JPWO2018139163A1 - Disc brake - Google Patents

Abstract

By engaging the protrusions 181 and 182 of the holder 205 with the fixing flange surface 202A of the motor flange 202, the motor 200 is fixed to the holder 205 in the motor axial direction and the motor rotating direction, so that a tool path is secured. Therefore, the degree of freedom in design is not impaired, and the housing in which the motor gear assembly is accommodated, and thus the disc brake can be reduced in size.

Description

  The present invention relates to a disc brake used for braking a vehicle.

  Patent Literature 1 discloses a disc brake having a parking disc brake mechanism that operates during parking brake. In the disc brake, two metal nuts are insert-molded on the motor support portion of the holder, and the motor is attached to the holder by fastening a mounting bolt to each nut via a motor flange.

Japanese Patent Laid-Open No. 2006-125545

  The disc brake of Patent Document 1 needs to determine the layout in consideration of a tool path (space for allowing the tool to pass) when tightening the mounting bolt, and thus has a problem that the housing becomes large.

  The subject of this invention is providing the disc brake reduced in size.

  The present invention includes a motor that generates a rotational motion upon receiving a current, a holder that supports the motor and a speed reduction mechanism that increases the rotational motion from the motor, the holder, the motor, and the speed reduction mechanism. The motor has an uneven portion in the motor radial direction, the holder has a protruding portion protruding in the motor axial direction, the uneven portion of the motor and the protruding portion of the holder And the motor is fixed to the holder in the motor shaft direction and the motor rotation direction.

  According to the present invention, the disc brake can be reduced in size.

It is sectional drawing of the disc brake which concerns on 1st Embodiment. FIG. 2 is an enlarged view of a rotation / linear motion conversion mechanism in the disc brake shown in FIG. 1. It is a disassembled perspective view in the housing of the disc brake concerning a 1st embodiment. It is a disassembled perspective view in the housing of the disc brake concerning a 1st embodiment. It is a top view which shows the inside of the 1st housing of the disc brake which concerns on 1st Embodiment. It is a figure which shows the rubber in the disc brake shown by FIG. 5 alone. It is a perspective view of the motor support structure in the disc brake concerning a 1st embodiment. It is a top view of the motor support structure of the disc brake which concerns on 1st Embodiment. It is AA sectional drawing in FIG. It is a top view of the motor support structure which shows the modification of 1st Embodiment. It is a perspective view of the motor support structure of the disc brake which concerns on 2nd Embodiment. It is a top view of the motor support structure of the disc brake which concerns on 2nd Embodiment. It is BB sectional drawing in FIG. It is a disassembled perspective view of the motor support structure of the disc brake which concerns on 3rd Embodiment. It is a top view of the motor support structure of the disc brake which concerns on 3rd Embodiment. It is CC sectional drawing in FIG. It is sectional drawing of the motor support structure which shows the modification of 3rd Embodiment. It is a disassembled perspective view of the motor support structure of the disc brake which concerns on 4th Embodiment. It is a perspective view of the motor support structure of the disc brake which concerns on 4th Embodiment. It is sectional drawing of the motor support structure of the disc brake which concerns on 4th Embodiment.

[First Embodiment]
A first embodiment of the present invention will be described with reference to the accompanying drawings.
As shown in FIG. 1, the disc brake 1 includes a pair of inner brake pads 2 and outer brake pads 3 disposed on both sides in the axial direction across a disc rotor D attached to a rotating portion of the vehicle, and a caliper 4. And are provided. The disc brake 1 is configured as a caliper floating type. The pair of inner brake pad 2 and outer brake pad 3 and caliper 4 are supported so as to be movable in the axial direction of the disc rotor D by a bracket 5 fixed to a non-rotating portion such as a knuckle of a vehicle. For convenience, the right side in FIGS. 1 and 2 is referred to as one end side, and the left side is referred to as the other end side.

  The caliper body 6 that is the main body of the caliper 4 includes a cylinder portion 7 that is disposed on the base end side facing the inner brake pad 2 on the vehicle inner side, and a claw that is disposed on the distal end side facing the outer brake pad 3 on the vehicle outer side. Part 8. The cylinder portion 7 is formed with a bottomed cylinder 15 that is a large-diameter opening portion 9A that is open on the inner brake pad 2 side, and that is closed by a bottom wall 11 having a hole portion 10 on the opposite side. On the bottom wall 11 side in the cylinder 15, a small-diameter opening 9 </ b> B that is continuous with the large-diameter opening 9 </ b> A and has a smaller diameter than the large-diameter opening 9 </ b> A is formed. The cylinder 15 has a piston seal 16 disposed on the inner peripheral surface of the large-diameter opening 9A.

  As shown in FIGS. 1 and 2, the piston 18 is formed in a bottomed cup shape including a bottom portion 19 and a cylindrical portion 20. The piston 18 is accommodated in the cylinder 15 so that the bottom portion 19 faces the inner brake pad 2. The piston 18 is housed in the large-diameter opening 9A of the cylinder 15 so as to be movable in the axial direction while being in contact with the piston seal 16. A space between the piston 18 and the bottom wall 11 of the cylinder 15 is defined as a hydraulic chamber 21 by a piston seal 16. Fluid pressure is supplied to the fluid pressure chamber 21 from a fluid pressure source (not shown) such as a master cylinder or a fluid pressure control unit through a port (not shown) provided in the cylinder portion 7.

  On the inner peripheral surface of the piston 18, a rotation restricting vertical groove 22, which is a plurality of concave portions, is formed along the circumferential direction. The bottom portion 19 of the piston 18 is provided with a recess 25 on the outer peripheral side of the other end surface facing the inner brake pad 2. The concave portion 25 is engaged with a convex portion 26 formed on the back surface of the inner brake pad 2. Due to the engagement between the concave portion 25 and the convex portion 26, the piston 18 is restricted so as not to rotate relative to the cylinder 15 and thus the caliper body 6. Between the outer peripheral surface of the piston 18 on the bottom 19 side and the inner peripheral surface of the large-diameter opening 9 </ b> A of the cylinder 15, a dust boot 27 that prevents foreign matter from entering the cylinder 15 is interposed.

  3 and 4, a housing 30 in which the motor gear assembly 29 is accommodated is attached to the bottom wall 11 side of the cylinder 15 of the caliper body 6. An opening 30 </ b> A is provided at one end of the housing 30. A cover 36 that is airtightly closed is attached to the opening 30A. In other words, the opening 30 </ b> A of the housing 30 is closed by the cover 36. A seal member 37 is provided between the housing 30 and the cylinder portion 7. The inside of the housing 30 is kept airtight by the seal member 37. The housing 30 covers the outer periphery of the bottom wall 11 of the cylinder 15, and includes a first housing 31 that houses a spur multi-stage reduction mechanism 44 and a planetary gear reduction mechanism 45, which will be described later, and a bottom that is integrated with the first housing 31. A second housing 32 that protrudes in a cylindrical shape and accommodates the motor 200 is formed. The housing 30 accommodates the motor 200 arranged so as to be aligned with the caliper body 6 by the bottomed cylindrical second housing 32.

  The first housing 31 includes an outer wall portion 31F and a bottom surface portion 31G that surround a housing chamber 31E that houses a flat-tooth multistage reduction mechanism 44 and a planetary gear reduction mechanism 45, which will be described later, together with a cover 36, and a part of the bottom wall 11 of the cylinder 15. A mounting opening 31A for receiving and inserting a polygonal shaft portion 81 of a base nut 75 of the rotation / linear motion converting mechanism 43, which will be described later, and an inner annular wall portion 31B protruding around the mounting opening 31A, An outer annular wall portion 31C that protrudes radially outward from the inner annular wall portion 31B, and a plurality of engagement grooves 31D that are formed at intervals in the circumferential direction of the outer annular wall portion 31C. Have. A connector portion 34 having two connection terminals 33 inside is integrally provided so as to straddle the first housing 31 and the second housing 32. Each connection terminal 33 is electrically connected to each connection terminal 35 disposed in the second housing 32.

  As shown in FIG. 1 and FIG. 2, the caliper body 6 reinforces the driving force from the motor 200 and the rotation / linear motion converting mechanism 43 that propels the piston 18 and holds the propelled piston 18 in the braking position. A spur multi-stage reduction mechanism 44 and a planetary gear reduction mechanism 45 are provided. The spur multi-stage reduction mechanism 44 and the planetary gear reduction mechanism 45 as the reduction mechanism are accommodated in the accommodation chamber 31 </ b> E inside the first housing 31 of the housing 30.

