WO2014006659A1 - ディスクブレーキ装置 - Google Patents
ディスクブレーキ装置 Download PDFInfo
- Publication number
- WO2014006659A1 WO2014006659A1 PCT/JP2012/004376 JP2012004376W WO2014006659A1 WO 2014006659 A1 WO2014006659 A1 WO 2014006659A1 JP 2012004376 W JP2012004376 W JP 2012004376W WO 2014006659 A1 WO2014006659 A1 WO 2014006659A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- braking surface
- rotor
- shaft member
- electric motor
- disc brake
- Prior art date
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Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/38—Slack adjusters
- F16D65/40—Slack adjusters mechanical
- F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
- F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
- F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
- F16D65/568—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake for synchronous adjustment of actuators arranged in parallel
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- 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
- F16D2121/24—Electric or magnetic using motors
-
- 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
- F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
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- 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
- F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
- F16D2125/28—Cams; Levers with cams
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- 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
-
- 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
- F16D2125/64—Levers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2127/00—Auxiliary mechanisms
- F16D2127/08—Self-amplifying or de-amplifying mechanisms
- F16D2127/10—Self-amplifying or de-amplifying mechanisms having wedging elements
Definitions
- the present invention relates to a disc brake device that is used in a vehicle or the like and generates a braking force by friction.
- Disc brake devices are widely used in vehicles and the like. For example, in response to a depressing operation of a brake pedal, a friction pad is pressed against a rotor that rotates integrally with a wheel to generate a frictional force, thereby braking the rotation of the rotor. Configured.
- a disc brake device a disc brake device of a type in which a friction pad is pressed against a rotor using hydraulic pressure is known.
- This type of disc brake device has a configuration in which a piston is operated by hydraulic pressure, and a friction pad facing the rotor is moved and pressed in a direction perpendicular to the rotor.
- the hydraulically driven disc brake device requires a booster that amplifies the operating force to the brake pedal, and a master cylinder that converts the operating force amplified by the booster to hydraulic pressure. The configuration tends to be complicated.
- the present invention has been made in view of the above-described problems, and an object of the present invention is to provide a disc brake device with an increased degree of freedom in arrangement of an electric motor.
- a disc brake device comprises a rotor having a disc-shaped braking surface that is connected to a rotating body to be braked and rotates, and a support member that rotatably supports the rotating body (for example, a carrier attached to the axle 2) in the embodiment and disposed opposite to the braking surface of the rotor, a caliper attached to the carrier so as to be movable in a direction perpendicular to the braking surface, A friction pad (for example, the inner pad 43 in the embodiment) disposed opposite to the braking surface, and a braking operation mechanism that is attached to the caliper and performs an operation of pressing the friction pad against the braking surface.
- a disc brake device configured, wherein the braking operation mechanism is a base member held by the caliper (for example, in the embodiment) A base plate 35), a slide member (for example, a wedge plate 37 in the embodiment) that is disposed opposite to the base member and holds the friction pad, and the slide member is parallel to the braking surface with respect to the base member and A first motion conversion mechanism (for example, a wedge groove 35a, a roller 36, a wedge groove 37a, a clamping unit 39, and a cage 45 in the embodiment) that moves in a direction perpendicular to the braking surface while sliding in the rotational direction of the rotor;
- An electric motor unit for example, the electric motor 110 in the embodiment
- An electric motor 110 in the embodiment including an output shaft member (for example, the motor output shaft 112 in the embodiment) that outputs a rotational driving force, and a drive shaft that is rotationally driven by the output shaft member A member (for example, the cam drive shaft 170 in the embodiment), and the drive A second motion conversion mechanism (for
- the electric motor unit is attached to the caliper so that the output shaft member is positioned on the outer peripheral side with respect to the drive shaft member, and the rotational driving force of the output shaft member is transmitted to the drive shaft member.
- a driving force transmission mechanism for example, the driving force transmission shaft 130 and the gear unit 140 in the embodiment.
- the driving force transmission mechanism transmits the rotational driving force of the output shaft member to the driving shaft member while allowing an inclination between the axis of the output shaft member and the axis of the driving shaft member.
- a possible configuration is preferred.
- the driving force transmission mechanism has a configuration using gears (for example, the input side spur gear 150 and the output side spur gear 160 in the embodiment).
- the electric motor unit is attached to the caliper so that the output shaft member is positioned on the outer peripheral side with respect to the drive shaft member, and the rotational driving force of the output shaft member is transmitted to the drive shaft member.
- a driving force transmission mechanism is provided.
- the electric motor unit is arranged at a position other than the axis of the drive shaft member to increase the degree of freedom of arrangement of the electric motor unit, and the rotational driving force of the electric motor unit is surely driven by the driving force transmission mechanism. It can be transmitted to the member.
- the driving force transmission mechanism can transmit the rotational driving force while allowing an inclination between the axis of the output shaft member and the axis of the driving shaft member. Since the caliper to which the electric motor unit is attached is slidable with a clearance with respect to the carrier, the axis of the output shaft member and the axis of the drive shaft member may be positioned at an inclination. Even in such a case, the rotational drive force of the output shaft member can be reliably and smoothly transmitted to the drive shaft member while allowing the inclination of the mutual axis lines.
- the driving force transmission mechanism has a configuration using gears.
