JP2011179655A - Electric brake device for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent easy accumulation of water in recessed parts even when the recessed parts are formed on an outer periphery of a lid member in an electric brake device for a vehicle wherein the lid member made of resin held between a caliper body and a flange part by forming a speed reduction chamber between the caliper body and the flange part provided in an opening end of a bottomed cylindrical yoke composing one part of a motor case is fastened to the caliper body by common fastening of a plurality of bolts, and a motion converting mechanism converting rotating power into an axial reciprocating action of a brake piston is connected to an electric motor via a reduction gear housed in the speed reduction chamber. <P>SOLUTION: A plurality of boss parts 88c buried with cylindrical collars 94 for inserting the bolts 90, and the recessed parts 89 respectively disposed between each boss part 88c are formed on an outer peripheral surface of a lid member body 88a. Thinning communication holes 104 mutually communicating the recessed parts 89 in both sides of the boss parts 88c are formed in an inner end of the boss parts 88c in the radial direction of the lid member body 88a. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  According to the present invention, a flange portion is provided at an opening end of a bottomed cylindrical yoke that constitutes a part of a motor case included in an electric motor, and a caliper body of a disc brake has an accommodating recess that opens toward the electric motor. A lid member main portion formed in a disc shape so as to be able to close the housing recess, and a coupler portion integrally projecting outward from the lid member main portion for supplying power to the electric motor, A resin-made lid member in which concave portions are formed at a plurality of locations spaced in the circumferential direction of the outer periphery of the lid member main part forms a deceleration chamber between the caliper body and the caliper body and the flange part. The flange portion and the lid member are fastened to the caliper body by joint tightening with a plurality of bolts, and the rotational power is converted into the axial movement of the brake piston. Motion conversion mechanism to a vehicle electric brake system coupled to the electric motor via the reduction gear housed in the speed reduction chamber.

  Such an electric brake device for a vehicle is known from Patent Document 1, in which a flange portion of a bottomed cylindrical yoke that constitutes a part of a motor case in an electric motor, and a caliper body of a disc brake. When a coupler for supplying power to the electric motor is integrally provided, a synthetic resin brush holder is sandwiched, and the flange and the brush holder are fastened to the caliper body by joint fastening with a plurality of bolts. ing.

JP 2008-240869 A

  In the one disclosed in Patent Document 1, cylindrical collars through which bolts for fastening the flange portion of the yoke and the brush holder to the caliper body are inserted are embedded in a plurality of locations near the outer periphery of the brush holder. In the portion corresponding to each color, the collar is embedded in the outer periphery of the brush holder to prevent the occurrence of “sinking” due to the presence of the collar when the brush holder is molded. Each of the recesses is formed. However, water from the outside easily accumulates in the concave portion that is located at the upper position when the vehicle is mounted, which may cause rusting of surrounding parts and reduce the durability of the brush holder.

  The present invention has been made in view of such circumstances, and a reduction chamber is formed between the caliper body and a recess is formed on the outer periphery of a resin lid member sandwiched between the caliper body and the yoke. Another object of the present invention is to provide a vehicular electric brake device in which water does not easily accumulate in the recess.

  In order to achieve the above object, according to the present invention, a flange portion is provided at an open end of a bottomed cylindrical yoke that constitutes a part of a motor case included in an electric motor, and the caliper body of a disc brake is provided with the electric motor. An accommodation recess opening on the motor side is provided, and protrudes outward from the lid member main portion for feeding power to the electric motor and a lid member main portion formed in a disc shape so as to be able to close the accommodation recess. A resin lid member having a coupler portion integrally and having recesses formed at a plurality of locations spaced in the circumferential direction of the outer periphery of the lid member main portion forms a deceleration chamber with the caliper body. It is sandwiched between the caliper body and the flange portion, and the flange portion and the lid member are fastened to the caliper body by joint fastening with a plurality of bolts, and the rotational power is supplied to the brake piston. In the vehicular electric brake device in which the motion conversion mechanism that converts the movement to the axial advance / retreat operation is connected to the electric motor via the reduction gear housed in the reduction chamber, the outer peripheral surface of the lid member main part includes A plurality of boss portions in which a cylindrical collar through which the bolt is inserted are embedded, and the concave portions respectively disposed between the boss portions are formed, and the inside of the boss portion along the radial direction of the lid member main portion is formed. A first feature is that the end portion is formed with a through hole for communicating the concave portions on both sides of the boss portions with each other.