  The rotation / linear motion conversion mechanism 43 converts the rotational motion (that is, the rotation of the motor 200) from the spur multi-stage speed reduction mechanism 44 and the planetary gear speed reduction mechanism 45 into a linear motion (hereinafter referred to as “linear motion”). The piston 18 is held at the braking position by applying a thrust force to the piston 18. The rotation / linear motion conversion mechanism 43 is screwed into a base nut 75 to which the rotational motion from the spur multi-stage speed reduction mechanism 44 and the planetary gear speed reduction mechanism 45 is transmitted, and a female thread portion 97 of the base nut 75 so as to be rotatable. The push rod 102 is supported so as to be linearly movable, and the ball and ramp mechanism 127 is screwed to the push rod 102 and applies thrust in the axial direction to the piston 18 by the rotation of the push rod 102. The rotation / linear motion conversion mechanism 43 is accommodated between the cylinder 15 and the piston 18 of the caliper body 6.

  Referring to FIGS. 1, 3, and 4, the spur multi-stage reduction mechanism 44 includes a pinion gear 46, a first reduction gear 47, a non-reduction spur gear 48, and a second reduction gear 49. For the first reduction gear 47, the non-reduction spur gear 48, and the second reduction gear 49, a metal material or a resin material such as fiber reinforced resin is used. The pinion gear 46 has a hole 50 that is formed in a cylindrical shape and is press-fitted and fixed to the rotating shaft 201 of the motor 200, and a gear 51 that is formed on the outer periphery. The first reduction gear 47 is integrally formed with a large-diameter large gear 53 that meshes with the gear 51 of the pinion gear 46 and a small-diameter small gear 54 that extends from the large gear 53 in the axial direction. The first reduction gear 47 is rotatably supported by the shaft 52 with respect to the support plate 59 and the holder 205. One end of the shaft 52 is supported by a support plate 59 close to the cover 36, and the other end is supported by a holder 205.

  The small gear 54 of the first reduction gear 47 is meshed with the non-reduction spur gear 48. The non-reducing spur gear 48 is rotatably supported by the shaft 55 with respect to the support plate 59 and the holder 205. One end of the shaft 55 is supported by a support plate 59 close to the cover 36, and the other end is supported by a holder 205. The second reduction gear 49 is integrally formed with a large-diameter large gear 56 that meshes with the non-reducing spur gear 48 and a small-diameter sun gear 57 that extends from the large gear 56 in the axial direction. The sun gear 57 is configured as a part of a planetary gear reduction mechanism 45 described later. In the second reduction gear 49, a shaft 58 is inserted through a central hole 49A. The shaft 58 is press-fitted and fixed to a support plate 59 provided at one end close to the cover 36. The second reduction gear 49 is rotatably supported by the shaft 58. An annular stopper portion 56A that protrudes toward the planetary gear reduction mechanism 45 is formed on the annular wall portion of the large gear 56 of the second reduction gear 49.

  The planetary gear reduction mechanism 45 includes a sun gear 57 of the second reduction gear 49, a plurality (four in this embodiment) of planetary gears 60, an internal gear 61, and a carrier 62. Each planetary gear 60 has a gear 63 meshed with the sun gear 57 of the second reduction gear 49 and a hole 64 through which a pin 65 erected from the carrier 62 is rotatably inserted. The planetary gears 60 are arranged at equal intervals on the circumference of the carrier 62.

  The carrier 62 is formed in a disk shape, and a polygonal hole 68 is formed at the substantially radial center. The outer diameter of the carrier 62 is substantially the same as the outer diameter of the revolution trajectory of each planetary gear 60. A plurality of pin holes 69 are formed on the outer peripheral side of the carrier 62 at intervals along the circumferential direction. Each pin 65 is press-fitted and fixed in each pin hole 69. Each pin 65 is rotatably inserted into the hole 64 of each planetary gear 60. The polygonal hole 68 of the carrier 62 and the polygonal shaft portion 81 of the base nut 75 of the rotation / linear motion converting mechanism 43 to be described later are fitted to each other, so that rotational torque is mutually generated between the carrier 62 and the base nut 75. Is transmitted. An annular support member 78 (see FIG. 3) is provided between the carrier 62 and each planetary gear 60.

  The internal gear 61 extends in a radial direction continuously from an inner tooth 71 meshed with the gear 63 of each planetary gear 60 and one end of the inner tooth 71 on the cover 36 side, and moves the planetary gear 60 in the axial direction. An annular wall portion 72 to be regulated, and a cylinder that extends from the inner teeth 71 toward the bottom wall 11 of the cylinder 15 and is inserted into an annular space between the inner annular wall portion 31B and the outer annular wall portion 31C of the first housing 31. And a wall portion 73. On the outer peripheral surface of the internal gear 61, a plurality of protrusions 74 are provided that are spaced apart in the circumferential direction. Each protrusion 74 protrudes radially outward and engages with each engagement groove 31 </ b> D provided in the first housing 31.

  A plurality of pins 65 corresponding to each planetary gear 60 are disposed inside the annular wall portion 72 of the internal gear 61, and each pin 65 protrudes slightly toward the cover 36 from the annular wall portion 72. The internal gear 61 is supported in the first housing 31 so as to be non-rotatable by the projections 74 being inserted into and engaged with the engagement grooves 31 </ b> D of the first housing 31. Since the internal gear 61 is provided with an annular stopper portion 56A provided on the large gear 56 of the second reduction gear 49 on the cover 36 side of the annular wall portion 72, the first housing 31 is not movable in the axial direction. Supported within.

  As shown in FIGS. 3 and 4, the motor 200 is supported by a holder 205 disposed on the motor flange 202. In the holder 205, a motor support portion 206 and a ring-shaped support portion 207 are integrally formed. The motor support 206 is disposed between the first reduction gear 47 and the non-reduction spur gear 48 and the motor flange 202. The ring-shaped support portion 207 is disposed around the internal gear 61 so as to surround the internal gear 61 of the planetary gear reduction mechanism 45. The motor support portion 206 is formed with a rotation shaft insertion hole 208 through which the pinion gear 46 press-fitted and fixed to the rotation shaft 201 of the motor 200 is inserted. Around the rotation shaft insertion hole 208, terminal insertion holes through which the motor terminals 203 of the motor 200 are inserted are formed at two locations, and each terminal insertion hole is in the radial direction of the rotation shaft insertion hole 208. A pair is formed on both sides. Harnesses 242 and 243 are connected to the motor terminals 203 of the motor 200, respectively. The harnesses 242 and 243 are connected to the connection terminals 35 disposed in the second housing 32.

  Referring to FIGS. 3 to 5, the motor support 206 of the holder 205 includes a holder-side first convex portion 211, a holder-side, around the rotation shaft insertion hole 208 on the side opposite to the planetary gear reduction mechanism 45. The 2nd convex part 212 and the holder side 3rd convex part 213 are formed at intervals. These cylindrical convex portions 211, 212, and 213 are projected toward the cover 36 side. The holder-side first convex portion 211 is disposed in the vicinity of the rotation shaft 201 of the motor 200, and more specifically, the radial center of the rotation shaft 201 of the motor 200 and the radial center of the sun gear 57 of the planetary gear reduction mechanism 45. Is located on the opposite side of the rotating shaft 201 of the motor 200 from the planetary gear reduction mechanism 45 side. The holder side second convex portion 212 is formed on the first reduction gear 47 side, and the holder side third convex portion 213 is formed on the non-reduction spur gear 48 side. The motor 200 is supported on the motor support 206 of the holder 205 by a motor support structure 191 described later.

  The ring-shaped support portion 207 is disposed on each protrusion 74 so as to contact the outer peripheral surface of the internal gear 61 of the planetary gear reduction mechanism 45. As shown in FIG. 3, two cylindrical support portions 217 and 217 are integrally formed with a space between the motor support portion 206 and the ring-shaped support portion 207 of the holder 205. A support plate 59 is disposed on each cylindrical support portion 217, 217, and each mounting bolt 218, 218 is fastened to each cylindrical support portion 217, 217 of the holder 205 via the support plate 59, thereby supporting plate 59 are supported on the holder 205 at intervals.