- the backlash of the gears is made as small as possible, it is possible to configure a driving force transmission mechanism that has a relatively simple configuration and improved driving response.
- FIG. 1 is a perspective view showing a disc brake device according to an embodiment of the present invention.
- FIG. 2 is a cross-sectional view showing a II-II portion in FIG. 1.
- FIGS. 3A and 3B are diagrams showing a carrier, in which FIG. 3A is a front view, FIG. 3B is a plan view, and FIG. 3C is a cross-sectional view taken along line III (c) -III (c) in FIG. .
- omitted omitted
- FIG. 1 It is a perspective view which shows a braking unit (a pad and a shoe plate are included). It is a top view which shows a braking unit (a pad and a shoe plate are included). It is a figure which shows a wedge plate, Comprising: (a) shows a rear view, (b) shows a top view, (c) shows a front view (a shoe plate is added by a two-dot chain line). It is a figure which shows an inner pad and a shoe plate, Comprising: (a) shows a top view, (b) shows a front view, respectively.
- FIG. 1 is a front view of the coupling clip
- FIG. 1 is a front view of the coupling clip
- FIG. 1 shows a front view of the coupling clip
- FIG. 1 shows a side view of the coupling clip
- FIG. 1 shows a side view of the coupling clip
- FIG. 1 shows a side view of the coupling clip
- FIG. 1 shows a bottom view, respectively.
- FIG. 3 is a cross-sectional view showing a portion XIII-XIII in FIG.
- FIG. 4 is a cross-sectional view showing a XIV-XIV portion in FIG. 1.
- FIG. 15 is a diagram illustrating a driving force transmission shaft, where (a) is a plan view, (b) is a cross-sectional view of the portion XV (b) -XV (b) in FIG. Respectively.
- FIG. 17A is a front view of the input side spur gear, and FIG. 16B is a cross-sectional view of the XVI (b) -XVI (b) portion in FIG.
- FIG. 1 shows a state in which a disc brake device 1 as an example to which the present invention is applied is mounted on a vehicle.
- the outer side in the left-right direction of the vehicle is referred to as the outer side
- the inner side in the left-right direction is referred to as the inner side
- the front side of the vehicle is referred to as the forward side
- the rear side of the vehicle is referred to as the reverse side.
- the disc brake device 1 includes a rotor 4 having a braking surface 4 a and a disc shape, and a carrier 5 disposed so as to sandwich the braking surface 4 a of the rotor 4. And a caliper assembly 10 attached to the carrier 5.
- the rotor 4 is connected to a wheel (not shown) to be braked and is rotatably supported by the axle 2.
- a support plate 3 is fixed to the axle 2, and a carrier 5 is fixed to the support plate 3.
- the carrier 5 includes a pair of inner side frame portions 15 positioned on the inner side, an outer side frame portion 18 positioned on the outer side, and a pair of connecting frame portions 21 that connect the frame portions 15 and 18. And a rotor accommodating space 22 penetrating vertically in the center.
- Each of the inner side frame portions 15 includes an inner side rotation direction movement restricting portion 16 standing upward and a flat plate-like inner side radial direction movement restricting portion 17 connected to the lower end portion of the inner side rotation direction movement restricting portion 16. And is configured.
- Each of the inner side rotational direction movement restricting portions 16 is formed with a flat inner side rotational direction movement restricting surface 16a facing each other, and each of the inner side radial direction movement restricting portions 17 has a flat inner side diameter.
- a direction movement restricting surface 17a is formed.
- the outer side frame portion 18 includes a pair of outer side rotation direction movement restricting portions 19 erected upward and a flat plate-like outer side radial direction movement restricting portion 20 connected to the lower end portion of the outer side rotation direction movement restricting portion 19. And is configured.
- Each of the outer side rotational direction movement restricting portions 19 is formed with a flat outer side rotational direction movement restricting surface 19a facing each other, and each of the outer side radial direction movement restricting portions 20 has a flat outer side diameter.
- a direction movement restricting surface 20a is formed.
- the caliper assembly 10 includes a caliper 7 formed by connecting an inner housing 6a and an outer housing 6b, a braking unit 11 disposed in the caliper 7, and a caliper 7
- the outer pad 41 and the inner pad 43 disposed opposite to the braking surface 4 a of the rotor 4, the pair of adjustment units 30 disposed in the caliper 7, and the caliper 7 are disposed inside and outside.
- a cam drive unit 100 is disposed.
- the caliper 7 is attached to the carrier 5 using a slide pin 8 and is slidable in the axial direction of the rotor 4. For this reason, the caliper assembly 10 (the caliper 7 and the brake unit 11, the adjustment unit 30 and the cam drive unit 100 disposed inside and outside the caliper 7) is integrally slidable in the axial direction of the rotor 4.
- the braking unit 11 holds a cam member 27, a base plate 35, a wedge plate 37 disposed to face the base plate 35, a roller 36 formed in a columnar shape, and the roller 36. And a clamping unit 39 (FIGS. 5 to 7) that elastically pulls the wedge plate 37 toward the inner side and clamps the roller 36 between the plates 35 and 37.
- the cam member 27 includes a main body portion 27b in which an involute spline bearing portion 27a is formed and an engagement tooth 27d in which an involute cam-side contact surface 27c is formed.