  In addition to the configuration of the first feature, the present invention provides a motor chamber formed in the motor case on one of the electric motor side surface and the speed reducer side surface of the lid member main portion, and A second feature is that a heat insulation space recess that forms a heat insulation space interposed between the deceleration chambers is provided.

  Further, according to the third feature of the present invention, in addition to the configuration of the first or second feature, a plurality of ribs arranged in the recess are provided integrally on the outer periphery of the lid member main portion. To do.

  The screw mechanism 24 of the embodiment corresponds to the motion conversion mechanism of the present invention.

  According to the first feature of the present invention, a plurality of boss portions in which a collar is embedded and the concave portions respectively disposed between the boss portions are formed on the outer peripheral surface of the lid member main portion of the lid member. Therefore, it is possible to reduce the cost by reducing the weight of the lid member and reducing the material. In addition, a through hole for communicating the recesses on both sides of the inner end of the boss portion along the radial direction of the lid member main portion is formed, thereby further reducing the weight of the lid member and reducing costs by reducing the material. In addition, even if water from the outside enters the concave portion that is in the upper position when the vehicle is mounted, water can flow to the concave portion on the lower side through the lightening communication hole, and water is accumulated in the concave portion. This can prevent the surrounding parts from being rusted and prevent the lid member from being lowered in durability.

  According to the second feature of the present invention, since the heat insulating space is interposed between the speed reduction chamber and the motor chamber, heat transfer from the electric motor to the speed reducer can be suppressed, and the components constituting the speed reducer are synthesized. Even if it is resin, the thermal deformation and strength reduction can be suppressed. In addition, since the heat insulation space is formed by a heat insulation space recess provided on either the electric motor side surface of the lid member main portion or the speed reducer side surface, further cost reduction is achieved by reducing the weight of the lid member and reducing the material. Can be achieved.

  Furthermore, according to the third feature of the present invention, since the ribs arranged in the recesses are provided integrally on the outer periphery of the lid member main part, the strength of the lid member is prevented from being reduced due to the formation of the recesses. Can do.

It is a longitudinal cross-sectional view of the electric brake device for vehicles. It is a principal part side view of the electric brake device for vehicles. FIG. 3 is a sectional view taken along line 3-3 in FIG. 1. FIG. 4 is an enlarged view of a portion indicated by an arrow 4 in FIG. 1. It is a disassembled perspective view of a reduction gear. FIG. 6 is an enlarged view of a portion indicated by an arrow 6 in FIG. 2. FIG. 7 is a cross-sectional view taken along line 7-7 in FIG.

  Hereinafter, an embodiment of the present invention will be described with reference to the accompanying FIGS. 1 to 7. First, in FIG. 1, an electric brake device for a vehicle includes a disc brake 21 and a caliper body 26 of the disc brake 21. The disc brake 21 is configured such that a forward / reversely rotatable electric motor 22 attached to the electric motor 22, a speed reducer 23 connected to the electric motor 22, and a rotational motion output from the speed reducer 23 is converted into an axially reciprocating motion. And a screw mechanism 24 which is a motion conversion mechanism provided between the brake piston 38 and the speed reducer 23.

  The disc brake 21 makes it possible to obtain a service brake state by hydraulic pressure and to operate by an electric motor 22 to obtain a parking brake state. The disc brake 21 rotates with a wheel of a wheel (not shown). 25, a caliper body 26, and a pair of friction pads 27, 28 disposed opposite to both side surfaces of the disk rotor 25 and disposed between the disk rotor 25 and the caliper body 26.

  Referring also to FIG. 2, the caliper body 26 includes a housing portion 26a supported by a bracket 29 attached to the vehicle body side so as to be slidable in a direction along the axis of the disc rotor 25, and a housing portion 26a. And an arm portion 26b extending across the disk rotor 25 to the opposite side.