  As shown in FIG. 4, a cover side first cylindrical portion 221, a cover side second convex portion 222, and a cover side third convex portion 223 are suspended from the inner surface of the cover 36. These cover-side first cylindrical portion 221, cover-side second convex portion 222, and cover-side third convex portion 223 are the corresponding holder-side first convex portion 211 and holder-side second convex portion provided on the holder 205. 212 and the holder side third convex portion 213. The cover-side first cylindrical portion 221 and the inner peripheral wall of the cover 36 are connected by a first rib 224. The cover side first cylindrical portion 221 and the cover side second convex portion 222 are connected by a second rib 225. The cover side first cylindrical portion 221 and the cover side third convex portion 223 are connected by a third rib 226. And the cover side 1st cylindrical part 221, the cover side 2nd convex part 222, the cover side 3rd convex part 223 of the cover 36, the holder side 1st convex part 211, the holder side 2nd convex of the holder 205 A rubber 230 made of an elastic member is interposed between the portion 212 and the holder side third convex portion 213.

  As shown in FIG. 3, in the first embodiment, a plurality of types of rubbers 246, 247, and 248 different from the rubber 230 described above are provided in the housing 30. A U-shaped support section 245 is formed at the end of the holder 205 on the motor support section 206 side, and a U-shaped rubber section 246 is integrally provided therein. A block-shaped rubber 247 is disposed between the outer peripheral surface near the cylindrical support portions 217 and 217 and the inner wall surface of the first housing 31 in the ring-shaped support portion 207 of the holder 205. A cylindrical rubber 248 is disposed between the main body side end portion of the motor 200 and the bottom wall portion of the second housing 32.

  3 to 6, the rubber 230 includes a first cup part 231, a second cup part 232, a third cup part 233, the first cup part 231, the second cup part 232, and a third cup part 231. It is comprised by the plate-shaped base part 234 which connects the edge part of the cup part 233 integrally. The first cup portion 231 includes a circular first top end portion 231A and a first cylindrical portion 231B that is integrally suspended from the first top end portion 231A. A first protruding portion 231 </ b> C protrudes from one surface of the first top end portion 231 </ b> A of the first cup portion 231. The first projecting portion 231C is formed in a circular shape having a smaller diameter than the first top end portion 231A.

  The second cup portion 232 includes a circular second top end portion 232A and a second cylindrical portion 232B that is integrally suspended from the second top end portion 232A. A second projecting portion 232C projects from one surface of the second top end 232A. The second projecting portion 232C is formed in a circular shape having a smaller diameter than the second top end portion 232A. The third cup portion 233 includes a circular third top end portion 233A and a third cylindrical portion 233B that is integrally suspended from the third top end portion 233A. A third projecting portion 233C projects from one surface of the third top end 233A. The third projecting portion 233C is formed in a circular shape having a smaller diameter than the third top end portion 233A.

  5 and 6, the base part 234 of the rubber 230 has a first notch part 235A, a second notch part 235B, and a third notch part 235C to prevent interference with other components. It is formed. In the vicinity of the first cutout portion 235A, a protective wall portion 237 as a guide portion protrudes from the outer peripheral edge of the base portion 234. The protective wall portion 237 extends substantially parallel to the inner wall surface of the first housing 31. That is, the protective wall portion 237 is disposed between the first harness 242 and the first housing 31. The height of the protective wall portion 237 is formed to be higher than the outer diameter of the first harness 242. Between the first cup part 231 and the third cup part 233, a first guide wall part 239 and a second guide wall part 240 as guide parts that project linearly from the base part 234 are provided.

  The first guide wall portion 239 and the second guide wall portion 240 extend substantially parallel to each other in the same direction as the protective wall portion 237. The first guide wall portion 239 is disposed on the first cup portion 231 side, and the second guide wall portion 240 is disposed on the third cup portion 233 side. One end portion of the first guide wall portion 239 on the third notch portion 235C side and one end portion of the second guide wall portion 240 on the third notch portion 235C side are formed in a thin shape. The first guide wall portion 239 and the second guide wall portion 240 have the same height and are formed to be larger than the outer diameter of the second harness 243. The second harness 243 is supported between the first guide wall part 239 and the second guide wall part 240. The rubber 246 having a U-shaped cross section may be integrally suspended from the position of the third notch 235C on the bottom surface of the base portion 234 of the rubber 230.

  And the 1st cylindrical part 231B of the 1st cup part 231 of the rubber 230 is fitted to the holder side 1st convex part 211 of the holder 205, and the 2nd cylindrical part 232B of the 2nd cup part 232 of the rubber 230 is a holder. The rubber 230 is fitted by fitting the third cylindrical portion 233B of the third cup portion 233 of the rubber 230 to the holder-side third convex portion 213 of the holder 205. The holder 205 is unitized. Further, the cover-side first cylindrical portion 221 of the cover 36 is fitted to the first cylindrical portion 231B including the first projecting portion 231C of the first cup portion 231 of the rubber 230, and the cover-side second side of the cover 36 is fitted. The convex part 222 is brought into contact with the second projecting part 232C of the second cup part 232 of the rubber 230, and the cover side third convex part 223 of the cover 36 is provided with the third projecting part of the third cup part 233 of the rubber 230. The cover 36 is covered by contacting the portion 233C. As a result, a space is formed between the surface of the base portion 234 of the rubber 230 and the bottom surface of the cover 36.

  As shown in FIG. 5, the harnesses 242 and 243 extending from the motor terminals 203 of the motor 200 are arranged along the base portion 234 of the rubber 230. Specifically, of the harnesses 242 and 243, the first harness 242 protrudes from the first notch 235 </ b> A of the rubber 230, extends toward the protective wall 237 of the rubber 230, and is close to the protective wall 237. And the terminal is connected to one connection terminal 35. Of the harnesses 242 and 243, the second harness 243 protrudes from the vicinity of the third cup portion 233 of the rubber 230 and is formed between the first guide wall portion 239 and the second guide wall portion 240 provided on the rubber 230. Guided along, the terminal is connected to the other connection terminal 35.

  The motor gear assembly 29 is configured by assembling the motor 200, the spur multi-stage reduction mechanism 44, the planetary gear reduction mechanism 45, and the rubbers 230, 246, 247, 248 to the holder 205 and the support plate 59. The motor gear assembly 29 is attached to the housing 30 and the cover 36 in a floating state by rubbers 230, 246, 247 and 248. In other words, the motor gear assembly 29 is fixed to the housing 30 and the cover 36 via the rubbers 230, 246, 247, and 248 without the holder 205 being in contact with the housing 30 and the cover 36. As described above, the motor gear assembly 29 is fixed to the housing 30 and the cover 36 via the rubbers 230, 246, 247, 248, so that the motor 200, the spur multi-stage reduction mechanism 44, and the planetary gear reduction mechanism 45 are generated. Transmission of vibrations to the housing 30 and the cover 36 is suppressed, and generation of noise due to vibrations can be suppressed.

  In the first embodiment, the spur multi-stage reduction mechanism 44 and the planetary gear reduction mechanism 45 are employed as the reduction mechanism for increasing the driving force by the motor 200 in order to obtain the rotational force for propelling the piston 25. You may comprise only the deceleration mechanism 45. FIG. Further, a speed reducer according to another known technique such as a cycloid speed reduction mechanism or a wave speed reducer may be combined with the planetary gear speed reduction mechanism 45.

  As shown in FIGS. 1 and 2, the base nut 75 which is the configuration of the rotation / linear motion converting mechanism 43 is configured by a cylindrical portion 76 and a nut portion 77 provided integrally with the other end of the cylindrical portion 76. The A washer 80 is disposed so as to contact the bottom wall 11 of the cylinder 15. The cylindrical portion 76 of the base nut 75 is inserted through the insertion hole 80 </ b> A of the washer 80 and the hole 10 provided in the bottom wall 11 of the cylinder 15. A polygonal shaft portion 81 is integrally formed at the tip of the cylindrical portion 76. The polygon shaft 81 is inserted into the attachment opening 31 </ b> A of the first housing 31 and is fitted into the polygon hole 68 of the carrier 62. The nut portion 77 of the base nut 75 is formed in a bottomed cylindrical shape. The nut portion 77 includes a circular wall portion 82 and a cylindrical portion 83 that projects integrally from the other end surface of the circular wall portion 82. The outer peripheral surface of the circular wall portion 82 is close to the inner wall surface of the small diameter opening 9 </ b> B of the cylinder 15. A small-diameter circular wall portion 84 projects from the radial center of one end surface of the circular wall portion 82. A cylindrical portion 76 projects from one end surface of the small-diameter circular wall portion 84 toward one end side. The outer diameter of the cylindrical portion 76 is formed smaller than the outer diameter of the cylindrical portion 83 of the nut portion 77.