- the base plate 35 is formed in a substantially flat plate shape as shown in FIGS. 6 and 7, and a wedge groove 35a having a V-shaped cross-sectional view for fitting and holding the roller 36 on a surface facing the wedge plate 37. Is formed.
- the wedge plate 37 is formed in a substantially flat plate shape as shown in FIGS. 4 and 7, and a wedge groove 37a having a V-shaped cross-sectional view for fitting and holding the roller 36 on a surface facing the base plate 35. Is formed.
- an insertion space 37b penetrating in the axial direction of the rotor 4 is formed in the central portion of the wedge plate 37, and the cam member 27 is disposed in the insertion space 37b.
- An escape portion 37c is formed in the upper portion of the insertion space 37b so that the main body portion 27b of the cam member 27 and the wedge plate 37 do not interfere when the wedge plate 37 is slid in the rotational direction with respect to the base plate 35.
- a rack-side contact surface 37d that contacts the cam-side contact surface 27c of the cam member 27 is formed below the insertion space 37b.
- the wedge plate 37 includes a pair of coupling protrusions 53 that are substantially rectangular in cross-section and project toward the outer side, and a pair of plate holding portions 51 that are formed with pin receiving grooves 52 extending vertically. Prepare.
- the cage 45 includes a base portion 45a formed in a substantially flat plate shape, a pair of roller holding portions 45b for accommodating and holding the roller 36, and a guide opening portion 45c formed in the center portion. And is configured.
- the clamping unit 39 includes a base member 39a attached to the wedge plate 37, a support member 39b attached to the base member 39a, a compression spring 39c, and a spring retainer 39d. Is done.
- the base member 39a is fitted in the guide opening 45c of the cage 45, and is slidable in the front-rear direction of the vehicle by being guided by the guide opening 45c.
- the assembly structure of the clamping unit 39 will be described. As shown in FIG. 6, first, the base plate 35 is disposed on the inner side of the base member 39a, and the compression spring 39c is inserted through the support member 39b.
- a spring retainer 39d is attached to the tip of the support member 39b, and the compression spring 39c is held in a compressed state and assembled.
- a force toward the inner side is always applied to the wedge plate 37, and the roller 36 is elastically held between the wedge plate 37 (wedge groove 37a) and the base plate 35 (wedge groove 35a).
- the outer pad 41 (also referred to as a friction material) includes a shoe plate 42 on the outer side, as shown in FIG.
- the outer pad 41 is disposed so as to face the outer braking surface 4a of the pair of braking surfaces 4a.
- the inner pad 43 includes a shoe plate 44 on the inner side.
- the inner pad 43 is disposed so as to face the inner brake surface 4a of the pair of brake surfaces 4a.
- what attached the shoe plate to the pad may only be called a pad (friction pad).
- a pair of coupling grooves 44a are formed on the inner side of the shoe plate 44.
- the pair of coupling grooves 44a are substantially rectangular in cross section and extend vertically to fit with the coupling protrusions 53 of the wedge plate 37.
- a pin mounting hole 44b is formed in a portion of the shoe plate 44 adjacent to the coupling groove 44a.
- the coupling pin 70 shown in FIG. 4 is attached to the pin attachment hole 44b.
- the coupling pin 70 is connected to the disc-shaped spring load receiving portion 71, the connecting shaft portion 72 connected to the spring load receiving portion 71, and the connecting shaft portion 72.
- the insertion shaft portion 73 having a diameter larger than that of the connecting shaft portion 72 and the screw portion 74 are configured.
- the coupling pin 70 is attached to the shoe plate 44 by the screw portion 74 being fastened to the pin attachment hole 44 b of the shoe plate 44.
- the coupling clip 60 shown in FIG. 4 is used.
- the coupling clip 60 is formed by using a flat metal material that can be elastically deformed, and has a slit portion 62 so as to be curved.
- a base portion 61, an upper locking portion 63 formed by bending the upper end portion of the base portion 61, and a lower locking portion 64 formed by bending the lower end portion of the base portion 61 are provided.
- FIG. 11A first, the coupling groove 44a of the shoe plate 44 is fitted into the coupling protrusion 53 of the wedge plate 37, the inner pad 43 is slid downward, and the coupling pin 70 of the shoe plate 44 is moved. It is received in the pin receiving groove 52 of the wedge plate 37 (see FIG. 11B).
- FIG. 11B when the coupling clip 60 is inserted and attached to the gap between the spring load receiving portion 71 and the plate holding portion 51 from above, the lower side of the plate holding portion 51 is placed on the lower side. The locking portion 64 is locked and the upper locking portion 63 is locked to the upper end portion of the plate holding portion 51.
- the inner pad 43 When the inner pad 43 is attached to the wedge plate 37 using the coupling clip 60, the inner pad 43 can be elastically pressed against the wedge plate 37 by the spring force of the base portion 61. For this reason, since the inner pad 43 can be moved integrally with the wedge plate 37, the inner pad 43 can be controlled to move in the rotational direction and the radial direction with high accuracy. In addition, generation of drag torque or the like by the inner pad 43 can be suppressed.
- a leaf spring 9a that can be elastically deformed up and down is attached to the upper part of the shoe plate 44, and the retainer plate 9b is pressed so as to press the leaf spring 9a from above. Install. In this way, the inner pad 43 is elastically held so as not to come out of the outer housing 6b by the spring force of the leaf spring 9a.
