a and the end surface 141e2.
  • the torque Tl required for elastically releasing the compression state by the coil spring 151 by moving the linear motion member 142 rearward in the direction D1 from the non-braking position Pn can be expressed by the following equation (2).
  • the sign of the fastening torque in the second term is negative.
  • a predetermined value of torque is detected by the drive current of the motor 120, and the motor 120 is stopped from the point of detection. That is, the torque Tt is a value overrun from a predetermined value of torque. The torque overrun increases as the friction torque decreases. Therefore, the magnitude of the torque Tl required to move the linear motion member 142 backward from the non-braking position Pn in the direction D1 should be evaluated by the relative value Tl / Tt of the torque Tl with respect to the torque Tt (formula (3)). is there.
  • FIG. 17 is a graph showing the correlation between R and the relative value Tl / Tt of equation (3)
  • FIG. 18 shows the correlation between ⁇ e and the relative value Tl / Tt of equation (3). It is a graph to show.
  • Equation (3) the smaller R and ⁇ e, the smaller the relative value Tl / Tt.
  • the stepped surface 141e3 as the facing portion is located radially outward of the end surface 141e2 as the sliding portion
  • the inclined surface 151b as the facing portion is The end face 151a serving as the sliding portion is located radially outward.
  • the torque Tt is reduced.
  • the relative value Tl / Tt of the torque Tl that is, the torque at the start of the motor 120 for starting braking (initially at the start of rotation) and the subsequent torque during rotation can be reduced.
  • an inclined surface may be provided on the flange 141e, or a step surface may be provided on the coil spring 151. Further, both the flange 141e and the coil spring 151 may be provided with facing portions.
  • the brake device 2 is configured as a leading trailing drum brake, but the present invention can also be configured as other types of brake devices. Further, the present invention can be implemented as a configuration corresponding to the other actuator of a brake device having a disc brake by one actuator and a drum brake by another actuator. Moreover, the effect by an elastic member does not presuppose the structure by which the movement of the axial direction of a linear motion member is restrict
  • the configuration in which the operating member that moves the braking member is the cable 82 is exemplified, but the operating member may be other than the cable 82 such as a rod or a lever.
  • the actuating member may move the braking member by pushing instead of pulling.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)
  • Braking Systems And Boosters (AREA)

Abstract

L'invention concerne, par exemple, un frein de véhicules présentant une nouvelle configuration associée à un élément élastique et n'ayant que peu d'inconvénients. Le frein de véhicules est équipé, par exemple : d'un élément d'actionnement qui peut déplacer un élément de freinage de manière à freiner une roue; d'un moteur; d'un élément tournant pouvant être entraîné en rotation par le moteur; d'un élément à déplacement linéaire pouvant se déplacer linéairement en synchronisation avec la rotation de l'élément tournant de façon à déplacer l'élément d'actionnement; et d'un élément élastique disposé entre l'élément tournant et l'élément à déplacement linéaire et pouvant être déformé élastiquement dans la direction de l'axe de l'élément tournant entre l'élément tournant et l'élément à déplacement linéaire consécutivement au déplacement de l'élément à déplacement linéaire dans la direction de l'axe de l'élément tournant.
PCT/JP2016/081247 2015-10-23 2016-10-21 Frein de véhicules WO2017069234A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112016004838.6T DE112016004838B4 (de) 2015-10-23 2016-10-21 Bremse für Fahrzeuge
CN201680056329.7A CN108138880B (zh) 2015-10-23 2016-10-21 车辆用制动器

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2015-209219 2015-10-23
JP2015209219 2015-10-23
JP2016195045A JP6361715B2 (ja) 2015-10-23 2016-09-30 車両用ブレーキ
JP2016-195045 2016-09-30

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Publication number Priority date Publication date Assignee Title
WO2020004524A1 (fr) * 2018-06-29 2020-01-02 株式会社アドヴィックス Dispositif de frein
JP2020008165A (ja) * 2018-06-29 2020-01-16 株式会社アドヴィックス ブレーキ装置
WO2020175190A1 (fr) * 2019-02-25 2020-09-03 株式会社アドヴィックス Dispositif de frein
JPWO2019187362A1 (ja) * 2018-03-30 2021-04-08 日信工業株式会社 電動パーキングブレーキ装置
CN113833780A (zh) * 2021-10-21 2021-12-24 杭州速博雷尔传动机械有限公司 一种高效双制动减速机

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WO2014025010A1 (fr) * 2012-08-09 2014-02-13 曙ブレーキ工業株式会社 Appareil de frein à disque électrique
JP2014226005A (ja) * 2013-05-17 2014-12-04 Ntn株式会社 電動式直動アクチュエータおよび電動式ブレーキ装置
WO2015053333A1 (fr) * 2013-10-08 2015-04-16 曙ブレーキ工業株式会社 Frein à disque
JP2015152044A (ja) * 2014-02-12 2015-08-24 株式会社アドヴィックス 電動駐車ブレーキ

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WO2014025010A1 (fr) * 2012-08-09 2014-02-13 曙ブレーキ工業株式会社 Appareil de frein à disque électrique
JP2014226005A (ja) * 2013-05-17 2014-12-04 Ntn株式会社 電動式直動アクチュエータおよび電動式ブレーキ装置
WO2015053333A1 (fr) * 2013-10-08 2015-04-16 曙ブレーキ工業株式会社 Frein à disque
JP2015152044A (ja) * 2014-02-12 2015-08-24 株式会社アドヴィックス 電動駐車ブレーキ

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Publication number Priority date Publication date Assignee Title
JPWO2019187362A1 (ja) * 2018-03-30 2021-04-08 日信工業株式会社 電動パーキングブレーキ装置
JP7194172B2 (ja) 2018-03-30 2022-12-21 日立Astemo株式会社 電動パーキングブレーキ装置
WO2020004524A1 (fr) * 2018-06-29 2020-01-02 株式会社アドヴィックス Dispositif de frein
JP2020008165A (ja) * 2018-06-29 2020-01-16 株式会社アドヴィックス ブレーキ装置
CN112368488A (zh) * 2018-06-29 2021-02-12 株式会社爱德克斯 制动装置
CN112368488B (zh) * 2018-06-29 2022-06-24 株式会社爱德克斯 制动装置
JP7229810B2 (ja) 2018-06-29 2023-02-28 株式会社アドヴィックス ブレーキ装置
WO2020175190A1 (fr) * 2019-02-25 2020-09-03 株式会社アドヴィックス Dispositif de frein
CN113833780A (zh) * 2021-10-21 2021-12-24 杭州速博雷尔传动机械有限公司 一种高效双制动减速机
CN113833780B (zh) * 2021-10-21 2023-07-25 杭州速博雷尔传动机械有限公司 一种高效双制动减速机

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