  A thrust bearing 87 is disposed between the washer 80 and the circular wall portion 82 around the small-diameter circular wall portion 84 provided on the nut portion 77 of the base nut 75. The base nut 75 is rotatably supported on the bottom wall 11 of the cylinder 15 via a thrust bearing 87. A seal member 88 and a sleeve 89 are provided between the outer peripheral surface of the cylindrical portion 76 of the base nut 75 and the hole 10 of the bottom wall 11 of the cylinder 15. Thereby, the fluid tightness of the hydraulic chamber 21 is maintained. A retaining ring 90 is mounted in the annular groove between the cylindrical portion 76 of the base nut 75 and the polygonal shaft portion 81, and movement of the base nut 75 in the axial direction relative to the cylinder 15 is restricted by the retaining ring 90.

  The cylindrical portion 83 of the nut portion 77 of the base nut 75 includes a large diameter cylindrical portion 91 disposed on one end side and a small diameter cylindrical portion 92 disposed on the other end side. One end of the large diameter cylindrical portion 91 is integrally connected to the circular wall portion 82. A plurality of through holes 95 extending in the radial direction are formed in the peripheral wall portion of the large diameter cylindrical portion 91. The plurality of through holes 95 are formed at intervals in the circumferential direction. A female screw portion 97 is formed on the inner peripheral surface of the small diameter cylindrical portion 92 of the nut portion 77. A plurality (four in the first embodiment) of locking grooves 98 are formed on the other end surface of the peripheral wall portion of the small-diameter cylindrical portion 92 at intervals in the circumferential direction.

  As shown in FIG. 2, the front end portion of the first spring clutch 100 that imparts rotational resistance to rotation in one direction is fitted in one of the locking grooves 98 of the small-diameter cylindrical portion 92 of the base nut 75. Is done. The first spring clutch 100 is constituted by a coil portion wound continuously and continuously from a tip portion facing outward in the radial direction. The front end of the first spring clutch 100 is fitted into one of the plurality of locking grooves 98 of the small-diameter cylindrical portion 92 of the base nut 75, and the coil portion is the outer periphery on the other end side of the male screw portion 103 of the push rod 102 described later. Wrapped around. The first spring clutch 100 applies rotational resistance torque to the rotational direction (the rotational direction at the time of release) when the push rod 102 moves toward the bottom wall 11 of the cylinder 15 with respect to the base nut 75, while pushing The rod 102 is configured to allow rotation in the rotation direction (rotation direction at the time of application) when moving to the bottom 19 side of the piston 18 with respect to the base nut 75.

  One end side of the push rod 102 is inserted into the nut portion 77 of the base nut 75. On one end side of the push rod 102, a male screw portion 103 that is screwed into the female screw portion 97 of the small diameter cylindrical portion 92 of the base nut 75 is formed. The first screwing portion 105 formed by the male screw portion 103 of the push rod 102 and the female screw portion 97 of the small diameter cylindrical portion 92 of the base nut 75 prevents the base nut 75 from rotating due to an axial load from the piston 18 to the push rod 102. The reverse efficiency is 0 or less, that is, it is configured as a screwed portion having a large irreversibility.

  On the other hand, the other end side of the push rod 102 is formed with a male screw portion 104 that is screwed into a female screw portion 162 provided on a rotary linear motion lamp 151 of a ball and ramp mechanism 127 described later. Here again, the second threaded portion 106 formed by the male threaded portion 104 of the push rod 102 and the female threaded portion 162 provided in the rotary linear motion ramp 151 is caused by the axial load from the piston 18 to the rotational linear motion ramp 151. So as not to rotate, the reverse efficiency is 0 or less, that is, it is configured as a screwed portion having a large irreversibility.

  The push rod 102 is provided with a spline shaft 108 between a male screw portion 103 on one end side and a male screw portion 104 on the other end side. The outer diameter of the male screw portion 103 on one end side is formed larger than the outer diameter of the male screw portion 104 on the other end side. The outer diameter of the male screw portion 103 on one end side is formed larger than the outer diameter of the spline shaft 108. The other end surface of the male screw portion 104 of the push rod 102 faces the bottom portion 19 of the piston 18.

  A retainer 110 is supported between the outer peripheral surface of the small diameter cylindrical portion 92 of the cylindrical portion 84 constituting the nut portion 77 of the base nut 75 and the inner peripheral surface of the cylindrical portion 20 of the piston 18 so as to be movable in the axial direction. The The retainer 110 has an annular wall portion 111 on one end side, and is configured in a substantially cylindrical shape as a whole. A plurality of through holes are formed in the outer peripheral wall of the retainer 110. Within the retainer 110, one end side washer 120, a coil spring 121, the other end side washer 122, a support plate 123, a second spring clutch 124, a rotating member 125, a thrust bearing 126, a ball and ramp mechanism 127, in order from one end side. A thrust bearing 128 and an annular pressing plate 129 are arranged. The one end side washer 120 is disposed so as to contact the other end surface of the annular wall portion 111 of the retainer 110.

  The coil spring 121 is interposed between the one end side washer 120 and the other end side washer 122. The coil spring 121 urges the one end side washer 120 and the other end side washer 122 in a direction to separate them. A plurality of (three in the first embodiment) locking grooves 132 having a predetermined depth are formed on the other end surface of the peripheral wall portion of the retainer 110 at intervals in the circumferential direction. At the other end of the retainer 110, a plurality of claw portions 136 are formed toward the bottom portion 19 of the piston 18. In the retainer 110, one end side washer 120, coil spring 121, other end side washer 122, support plate 123, second spring clutch 124, rotating member 125, thrust bearing 126, ball and ramp mechanism 127, thrust bearing 128 and annular pressure After the plate 129 is accommodated, each of the claws 136 of the retainer 110 is folded toward the accommodating recess 171 of the annular pressing plate 129 described later, whereby the above-described components are integrally disposed in the retainer 110 and assembled. Can do.

  An annular support plate 123 abuts on the other end surface of the other end washer 122. A plurality (three in the first embodiment) of projecting pieces 137 are provided on the outer peripheral surface of the support plate 123 at intervals in the circumferential direction. Each protruding piece 137 is fitted into the locking groove 132 of the retainer 110 and the rotation restricting vertical groove 22 provided on the inner peripheral surface of the piston 18. As a result, the retainer 110 is supported together with the one end side washer 120, the coil spring 121, the other end side washer 122, and the support plate 123 so as not to be relatively rotatable with respect to the piston 18 and to be relatively movable in the axial direction.

  In the retainer 110, the rotation member 125 is rotatably supported on the other end side of the support plate 123. The rotating member 125 includes a large-diameter annular portion 141 having a spline hole 140 and a small-diameter cylindrical portion 142 that projects integrally from one end surface of the large-diameter annular portion 141. One end of the small diameter cylindrical portion 142 is in contact with the other end surface of the support plate 123. By inserting the push rod 102 into the rotating member 125, the spline hole 140 of the large-diameter annular portion 141 of the rotating member 125 and the spline shaft 108 of the push rod 102 are spline-coupled. Thereby, the rotational torque is transmitted between the rotating member 125 and the push rod 102.

  A second spring clutch 124 that imparts rotational resistance to rotation in one direction is wound around the outer peripheral surface of the small-diameter cylindrical portion 142 of the rotating member 125. Similar to the first spring clutch 100, the second spring clutch 124 is configured by a coil portion wound continuously and continuously from a tip portion facing radially outward. The tip of the second spring clutch 124 is fitted into the locking groove 132 of the retainer 110, and the coil portion is wound around the outer periphery of the small diameter cylindrical portion 142 of the rotating member 125. The second spring clutch 124 applies a rotational resistance torque to the rotational direction (the rotational direction at the time of application) when the rotational member 125 (push rod 102) moves toward the bottom 19 side of the piston 18 with respect to the retainer 110. On the other hand, rotation in the rotation direction (rotation direction at release) when moving to the bottom wall 11 side of the cylinder 15 is allowed.