- the adjustment unit 30 includes a pressing force sensor 31, an adjuster main body 32, an adjuster cylindrical body 33, and an adjustment drive gear 38.
- the pressing force sensor 31 is a sensor that detects a pressing force when the inner pad 43 is pressed against the braking surface 4a.
- the adjuster main body 32 is formed in a columnar shape and includes a spiral main body side screw (not shown) on the outer peripheral surface thereof.
- the adjuster cylindrical body 33 is formed in a substantially cylindrical shape, and includes a cylindrical portion 33a in which a spiral cylindrical side screw (not shown) meshing with the main body side screw is formed on the inner peripheral surface, and the cylindrical portion 33a. And an adjustment driven gear 33b formed at the inner side end.
- the adjuster cylinder 33 is rotatably supported with respect to the inner housing 6a by a bearing 30a (see FIG. 18) provided between the adjuster cylindrical body 33 and the inner housing 6a.
- the adjustment drive gear 38 is rotatably supported by the inner housing 6 a and meshes with the adjustment driven gears 33 b of the pair of adjustment units 30.
- the adjustment unit 30 adjusts the gap so that the gap between the braking surface 4a of the rotor 4 and the inner pad 43 becomes a predetermined interval each time a brake operation is performed.
- the adjustment unit 30 is disposed between the adjustment case 34 and the inner housing 6a.
- the adjustment unit 30 rotates the adjuster cylindrical body 33 by the adjustment drive gear 38 and pushes the adjuster main body 32 to the outer side, thereby bringing the inner pad 43 closer to the braking surface 4 a of the rotor 4 via the braking unit 11.
- the gap can be adjusted.
- the braking unit 11 is provided on the outer side of the adjustment case 34.
- the base plate 35 is placed on the inner side radial direction movement restricting portion 17 of the carrier 5 and is sandwiched and disposed by the inner side rotational direction movement restricting portion 16 of the carrier 5.
- the base plate 35 is provided with a pressing positioning member 80 for positioning by restricting the movement of the base plate 35 in the rotation direction.
- the pressing positioning member 80 is formed using a flat metal material that can be elastically deformed.
- the pressing body 80 is deformed by a deflection amount d, and the plate-like main body 81 is formed.
- the upper locking portion 82 formed by bending the upper end portion of the plate body and the engaging portion 83 formed by bending the center portion in the vertical direction of the plate-like main body portion 81 are configured.
- the cam drive unit 100 includes an electric motor 110 that rotates by receiving power supply, a speed reducer 120 that receives the rotational driving force of the electric motor 110, and an output of the speed reducer 120.
- a driving force transmission shaft 130 connected to the shaft, a gear unit 140 connected to the driving force transmission shaft 130, and a cam driving shaft 170 connected to the output side of the gear unit 140 are configured.
- the electric motor 110 includes a motor main body 111 that generates a rotational driving force upon receiving power supply, and a motor output shaft 112 that outputs the rotational driving force generated by the motor main body 111.
- the electric motor 110 includes a rotation angle sensor 113 (for example, an encoder) that detects the rotation angle of the electric motor 110.
- the electric motor 110 is attached to the outside of the inner housing 6a to ensure the degree of freedom of arrangement of the electric motor 110, and can be adapted to the increase in size of the electric motor 110.
- the reduction gear 120 includes a first input shaft 121 connected to the motor output shaft 112, a first planetary gear unit 122 configured to include a sun gear, a planetary gear, a ring gear, and the like (not shown), and a first planetary gear unit 122. And a second planetary gear unit 124 configured to include a sun gear, a planetary gear, a ring gear, and the like (not shown).
- the rotational driving force of the motor output shaft 112 is first decelerated by the first planetary gear unit 122, and further decelerated by the second planetary gear unit 124 and output.
- An involute serration bearing 154 as shown in FIG.
- 16A is formed on the output shaft (ring gear) of the second planetary gear unit 124.
- the speed reducer 120 configured by connecting two sets of planetary gear units 122 and 124 is illustrated, but a speed reducer having a different configuration (a speed reducer including one set of planetary gear units) is used. May be.
- the driving force transmission shaft 130 includes a cylindrical shaft main body 131 and an output-side involute serration shaft that is formed in the shaft main body 131 and has an arcuate cross section (see FIG. 15B). And an input-side involute serration shaft portion 133 having an arc-shaped cross section (see FIG. 15B).
- the input side involute serration shaft portion 133 meshes with an involute serration bearing portion formed on the output shaft of the second planetary gear unit 124.
- the gear unit 140 includes an input side spur gear 150, an output side spur gear 160 that meshes with the input side spur gear 150, and a gear holding frame 141 that rotatably holds these spur gears 150 and 160.
- the input-side spur gear 150 is formed by penetrating the ring-shaped gear main body 151, a plurality of meshing teeth 152 formed on the peripheral edge of the gear main body 151, and the gear main body 151.
- the shaft insertion portion 153 and an involute serration bearing portion 154 formed on the inner peripheral surface of the shaft insertion portion 153 are configured.
- the output side spur gear 160 includes a ring-shaped gear main body 161, a plurality of meshing teeth 162 that are formed on the peripheral edge of the gear main body 161 and mesh with the meshing teeth 152, and the gear main body.
- a shaft insertion portion (not shown) formed so as to penetrate through 161 and an involute spline bearing portion (not shown) formed on the inner peripheral surface of the shaft insertion portion are configured.
- the gear holding frame 141 rotatably holds the input side spur gear 150 and the output side spur gear 160 in a meshed state.
- the gear holding frame 141 includes a mounting protrusion 142 that protrudes to the outer side.
- an attachment hole 34 a is formed in the adjustment case 34.
- the attachment protrusion 142 is inserted into the attachment hole 34 a, and the gear unit 140 is slidable in the axial direction of the rotor 4 and attached to the adjustment case 34.
- the cam drive shaft 170 includes a cylindrical shaft main body portion 171, an output-side involute spline shaft portion 172 formed on the shaft main body portion 171, and an input-side involute spline shaft portion 173. Configured.
- the input side involute spline shaft portion 173 meshes with the involute spline bearing portion of the output side spur gear 160, and the output side involute spline shaft portion 172 meshes with the involute spline bearing portion 27 a of the cam member 27.
- the cam drive shaft 170 is rotatably supported by the adjustment case 34 via a bearing 179.
- a vehicle equipped with the disc brake device 1 to which the present invention is applied is provided with a brake pedal 92 that is operated by a driver.
- the depression force (brake operating force) of the brake pedal 92 is detected by being converted into an electric signal by the depression force sensor 92a.
- the vehicle is provided with a rotation direction sensor 93 for detecting the rotation direction of the rotor 4 (forward side f or reverse side r).
- the controller 91 that controls the operation of the electric motor 110 receives detection results detected by the pressing force sensor 31, the stepping force sensor 92a, the rotation direction sensor 93, and the rotation angle sensor 113.
- the controller 91 stores the brake operation force detected by the stepping force sensor 92a and the pressing force of the inner pad 43 corresponding to the brake operation force in association with each other.
- step S10 the rotation direction (forward f or reverse r) of the rotor 4 detected by the rotation direction sensor 93 is input to the controller 91.
- step S20 a signal indicating the brake operation force applied to the brake pedal 92 detected by the stepping force sensor 92a is input to the controller 91.
- step S 30 a signal indicating the pressing force of the inner pad 43 detected by the pressing force sensor 31 is input to the controller 91.
- step S40 the controller 91 determines whether or not the rotation direction of the rotor 4 input in step S10 is the forward side f. If the rotation of the rotor 4 is the forward side f, the forward side f A drive signal is output to the electric motor 110 so that the wedge plate 37 is slid and moved toward (step S51). When the electric motor 110 is rotationally driven based on this drive signal, the rotational driving force of the electric motor 110 is decelerated by the speed reducer 120 and then transmitted to the gear unit 140 via the driving force transmission shaft member 130.
- the rotational driving force transmitted to the gear unit 140 is transmitted from the input side spur gear 150 to the output side spur gear 160, and further from the output side spur gear 160 to the cam drive shaft member 170, and according to the rotational drive of the electric motor 110.
- the cam member 27 is rotationally driven.
- the rack-side contact surface 37d of the wedge plate 37 is pressed by the cam-side contact surface 27c of the cam member 27, so that the cam member 27 rotates in the rotation direction (in this case, the forward side f).
- the wedge plate 37 is slid.
- the cam side abutment surface 27c formed in an involute shape is abutted against the rack side abutment surface 37d, and the wedge plate 37 is slid, so that the cam side abutment surface 27c and the rack side abutment are in contact with each other. It is possible to efficiently convert the rotational driving force of the cam member 27 into the sliding movement of the wedge plate 37 while suppressing the slip generated between the surface 37d.
- FIG. 18 shows the members slid to the forward side f as a wedge plate 37f, a shoe plate 44f, and an inner pad 43f.
- FIG. 19 shows an enlarged view of the wedge plate 37f, the shoe plate 44f, and the inner pad 43f that are slid and moved to the forward side f.
- the roller 36 is pressed against the backward slope of the V-shaped wedge groove 37a. Therefore, the wedge plate 37 (the shoe plate 44 and the inner pad 43 integrated with the wedge plate 37) is pushed out to the outer side while sliding to the forward side f along the slope of the slope.
- step S40 if it is determined in step S40 that the rotation direction of the rotor 4 is the reverse side r, a drive signal is output from the controller 91 to the electric motor 110 so as to slide the wedge plate 37 toward the reverse side r.
- Step S52 each member slid to the reverse side r is shown as a wedge plate 37r, a shoe plate 44r, and an inner pad 43r.
- the wedge plate 37 is pushed to the outer side while sliding to the forward side f or the reverse side r according to the rotation angle of the cam member 27, and as a result, the inner pad 43 is pressed against the braking surface 4a. Then, the reaction force from the braking surface 4a acts on the caliper 7 (inner housing 6a) via the inner pad 43, the shoe plate 44, the wedge plate 37, the roller 36, the base plate 35, the adjustment case 34, and the adjustment unit 30. The caliper 7 is pressed toward the inner side.
- the shoe plate 42 and the outer pad 41 are integrally pressed toward the inner side by the outer housing 6b.