  The rotational resistance torque when the second spring clutch 124 is applied is larger than the rotational resistance torque of the first screwing portion 105 between the male screw portion 103 of the push rod 102 and the female screw portion 97 of the base nut 75. Set to A ball and ramp mechanism 127 is disposed on the other end side of the rotating member 125 via a thrust bearing 126. The rotating member 125 is rotatably supported by a ball and ramp mechanism 127 via a thrust bearing 126.

  The ball-and-ramp mechanism 127 includes a fixed lamp 150, a rotation / linear motion ramp 151, and each ball 152 interposed between the fixed lamp 150 and the rotation / linear motion ramp 151. The fixed lamp 150 is disposed on the other end side of the rotating member 125 via a thrust bearing 126. The fixed lamp 150 includes a disk-shaped fixed plate 154 and a plurality of convex portions 155 protruding from the outer peripheral surface of the fixed plate 154 along the circumferential direction. An insertion hole 156 through which the push rod 102 is inserted is formed at the center in the radial direction of the fixed plate 154. The fixed ramp 150 is configured such that each convex portion 155 is fitted to each locking groove 132 of the retainer 110 and each rotation regulating vertical groove 22 provided on the inner peripheral surface of the piston 18, so that It is supported so that it cannot rotate and is movable in the axial direction. A plurality of (three in the first embodiment) ball grooves 157 having a predetermined inclination angle along the circumferential direction and extending in an arc shape in the circumferential direction and having an arc-shaped cross section in the radial direction are formed on the other end surface of the fixed plate 154. Is formed.

  The rotation / linear motion ramp 151 is configured by an annular rotation / linear motion plate 160 and a cylindrical portion 161 integrally projecting from the radial center of the other end surface of the rotation / linear motion plate 160. On the inner peripheral surface from the rotary linear motion plate 160 to the cylindrical portion 161, a female screw portion 162 to which the male screw portion 104 of the push rod 102 is screwed is formed. On the surface of the rotary translation plate 160 facing the fixed plate 154 of the fixed lamp 150, a plurality of (first) extending in an arc shape with a predetermined inclination angle along the circumferential direction and having an arc-shaped cross section in the radial direction. In one embodiment, three ball grooves 163 are formed. In addition, each ball groove 157 of the fixed ramp 150 and each ball groove 163 of the rotary linear motion ramp 151 are configured such that a depression is provided in the middle of the inclination along the circumferential direction or the inclination is changed in the middle. Also good.

  The ball 152 is interposed between each ball groove 163 of the rotation linear movement ramp 151 (rotation linear movement plate 160) and each ball groove 157 of the fixed ramp 150 (fixation plate 154). When a rotational torque is applied to the rotation / linear motion ramp 151, the balls 152 between the ball grooves 163 of the rotation / linear motion plate 160 and the ball grooves 157 of the fixed plate 154 roll, and the rotation / linear motion plate 160. And the fixed plate 154, the relative distance in the axial direction between the rotary translation plate 160 and the fixed plate 154 varies.

  An annular pressing plate 129 is disposed on the other end surface of the cylindrical portion 161 of the rotary translation plate 160 via a thrust bearing 128. On the outer peripheral surface of the annular pressing plate 129, a plurality of convex portions 168 are provided protruding at intervals along the circumferential direction. The annular pressing plate 129 is fitted to the respective locking grooves 132 of the retainer 110 and the respective rotation restricting vertical grooves 22 provided on the inner peripheral surface of the piston 18, so that the annular pressing plate 129 is attached to the piston 18. Thus, it is supported so as not to be relatively rotatable and movable in the axial direction.

  The rotation / linear motion ramp 151 is supported by an annular pressing plate 129 so as to be rotatable via a thrust bearing 128. The other end surface of the annular pressing plate 129 comes into contact with the bottom portion 19 of the piston 18 and presses the piston 18. On the other end surface of the annular pressing plate 129, an accommodation recess 171 is formed on the outer peripheral portion between the projections 168 to accommodate the claw portions 136 of the retainer 110 that are folded inward.

  As shown in FIG. 2, a stopper member for determining a relative rotation range between the push rod 102 and the rotation linear motion ramp 151 of the ball and ramp mechanism 127 is provided at the tip of the male thread portion 104 of the push rod 102. 172 is fixed integrally. Further, as shown in FIG. 1, an ECU 175, which is an electronic control device that drives and controls the motor 200, is electrically connected to the motor 200 via a connector portion 34. The ECU 175 is connected to a parking switch 176 that is operated to instruct the operation / release of the parking brake. The ECU 175 can be operated based on a signal from the vehicle (not shown), regardless of the operation of the parking switch 176.

A motor support structure 191 for supporting the motor 200 on the motor support 206 of the holder 205 will be described mainly with reference to FIGS.
The holder 205 is provided with a plurality (two in the first embodiment) of projecting portions 181 and 182 projecting in a direction along the axis of the rotation shaft 201 of the motor 200 (hereinafter referred to as “motor shaft direction”). Each protrusion 181 and 182 extends in the direction opposite to the cover 36 side (downward direction in FIGS. 7 and 9) from the peripheral wall of the motor support portion 206. The tip portions (tip side) of the protrusions 181 and 182 face the motor flange 202. The motor flange 202 (flange) has a fixed flange surface 202A extending in an arc shape along the peripheral edge on one end side (the upper side in FIGS. 7 and 9) of the motor body, and an extension projecting in the motor radial direction. It has parts 202B and 202B, and notches 202C and 202C provided so as to avoid interference with rubber 246.

  Referring to FIG. 8, the protrusions 181 and 182 are closer to the ring-shaped support portion 207 side (upper side in FIG. 8) than the shaft center O1 of the motor 200, and the shaft center O1 and the shaft center O2 of the ring-shaped support portion 207. Are arranged on opposite sides via a straight line L1 orthogonal to the. Each protrusion 181 and 182 is curved along the outer peripheral surface of the motor 200. Engaging claws 183 and 184 that are engaged with the fixed flange surface 202A of the motor flange 202 are provided at the ends of the protrusions 181 and 182 on the front end side (the lower side in FIG. 9). Referring to FIG. 9, each of the engagement claws 183 and 184 has engagement surfaces 183A and 184A that protrude in a direction perpendicular to the motor shaft direction. The engaging surfaces 183A and 184A extend from the inner wall surfaces 181A and 182A of the protrusions 181 and 182 toward the inside (the axis of the motor 200). Each engagement claw 183, 184 has inclined surfaces 183B, 184B extending from the tips of the engagement surfaces 183A, 184A toward the tips of the protrusions 181, 182.

  As shown in FIG. 8, the engagement claws 183 and 184 are engaged with the fixed flange surface 202 </ b> A, in other words, an uneven portion of the motor 200 (an uneven portion in the motor radial direction) and a protruding portion 181 of the holder 205. , 182 are engaged with each other, the extended portions 202B, 202B of the motor flange 202 are brought into contact with the end surfaces of the boss portions 185, 186 formed on the motor support portion 206 of the holder 205. Further, the shoulder 202D on one side (counterclockwise direction side in FIG. 8) of one extension 202B of the motor flange 202 (the extension 202B positioned on the upper side in FIG. 8) is the other side of the protrusion 181. It abuts on the end in the clockwise direction in FIG.

  Thereby, the motor 200 is fixed to the holder 205 in the motor shaft direction and the motor rotation direction, that is, relative movement in the motor shaft direction and the motor rotation direction with respect to the holder 205 is prevented. The relative movement of the motor 200 with respect to the holder 205 in the motor rotation direction means the movement of the motor 200 in the counterclockwise direction around the axis O1 with respect to the holder 205 in FIG. 8 when the motor 200 is operated. It is.

Next, the operation of the above-described disc brake 1 will be described.
First, the operation during braking of the disc brake 1 as a normal hydraulic brake by operating a brake pedal (not shown) will be described.

  When the driver depresses the brake pedal, the hydraulic pressure corresponding to the depressing force of the brake pedal is supplied from the master cylinder to the hydraulic pressure chamber 21 in the caliper 4 via a hydraulic pressure circuit (not shown). Thereby, the piston 18 moves forward (moves leftward in FIG. 1) from the original position at the time of non-braking while elastically deforming the piston seal 16, and presses the inner brake pad 2 against the disc rotor D. The caliper body 6 moves to the right in FIG. 1 with respect to the bracket 5 by the reaction force of the pressing force of the piston 18, and presses the outer brake pad 3 attached to the claw portion 8 against the disc rotor D. As a result, the disc rotor D is pinched by the pair of inner and outer brake pads 2 and 3 to generate a frictional force, and thus a braking force for the vehicle.