- the outer pad 41 is pressed against the braking surface 4a on the outer side, and a braking force can be applied to the braking surface 4a.
- each of the outer pad 41 and the inner pad 43 is pressed against the braking surface 4 a to apply a braking force to the rotor 4.
- the disc brake device 1 is configured such that the pressing force pressing the inner pad 43 against the braking surface 4a is automatically amplified (generates a self-boosting) by the braking unit 11. This configuration will be described with reference to FIG. In the following description, the friction coefficient between the braking surface 4a and the inner pad 43 is assumed to be ⁇ .
- the inner pad 43 is pressed against the braking surface 4a by the pressing force obtained by adding the reaction force F ′ to the original pressing force F, and the frictional force (F + F ′) ⁇ ⁇ corresponding to the pressing force (F + F ′) is the inner pressure. It acts on the pad 43.
- step S60 when the braking force is applied by pressing the outer pad 41 and the inner pad 43 against the braking surface 4a, the pressing force of the inner pad 43 detected by the pressing force sensor 31 is detected in the controller 91. Then, it is determined whether or not the pressing force corresponding to the brake operation force detected by the stepping force sensor 92a is larger.
- step S71 a drive signal is output from the controller 91 to the electric motor 110 so as to weaken the pressing force by moving the wedge plate 37 backward.
- step S72 a drive signal is output from the controller 91 to the electric motor 110 so as to increase the pressing force by moving the wedge plate 37 forward.
- the rotational drive control of the electric motor 110 is performed so that the inner pad 43 is pressed against the braking surface 4a with a pressing force corresponding to the brake operating force applied to the brake pedal 92. .
- the braking force intended by the driver can be applied to the rotor 4 to decelerate the vehicle.
- the disc brake device 1 needs to slide the inner pad 43 in the rotational direction when moving the inner pad 43 in the direction perpendicular to the braking surface 4a.
- the inner pad 43 does not rotate together with the rotor 4 when the inner pad 43 is pressed against the braking surface 4a. Furthermore, it is necessary to regulate the movement of the inner pad 43 in the rotational direction.
- the carrier 5 When the inner pad 43 is pressed against the braking surface 4a, the rotational direction component of the braking force generated between the braking surface 4a and the inner pad 43 is transmitted to the base plate 35 via the wedge plate 37 and the roller 36. Is done. Therefore, as shown in FIGS. 2 and 3, the carrier 5 is provided with a pair of inner side rotational direction movement restricting portions 16, and a base plate 35 is sandwiched between them to restrict the rotational direction component of the braking force to the inner side rotational direction movement restriction. The configuration is such that it is received by the part 16. As shown in FIG. 1, the carrier 5 including the inner side rotational direction movement restricting portion 16 is fixed to the axle 2 via the support plate 3.
- the rotational direction component of the braking force is received by the carrier 5 fixed to the axle 2, and the movement of the inner pad 43 (base plate 35) in the rotational direction can be reliably restricted.
- the base plate 35 located in the vicinity of the inner pad 43 is sandwiched by the inner side rotation direction movement restricting portion 16, the movement of the inner pad 43 in the rotation direction can be effectively restricted.
- the radial component of the rotor 4 is that at least one of the inner pad 43, the shoe plate 44, and the wedge plate 37 is the inner component of the carrier 5.
- the side radial direction movement restricting portion 17 is abutted and received. In this way, both the rotational force and the radial force acting on the inner pad 43 are firmly received by the carrier 5 fixed to the axle 2, so that the disc brake device 1 can be made robust with increased rigidity.
- the wedge plate 37 and the inner pad 43 are allowed to slide in the rotation direction. ing. Therefore, when the inner pad 43 is moved in a direction perpendicular to the braking surface 4a, the braking force can be amplified by the wedge effect by sliding the inner pad 43 in the rotational direction.
- the outer pad 41 is placed on the outer-side radial movement restricting portion 20 in a state where the outer pad 41 is sandwiched between a pair of outer-side rotational direction movement restricting portions 19 provided on the carrier 5 and the movement in the rotational direction is restricted.
- the configuration capable of effectively restricting the movement of the inner pad 43 in the rotation direction when the braking force is applied while allowing the inner pad 43 to be pressed against the braking surface 4a while sliding in the rotation direction. did.
- the disc brake device 1 using the wedge effect, it is important to accurately control the sliding movement of the inner pad 43 in the rotation direction in order to control the pressing force of the inner pad 43 with high accuracy. Since the inner pad 43 is slid and moved with respect to the base plate 35, it is necessary to position the inner pad 43 by restricting the movement of the base plate 35 serving as a reference in the rotational direction. On the other hand, since the disc brake device 1 is assembled by inserting the base plate 35 between the pair of inner side rotation direction movement restricting portions 16, it is necessary to provide a gap (clearance) for absorbing machining errors.
- the reverse side end portion of the base plate 35 and the inner side rotational direction are arranged.
- a press positioning member 80 is vertically inserted and attached in the gap with the movement restricting portion 16.
- the forward end of the base plate 35 is elastically pressed against the inner side rotation direction movement restricting portion 16 by the spring force of the plate-like main body portion 81 constituting the pressing positioning member 80, thereby positioning the base plate 35 in the rotation direction. It can be kept in the state.