  And when a driver | operator releases a brake pedal, supply of the hydraulic pressure from a master cylinder stops, and the hydraulic pressure in the hydraulic pressure chamber 21 falls. As a result, the piston 18 is moved back to the original position by the restoring force of the elastic deformation of the piston seal 16, and the braking force is released. When the movement amount of the piston 18 increases with the wear of the inner and outer brake pads 2 and 3 and exceeds the limit of elastic deformation of the piston seal 16, slip occurs between the piston 18 and the piston seal 16. By this sliding, the original position of the piston 18 with respect to the caliper body 6 is moved, so that the pad clearance is adjusted to be constant.

Next, the operation of the parking brake as an example of the function of maintaining the vehicle stop state will be described.
The parking brake is activated (applied) by operating the parking switch 176 from the released state. At this time, the ECU 175 drives the motor 200 to rotate the sun gear 57 of the planetary gear reduction mechanism 45 via the spur multi-stage reduction mechanism 44. Due to the rotation of the sun gear 57, the carrier 62 is rotated via each planetary gear 60, and the rotational torque from the carrier 62 is transmitted to the base nut 75.

  Next, the rotational resistance torque in the apply direction of the rotating member 125 (push rod 102) to the retainer 110 (piston 18) by the second spring clutch 124 causes the first screwing portion between the push rod 102 and the base nut 75 to be applied. It is set to be larger than the rotational resistance torque by 105. Accordingly, the first spring clutch 100 is allowed to rotate the push rod 102 in the apply direction with respect to the base nut 75. For this reason, the rotation of the base nut 75 in the apply direction causes the first screwing portion 105 to rotate relative to each other, that is, only the base nut 75 rotates in the apply direction, while the push rod 102 extends along the axial direction at the bottom of the piston 18. Advance toward 19th side.

  As a result, the one end side washer 120 in the retainer 110 including the retainer 110 together with the push rod 102, the coil spring 121, the other end side washer 122, the support plate 123, the second spring clutch 124, the rotating member 125, the thrust bearing 126, the ball and The components of the ramp mechanism 127, the thrust bearing 128, and the annular pressing plate 129 are integrally moved forward toward the bottom 19 side of the piston 18 along the axial direction. When the annular pressing plate 129 comes into contact with the bottom portion 19 of the piston 18 by the advancement of these components and the piston 18 advances, one end surface of the bottom portion 19 of the piston 18 comes into contact with the inner brake pad 2.

  When the rotation drive of the motor 200 in the apply direction is continued, the piston 18 starts to press the disc rotor D via the brake pads 2 and 3 by the movement of the push rod 102. When the pressing force of the piston 18 to the disk rotor D starts to be generated, the rotational resistance torque in the first screwing portion 105 between the push rod 102 and the base nut 75 is caused by the axial force that is a reaction force against the pressing force. It increases and becomes larger than the rotational resistance torque of the second spring clutch 124. As a result, the push rod 102 starts rotating in the apply direction together with the rotating member 125 as the base nut 75 rotates. Then, due to the reaction force from the pressing force of the disk rotor D, the rotational resistance torque at the second screwing portion 106 between the push rod 102 and the ball and ramp mechanism 127 also increases due to the reaction force of the pressing force of the disk rotor D. Therefore, the rotational torque in the apply direction of the push rod 102 is transmitted to the rotation linear motion lamp 151 of the ball and ramp mechanism 127 via the second screwing portion 106.

  Then, while the linear motion ramp 151 of the ball and ramp mechanism 127 rotates in the apply direction, the linear motion ramp 151 and the fixed ramp 150 are separated from each other against the urging force of the coil spring 121 by the rolling of each ball 152. Thus, the annular pressing plate 129 further presses the bottom portion 19 of the piston 18. As a result, the pressing force of the disc rotor D by the inner and outer brake pads 2 and 3 increases. In the disc brake 1 of the first embodiment, first, the first screwing portion 105 between the push rod 102 and the base nut 75 is relatively rotated, the push rod 102 is advanced, and the piston 18 is advanced. A pressing force to the disk rotor D is obtained. Therefore, the original position of the push rod 102 with respect to the piston 18 that changes due to the wear of the pair of inner and outer brake pads 2 and 3 with time is adjusted by the operation of the first screwing portion 105.

  At this time, the ECU 175 drives the motor 200 until the pressing force from the pair of inner and outer brake pads 2 and 3 to the disc rotor D reaches a predetermined value, for example, until the current value of the motor 200 reaches a predetermined value. To do. Thereafter, when ECU 175 detects that the pressing force to disk rotor D has reached a predetermined value by the fact that the current value of motor 200 has reached a predetermined value, it stops energization of motor 200. As a result, the linear motion of the ball and ramp mechanism 127 accompanying the rotation of the rotary linear motion lamp 151 is stopped.

  Eventually, a reaction force of the pressing force from the disk rotor D acts on the rotary linear motion lamp 151, but the second screwing portion 106 between the push rod 102 and the ball and ramp mechanism 127 is mutually connected. And the first screwing portion 105 between the push rod 102 and the base nut 75 is also configured as a screw fitting portion that does not reversely operate. By the one-spring clutch 100, the push rod 102 is given a rotational resistance torque in the release direction with respect to the base nut 75, so that the piston 18 is held at the braking position. As a result, the braking force is maintained and the operation of the parking brake is completed.

  When releasing (releasing) the parking brake, the ECU 175 drives the motor 200 to rotate in the release direction that separates the piston 18 from the disk rotor D based on the parking release operation of the parking switch 176. Thereby, the spur multi-stage reduction mechanism 44 and the planetary gear reduction mechanism 45 are rotationally driven in the release direction for returning the piston 18, and the rotational drive in the release direction is transmitted to the base nut 75 via the carrier 62.

  At this time, the reaction force of the pressing force from the disk rotor D acts on the push rod 102. In other words, the push rod 102 has a second threaded portion between the push rod 102 and the ball and ramp mechanism 127. 106, rotation resistance torque of the first screwing portion 105 between the push rod 102 and the base nut 75, and rotation of the push rod 102 in the release direction with respect to the base nut 75 by the first spring clutch 100. Resistance torque is applied. For this reason, the rotational torque in the release direction from the base nut 75 is transmitted to the push rod 102 (including the rotating member 125), and is also transmitted to the rotary linear motion lamp 151 of the ball-and-ramp mechanism 127. As a result, the rotation linear motion lamp 151 only rotates in the release direction and returns to the initial position in the rotation direction.

  The reaction force to the push rod 102 is reduced, and the rotation resistance torque of the second screwing portion 106 between the push rod 102 and the ball and ramp mechanism 127 causes the push rod 102 to act on the base nut 75 by the first spring clutch 100. When the rotational resistance torque in the release direction is smaller than the rotational resistance obtained by adding the rotational resistance torque of the first screwing portion 105 between the push rod 102 and the base nut 75, only the second screwing portion 106 is relatively rotated. To do. As a result, the rotation / linear motion ramp 151 of the ball and ramp mechanism 127 moves along with the retainer 110 along the axial direction toward the bottom wall 11 (release direction) of the cylinder 15 and returns to the initial position in the axial direction.

  Further, when the motor 200 is driven to rotate in the release direction and the rotation of the base nut 75 continues in the release direction, the rotation linear motion lamp 151 of the ball and ramp mechanism 127 returns to the initial position in both the rotation direction and the axial direction. Then, the screwing position of the second screwing portion 106 between the push rod 102 and the ball and ramp mechanism 127 returns to the initial position, and the push rod 102 stops rotating in the release direction.

  Further, when the rotation of the base nut 75 continues in the release direction, the push rod 102 moves along the axial direction against the rotational resistance torque in the release direction of the push rod 102 with respect to the base nut 75 by the first spring clutch 100. Then, the cylinder 15 moves backward toward the bottom wall 11 side (release direction). As a result, the one end side washer 120 in the retainer 110 including the retainer 110 together with the push rod 102, the coil spring 121, the other end side washer 122, the support plate 123, the second spring clutch 124, the rotating member 125, the thrust bearing 126, the ball and The components of the ramp mechanism 127, the thrust bearing 128, and the annular pressing plate 129 are integrally retreated toward the bottom wall 11 side (release direction) of the cylinder 15 along the axial direction. When the piston 18 is moved back to the original position by the restoring force of the elastic deformation of the piston seal 16, the braking force is completely released.