- the disc brake device 1 can provide the clearance for absorbing the processing error, and can prevent the drive delay of the wedge plate 37 caused by the clearance, so that the inner pad 43 is controlled as controlled. It is configured to be able to slide and press against the braking surface 4a.
- the clearance is set to a value that can be inserted in a state where the plate-like main body 81 is compressed.
- the spring force of the plate-like main body 81 that constitutes the pressing positioning member 80 will be described with reference to FIG.
- the cam member 27 is driven using the rotational driving force of the electric motor 110, and the spring force of the compression spring 39c that pulls the wedge plate 37 toward the inner side.
- the driving force F 1 ′ against the braking force is applied to the wedge plate 37 to slide the wedge plate 37 forward.
- the reaction force F 1 acts on the cam member 27 toward the reverse side.
- the spring force F 2 required to deform the plate-like body portion 81 is configured to be larger than the reaction force F 1. For this reason, the forward side end of the base plate 35 is elastically pressed against the inner side rotational direction movement restricting part 16 so that no gap is generated between the pair of inner side rotational direction movement restricting parts 16 and the base plate 35. The state positioned in the rotation direction can be maintained.
- the engaging portion 83 is engaged with the backward end portion of the base plate 35, and the press positioning member 80 is moved to the base plate 35. Attached to. For this reason, it is possible to prevent the press positioning member 80 from dropping out from the gap between the base plate 35 and the inner side rotational direction movement restricting portion 16.
- the position where the pressing positioning member 80 receives the reaction force F 1 acting toward the reverse side that is, the reverse side end portion of the base plate 35 and the inner side rotational direction movement restricting portion 16. It is inserted into the gap. For this reason, during reverse travel, the plate-like main body portion 81 may be deformed by the braking force, and a gap may be generated between the pair of inner side rotational direction movement restricting portions 16 and the base plate 35.
- the forward travel which is more frequent than the reverse travel, is prioritized, and the drive delay of the wedge plate 37 during forward travel can be prevented.
- the electric motor 110 is not arranged on the axis of the cam drive shaft 170, but the caliper 7 ( An electric motor 110 is attached to the outer periphery of the inner housing 6a).
- the degree of freedom of arrangement of the electric motor 110 is increased while avoiding interference between the electric motor 110 and the components of the vehicle on which the disc brake device 1 is mounted. be able to.
- the electric motor 110 When the electric motor 110 is attached to the outer periphery of the caliper 7, a mechanism for transmitting the rotational driving force of the motor output shaft 112 to the cam driving shaft 170 is required.
- the caliper 7 to which the electric motor 110 is attached is attached to the carrier 5 via the slide pin 8 and has a clearance for allowing the slide movement.
- the cam drive shaft 170 is positioned on the carrier 5 via the base plate 35. Therefore, the axis of the motor output shaft 112 (the output shaft of the speed reducer 120) and the axis of the cam drive shaft 170 may be tilted.
- the output-side involute serration shaft portion 132 and the input-side involute serration shaft portion 133 constituting the driving force transmission shaft 130 have an arcuate cross section as shown in FIG.
- the driving force transmission shaft 130 maintains the meshing between the shaft portion and the bearing portion while allowing an inclination between the axis of the motor output shaft 112 (the output shaft of the speed reducer 120) and the axis of the cam drive shaft 170.
- the rotational driving force can be transmitted smoothly. Since the gear unit 140 is configured such that the backlash between the meshing tooth 152 of the input side spur gear 150 and the meshing tooth 162 of the output side spur gear 160 is minimized, the rotational driving force of the electric motor 110 is responsive. Good and efficient transmission is possible.
- the cam member 27 and the cam drive shaft 170 are integrally pushed out to the outer side.
- the gear unit 140 that transmits the rotational driving force to the cam drive shaft 170 is in contact with the inner housing 6a and the movement of the rotor 4 in the axial direction is restricted. Therefore, the rotational driving force can be transmitted while allowing the input side involute spline shaft portion 173 of the cam drive shaft 170 and the involute spline bearing portion of the output side spur gear 160 to move in the axial direction of the rotor 4. Is engaged.
- the input side involute spline shaft portion 173 is formed to extend in the axial direction so as to correspond to the adjustment.
- the configuration example in which the pressing force of the inner pad 43 is detected using the pressing force sensor 31 and the rotational driving control of the electric motor 110 is performed by feeding back the pressing force has been described.
- the present invention is not limited to the configuration example.
- the braking torque generated by pressing the inner pad 43 against the braking surface 4a is detected, or the deceleration of the vehicle is detected. You may comprise so that control may be performed.
- the configuration example has been described in which the adjustment drive gear 38 is automatically driven to rotate and the clearance is adjusted according to the clearance between the inner pad 43 and the braking surface 4a. It is not limited to examples. Instead of this configuration, an adjustment electric motor for rotationally driving the adjustment drive gear 38 may be separately provided, and the clearance adjustment may be performed by controlling the rotation drive of the adjustment electric motor.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
Description
2 アクスル(支持部材)
4 ローター
4a 制動面
5 キャリア
7 キャリパ
27 カム部材(第2運動変換機構)
35 ベースプレート(ベース部材)
35a ウェッジ溝(第1運動変換機構)
36 ローラ(第1運動変換機構)
37 ウェッジプレート(スライド部材)
37a ウェッジ溝(第1運動変換機構)
37d ラック側当接面(第2運動変換機構)
39 挟持ユニット(第1運動変換機構)
43 インナーパッド(摩擦パッド)
45 ケージ(第1運動変換機構)
110 電動モータ(電動モータユニット)
112 モータ出力軸(出力軸部材)
130 駆動力伝達軸(駆動力伝達機構)
140 歯車ユニット(駆動力伝達機構)
150 入力側平歯車(歯車)
160 出力側平歯車(歯車)
170 カム駆動軸(駆動軸部材)
Claims (3)
- 制動対象となる回転体に連結されて回転する円盤状の制動面を有したローターと、前記回転体を回転自在に支持する支持部材に取り付けられて前記ローターの制動面に対向して配置されたキャリアと、前記キャリアに前記制動面に垂直な方向へ移動可能に取り付けられたキャリパと、前記ローターの制動面に対向して配置される摩擦パッドと、前記キャリパに取り付けられて前記摩擦パッドを前記制動面に押し付ける作動を行わせる制動作動機構とを有して構成されるディスクブレーキ装置であって、
前記制動作動機構が、
前記キャリパに保持されるベース部材と、
前記ベース部材に対向配置されて前記摩擦パッドを保持するスライド部材と、
前記ベース部材に対して前記スライド部材を前記制動面に平行且つ前記ローターの回転方向にスライド移動させながら前記制動面に垂直な方向に移動させる第1運動変換機構と、
回転駆動力を出力する出力軸部材を備えた電動モータユニットと、
前記出力軸部材により回転駆動される駆動軸部材を備え、前記駆動軸部材が回転駆動されて前記スライド部材を前記制動面に平行且つ前記ローターの回転方向にスライド移動させる第2運動変換機構とを有し、
前記駆動軸部材に対して前記出力軸部材が外周側に位置するように、前記電動モータユニットが前記キャリパに取り付けられており、
前記出力軸部材の回転駆動力を前記駆動軸部材に伝達する駆動力伝達機構を備えたことを特徴とするディスクブレーキ装置。 - 前記駆動力伝達機構が、前記出力軸部材の軸線と前記駆動軸部材の軸線との傾きを許容しつつ、前記出力軸部材の回転駆動力を前記駆動軸部材に伝達可能に構成されたことを特徴とするディスクブレーキ装置。
- 前記駆動力伝達機構が、歯車を用いて構成されたことを特徴とする請求項1または2に記載のディスクブレーキ装置。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201280074464.6A CN104411995A (zh) | 2012-07-05 | 2012-07-05 | 盘式制动装置 |
US14/410,792 US20150136539A1 (en) | 2012-07-05 | 2012-07-05 | Disk brake device |
EP12880711.2A EP2871384A1 (en) | 2012-07-05 | 2012-07-05 | Disc brake device |
KR20157000662A KR20150031273A (ko) | 2012-07-05 | 2012-07-05 | 디스크 브레이크 장치 |
PCT/JP2012/004376 WO2014006659A1 (ja) | 2012-07-05 | 2012-07-05 | ディスクブレーキ装置 |
JP2014523452A JPWO2014006659A1 (ja) | 2012-07-05 | 2012-07-05 | ディスクブレーキ装置 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2012/004376 WO2014006659A1 (ja) | 2012-07-05 | 2012-07-05 | ディスクブレーキ装置 |
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Publication Number | Publication Date |
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WO2014006659A1 true WO2014006659A1 (ja) | 2014-01-09 |
Family
ID=49881458
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2012/004376 WO2014006659A1 (ja) | 2012-07-05 | 2012-07-05 | ディスクブレーキ装置 |
Country Status (6)
Country | Link |
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US (1) | US20150136539A1 (ja) |
EP (1) | EP2871384A1 (ja) |
JP (1) | JPWO2014006659A1 (ja) |
KR (1) | KR20150031273A (ja) |
CN (1) | CN104411995A (ja) |
WO (1) | WO2014006659A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2017137928A (ja) * | 2016-02-03 | 2017-08-10 | Ntn株式会社 | 電動ブレーキ装置 |
Families Citing this family (2)
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CN107816498A (zh) * | 2017-11-17 | 2018-03-20 | 金华职业技术学院 | 一种新型汽车线控制动器 |
CN114876983B (zh) * | 2022-04-26 | 2024-05-17 | 华为电动技术有限公司 | 制动机构、机械制动器、电子机械制动系统及车辆 |
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2012
- 2012-07-05 EP EP12880711.2A patent/EP2871384A1/en not_active Withdrawn
- 2012-07-05 KR KR20157000662A patent/KR20150031273A/ko not_active Application Discontinuation
- 2012-07-05 JP JP2014523452A patent/JPWO2014006659A1/ja active Pending
- 2012-07-05 US US14/410,792 patent/US20150136539A1/en not_active Abandoned
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- 2012-07-05 CN CN201280074464.6A patent/CN104411995A/zh active Pending
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KR20150031273A (ko) | 2015-03-23 |
US20150136539A1 (en) | 2015-05-21 |
JPWO2014006659A1 (ja) | 2016-06-02 |
EP2871384A1 (en) | 2015-05-13 |
CN104411995A (zh) | 2015-03-11 |
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