  Here, in a disc brake having a conventional motor support structure, that is, a disc brake in which a mounting bolt is fastened to a nut insert-molded in the holder 205 via a motor flange 202, a tool path is secured when the mounting bolt is tightened. In other words, it is necessary to lay out the peripheral parts while avoiding interference with the tightening tool, and the degree of freedom in design is reduced. As a result, there is a problem that the housing becomes large and it is difficult to accommodate the housing in a small-diameter wheel such as a compact car.

  In contrast, in the first embodiment, the holder 205 is provided with projecting portions 181 and 182 projecting in the motor axial direction, and the engaging claws 183 and 184 of the projecting portions 181 and 182 are fixed to the fixing flange surface 202A of the motor flange 202. The motor 200 is assembled to the holder 205 (temporarily fixed). When the motor 200 is assembled, the motor flange 202 (the outer peripheral edge of the fixed flange surface 202A) is brought into contact with the inclined surfaces 183B and 184B of the respective engaging claws 183 and 184. Press toward (toward the motor shaft). Then, the motor 200 moves to the holder 205 side while expanding the protrusions 181 and 182 with the motor flange 202, and when the engagement claws 183 and 184 face the motor flange 202, the engagement claws 183 and 183 are moved. 184 is engaged (fitted) with the fixed flange surface 202A of the motor flange 202.

  Thus, the disc brake 1 of the first embodiment can attach (temporarily fix) the motor 200 to the holder 205 without using a tightening tool such as a hexagon wrench. Accordingly, the design freedom (the degree of freedom of component layout around the motor 200) is not impaired in order to secure the tool path, and the housing 30 in which the motor gear assembly 29 is accommodated can be downsized.

  Further, in the disc brake 1 of the first embodiment, the motor 200 can be attached (temporarily fixed) to the holder 205 by a one-touch operation, and therefore, the work of tightening the mounting bolts generated in the conventional motor support structure is abolished. And the assembly work can be streamlined. Further, in the disc brake 1 of the first embodiment, the nut insert-molded in the holder 205 and the mounting bolt to be fastened to the nut, which are used in the conventional motor support structure, are not required, and the number of parts can be reduced. Can do. As a result, the disc brake 1 can be reduced in weight, and the manufacturing cost can be reduced.

  The disc brake 1 according to the first embodiment is perpendicular to the motor axial direction in a state in which the projecting portions 181 and 182 of the holder 205 are engaged (hooked) with the fixing flange surface 202A of the motor 200. The engaging surfaces 183A and 184A of the engaging claws 183 and 184 that protrude in the direction are in contact with a part of the fixed flange surface 202A that protrudes outward in the motor radial direction from the outer diameter of the motor 200, and the motor Since the shoulder portion 202D of the one extending portion 202B of the flange 202 is brought into contact with the other end of the protruding portion 181, the motor 200 can be fixed to the holder 205 in the motor axial direction and the motor rotating direction. .

Hereinafter, the operational effects of the first embodiment will be described.
The first embodiment includes a motor that generates a rotational motion upon receiving a current, a holder that supports a motor and a speed reduction mechanism that increases the rotational motion from the motor, and a housing that houses the holder, the motor, and the speed reduction mechanism. The motor has an uneven portion in the motor radial direction, the holder has a protruding portion protruding in the motor axial direction, and the uneven portion of the motor and the protruding portion of the holder are fitted, The motor is fixed to the holder in the motor shaft direction and the motor rotation direction.
Therefore, in the first embodiment, it is possible to fix the motor in the motor shaft direction and the motor rotation direction with respect to the holder without using a tool, and the degree of freedom in design is impaired in order to secure a tool path. In other words, since the layout around the motor can be improved, the housing for housing the holder, the motor, and the speed reduction mechanism can be reduced in size.

  In the first embodiment, the uneven portion of the motor is formed on one end side in the motor axial direction and is a part of the fixed flange surface extending outward in the motor radial direction from the outer diameter of the motor. The concave and convex portion (flange) of the motor can be reduced in size with respect to the motor support structure using the mounting bolt, and thus the holder and the housing can be reduced in size.

  In the first embodiment, the protruding portion of the holder has an engaging claw that protrudes in a direction perpendicular to the motor shaft direction on the tip side, and the engaging claw is engaged with a part of the fixed flange surface. Therefore, it is possible to fix the motor to the holder in the motor axial direction without using the mounting bolts used in the conventional motor support structure, and to reduce assembly man-hours and manufacturing costs. As well as the weight of the disc brake. Further, since the nut that has been insert-molded in the holder in the conventional motor support structure is not required, the disk brake can be reduced in weight and cost. Moreover, since the process of manually setting the nut in the insert molding die is eliminated, the manufacturing process can be streamlined.

  In the first embodiment, the motor is fixed with a backlash in the motor rotation direction with respect to the holder (relative movement is restricted), so that rapid input to the gears when starting the motor is reduced. It is possible to prevent the generation of noise.

  Although the first embodiment has been described above, the extending portions 202A and 202A of the motor flange 202 can be omitted. In this case, in the first embodiment, the extending portions 202A and 202A of the motor flange 202 are received by the boss portions 185 and 186 of the holder 205. However, as shown in FIG. The surface opposite to the surface 202 </ b> A is received by the boss portions 185 and 186 of the holder 205. In this modification, the motor 200 can be reduced in size and weight. The motor 200 can be fixed (rotation restricted) to the holder 205 in the motor rotation direction by bringing one notch C of the motor flange 202 into contact with the rubber 246 attached to the holder 205.

[Second Embodiment]
With reference to FIG. 11 thru | or FIG. 13, 2nd Embodiment is mainly demonstrated centering on a different part from 1st Embodiment. In addition, about the site | part common to 1st Embodiment, it represents with the same name and the same code | symbol.

  The second embodiment includes a motor support structure 192 that is different from the first embodiment. The motor support structure 192 includes protrusions 251 and 252 provided on the bosses 185 and 186 of the holder 205, and engagement holes 253 and 253 provided on the extension portions 202B and 202B of the motor flange 202 (flange). 253 (hole). The protrusions 251 and 252 protrude toward the motor flange 202 from one end surfaces of the bosses 185 and 186 of the holder 205. Each protrusion 251, 252 has a tapered tip, and is fitted into each engagement hole 253, 254 with a predetermined fit, and each protrusion 251, 252. Slits 251B and 252B extending in (in parallel with) the motor shaft direction.

  Each of the protrusions 251 and 251 has a tip outer diameter smaller than the outer diameter of the fitting portions 251A and 252A, in other words, smaller than the inner diameter of the engagement holes 253 and 254. The protrusions 251 and 251 have annular engagement surfaces 251C and 252C that protrude in a direction perpendicular to the motor shaft direction continuously to the outer peripheral surfaces of the fitting portions 251A and 252A.

  When the motor 200 is assembled, the engagement holes 253 and 254 of the motor flange 202 are aligned with the protrusions 251 and 252 of the holder 205, and in this state, the motor 200 is moved toward the holder 205 ( Press toward the motor shaft). Then, the projecting portions 251 and 252 are inserted into the engagement holes 253 and 254 while narrowing the width of the slits 251B and 252B, in other words, elastically deforming the slits 251B and 252B in a direction substantially perpendicular to the motor shaft direction. Finally, the fitting portions 251A and 252A are engaged with the engagement holes 253 and 254 of the motor flange 202, respectively.

In this state, the engagement surfaces 251C and 252C of the protrusions 251 and 252 are in contact with the fixed flange surface 202A of the motor flange 202, and the surface 255 of the motor flange 202 opposite to the fixed flange surface 202A is the holder 205. It abuts on the end faces of the bosses 185 and 186. In other words, the motor flange 202 is sandwiched between the engagement surfaces 251C and 252C of the projecting portions 251 and 252 and the end surfaces of the boss portions 185 and 186.
As described above, also in the second embodiment, as in the first embodiment, the motor 200 can be fixed to the holder 205 in the motor shaft direction and the motor rotation direction.

[Third Embodiment]
With reference to FIG. 14 to FIG. 16, the third embodiment will be described mainly with respect to differences from the first embodiment. In addition, about the site | part common to 1st Embodiment, it represents with the same name and the same code | symbol.

  The third embodiment includes a motor support structure 193 that is different from the first embodiment. In the motor support structure 193, the motor 200 does not have the motor flange 202 (see FIG. 8) as in the first embodiment. Therefore, unlike the motor support structure 191 in the first embodiment, the motor flange 202 cannot be received by the boss portions 185 and 186 of the holder 205. Therefore, in the motor support structure 193 of the third embodiment, a ring-shaped spacer 260 is interposed between the outer peripheral edge portion on one end side (the upper side in FIG. 16) of the motor 200 and the holder 205 instead of the motor flange 202. Is done.

  In the third embodiment, a plurality of (two in the third embodiment) engaging claws 263 and 264 (convex shapes) in a direction substantially perpendicular to the motor shaft direction are provided on the outer peripheral surface on one end side of the motor 200. . Each engagement claw 263, 264 is formed by cutting and raising the side wall 204 (housing) of the motor 200 in the motor radial direction. Each of the engaging claws 263 and 264 is formed in a rectangular shape and is bent at a predetermined bending angle (inclination angle) with one side on one end side being a bending line. On the other hand, the holder 205 is provided with a plurality of (two in the third embodiment) projecting portions 261 and 262 projecting in the motor shaft direction. On the side surfaces 261A and 262A of the projecting portions 261 and 262 on the motor 200 side, corresponding to the engaging claws 263 and 264, in other words, recessed portions 265 and 266 (recessed portions) into which the engaging claws 263 and 264 are fitted. Shape) is formed.

  When the motor 200 is assembled, the engaging claws 263 and 264 of the motor 200 are brought into contact with the tips of the protrusions 261 and 262 of the holder 205, and in this state, the motor 200 is moved toward the holder 205 (motor Press in the axial direction). Then, the motor 200 moves to the holder 205 side while expanding the protrusions 261 and 262 with the engagement claws 263 and 264, and the engagement claws 263 and 264 move to the recesses 265 and 266 of the protrusions 261 and 262. At the time of facing, the engaging claws 263, 264 are fitted into the recesses 265, 266, the side surfaces 261 A, 262 A of the projecting portions 261, 262 are brought into contact with the outer peripheral surface of the motor 200, and the motor 200 The outer peripheral edge portion on one end side is in contact with the spacer 260.

  Thereby, the motor 200 is fixed to the holder 205 in the motor shaft direction and the motor rotation direction.

  Although the third embodiment has been described above, the motor support structure 193 can be configured by replacing the convex shape (uneven portion) on the motor 200 side and the concave shape (projecting portion) on the holder 205 side. That is, as shown in FIG. 17, convex portions 267 and 268 (engagement formed on the tip side of the side surfaces 261A and 262A of the respective projecting portions 261 and 262 of the holder 205 and projecting in a direction substantially perpendicular to the motor shaft direction. The motor support structure 193 is fixed so that the motor 200 is fixed to the holder 205 in the motor axial direction and the motor rotation direction by fitting the claw) into recesses 269 and 270 formed on the outer peripheral surface on one end side of the motor 200. Can be configured.

[Fourth Embodiment]
With reference to FIG. 18 thru | or FIG. 20, 4th Embodiment is mainly demonstrated focusing on a different part from 1st Embodiment. In addition, about the site | part common to 1st Embodiment, it represents with the same name and the same code | symbol.

  The fourth embodiment includes a motor support structure 194 different from the first embodiment. In the motor support structure 194, the motor 200 does not have the motor flange 202 (see FIG. 8) as in the first embodiment. The motor 200 has an outer peripheral edge portion on one end side received by a motor support portion (not shown) formed inside the protruding portion 271 of the holder 205 (abuts against the motor support portion). The motor 200 includes a resin case 272 that is attached to the outer peripheral surface of the side wall 204 (housing) and covers the other end side of the motor 200. The case 272 is formed in a bottomed cylindrical shape, and an insertion hole 273 through which a cylindrical rubber 248 disposed between the main body side end portion of the motor 200 and the bottom wall portion of the second housing 32 is inserted in the bottom portion. It is formed.

  A plurality of (two in the fourth embodiment) engaging claws 275 and 276 (uneven portions) projecting outward in the motor radial direction are provided on the side wall of the case 272. The engaging claws 275 and 276 extend substantially perpendicular to the motor shaft direction and are arranged toward the other end side of the motor 200, and from the tips of the engaging surfaces 275A and 276A. The motor 200 has inclined surfaces 275B and 276B extending inclined to one end side. In other words, each of the engaging claws 275 and 276 is formed in a substantially right triangle in cross section by the axial plane of the case 272.

  The holder 205 is provided with a substantially cylindrical protruding portion 271 that covers one end side (the upper side in FIG. 20) of the motor 200. The opening side (upper side in FIG. 20) end of the case 272 attached to the motor 200 is fitted inside the opening side (lower side in FIG. 20) end of the protrusion 271. Rectangular engagement holes 277 and 278 (concave shapes) are formed on the side wall of the projecting portion 271 at positions corresponding to the engagement claws 275 and 276 of the case 272 of the motor 200. Then, the engagement claws 275 and 276 are engaged with the engagement holes 277 and 278, whereby the case 272 of the motor 200 is coupled (fixed) to the protruding portion 271 of the holder 205.

  When the motor 200 is assembled, the engaging claws 275 and 276 of the case 272 attached to the motor 200 are brought into contact with the open ends of the protrusions 271 of the holder 205, and in this state, the motor 200 is attached to the holder 205. Press toward the motor shaft. Then, the motor 200 moves to the holder 205 side while deforming the projections 271 so that the projections 271 are pushed and expanded by the engagement claws 275 and 276 of the case 271, and the engagement claws 275 and 276 are engaged with the engagements of the projections 271. When facing the holes 277 and 278, the engaging claws 275 and 276 are engaged (fitted) with the engaging holes 277 and 278, respectively. Thereby, the motor 200 is fixed to the holder 205 in the motor shaft direction and the motor rotation direction.

  According to the fourth embodiment, since it is not necessary to craft or process the motor 200, a general-purpose motor can be applied, and the manufacturing cost can be reduced.

DESCRIPTION OF SYMBOLS 1 Disc brake, 30 Housing, 44 Spur gear reduction mechanism (deceleration mechanism), 45 Planetary gear reduction mechanism (deceleration mechanism), 181 and 182 Protruding part, 200 Motor, 202 Motor flange (uneven part) 205 Holder

Claims (7)

A motor that receives a supply of electric current and generates rotational motion;
A holder for supporting the motor and a speed reduction mechanism for increasing rotational movement from the motor;
A housing for housing the holder, the motor, and the speed reduction mechanism;
With
The motor has an uneven portion in the motor radial direction,
The holder has a protruding portion protruding in the motor axial direction,
The disc brake according to claim 1, wherein the motor is fixed in the motor axial direction and the motor rotating direction with respect to the holder by fitting the uneven portion of the motor and the protruding portion of the holder.   The uneven portion of the motor is formed on one end side in the motor axial direction and is a part of a fixed flange surface extending outward in the motor radial direction from the outer diameter of the motor. Disc brake as described.   The protruding portion of the holder has an engaging claw that protrudes in a direction substantially perpendicular to the motor shaft direction on the tip side, and the engaging claw is engaged with a part of the fixed flange surface. The disc brake according to claim 2. A hole is formed in the fixed flange surface,
The protrusion of the holder is formed with a notch extending in the motor axial direction in the central region, can be elastically deformed in a direction substantially perpendicular to the motor axial direction, and the protrusion is inserted into the hole of the fixed flange surface. The disc brake according to claim 2, wherein the disc brake is fixed to the fixed flange surface. The uneven portion of the motor is a convex shape in a direction substantially perpendicular to the motor axial direction,
The disc brake according to claim 1, wherein the protrusion of the holder has a concave shape on a side surface on the motor side. The uneven portion of the motor is a concave shape formed on the side surface on the motor side,
The protrusion of the holder has an engaging claw in a direction substantially perpendicular to the motor shaft direction on the tip side, and the engaging claw is engaged with a concave shape formed on the motor side. The disc brake according to claim 1. The motor includes a case having the concavo-convex portion on the outer peripheral surface of the housing,
The disc brake according to claim 1, wherein the protrusion of the holder has a recess formed on a side surface on the motor side.

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