  The friction pad 27 facing one side of the disk rotor 25 on the housing portion 26a side of the caliper body 26 is formed by providing a lining 30 on the back metal 32 that can slide and come into contact with the disk rotor 25. The friction pad 28 facing the other side surface of the disk rotor 25 on the arm portion 26b side of the body 26 is formed by providing a lining 31 on the back metal 33 that can slide and come into contact with the disk rotor 25. , 28 can be moved in the direction along the axis of the disc rotor 25 and is held by the bracket 29.

  The housing portion 26a of the caliper body 26 includes a cylinder hole 34 that has an axis parallel to the axis of the disk rotor 25 and opens to the friction pad 27 side, and an accommodation recess that opens to the opposite side of the friction pad 27. 35 and a partition wall 36 interposed between the cylinder hole 34 and the accommodating recess 35 is provided. The cylinder hole 34 and the accommodating recess 35 are formed so as to have a circular cross section on the same axis, and a through hole 37 that coaxially connects the cylinder hole 34 and the accommodating recess 35 is provided at the center of the partition wall 36. .

  A brake piston 38 that is formed in a cylindrical shape with a bottom closed at the front end and that forms a hydraulic pressure chamber 39 with the partition wall 36 is accommodated in the cylinder hole 34 so as to be axially slidable. The front end contacts the back metal 32 of the friction pad 27 and is engaged with the back metal 32 in order to prevent rotation in the cylinder hole 34.

  An annular piston seal 40 interposed between the caliper body 26 and the brake piston 38 is mounted on the inner surface of the cylinder hole 34, and an annular dust boot 41 is provided between the opening end of the cylinder hole 34 and the brake piston 38. The housing portion 26a is provided with a fluid pressure passage 42 for guiding fluid pressure to the fluid pressure chamber 39.

  The screw mechanism 24 includes a screw shaft 45 that is coaxial with the cylinder hole 34, and a nut 46 that is engaged with the brake piston 38 and cannot be rotated relative to the screw shaft 45. The caliper body 26 is accommodated in the housing portion 26a.

  At the rear end of the screw shaft 45 on the side opposite to the brake piston 38, a connecting shaft portion 45a that rotatably passes through the through hole 37 of the partition wall 36 is coaxially and integrally connected. A flange portion 45b projecting outward in the radial direction so as to face the partition wall 36 is integrally provided, and an O-ring 47 is interposed between the partition wall 36 and the connecting shaft portion 45a.

  Referring also to FIG. 3, the screw shaft 45 is screwed into a nut 46 surrounding the screw shaft 45 in the brake piston 38. The nut 46 includes a cylindrical portion 46a (see FIG. 1) that coaxially surrounds the screw shaft 45, an engaging portion 46b projecting radially outward from the front end of the cylindrical portion 46a, and the engaging portion 46b. An abutment protrusion 46c that protrudes forward from the center of the front end and abuts against the inner surface of the front end of the brake piston 38 is integrally formed, and a screw hole 48 for screwing the screw shaft 45 is an axial total length of the nut 46. Provided.

  The outer periphery of the engaging portion 46b is formed in a petal shape having protrusions 49, 49,... Arranged at a plurality of locations, for example, eight locations, equally spaced in the circumferential direction, and has a bottomed cylindrical shape. The cross-sectional shape of the inner periphery of the front part of the brake piston 38 is composed of four flat portions 50 corresponding to the two protrusions 49, 49, and four bent portions 51 connecting the flat portions 50. Are formed in a non-circular shape. As a result, the nut 46 is inserted into the brake piston 38 that is prevented from rotating in the cylinder hole 34 by engaging with the back metal 32, so that the engaging portion 46 b of the nut 46 is relative to the front portion of the brake piston 38. It will be engaged so that it cannot rotate.

  Between the protrusions 49 on the outer periphery of the engaging portion 46b of the nut 46 and between the front inner periphery of the brake piston 38, passages 52 that allow the brake fluid to flow are formed, respectively. Four passage grooves 53 are provided on the front end surface of the abutting protrusion 46c at the front end of the nut 46, extending radially outward from the screw hole 48 and arranged in a cross shape.

  Referring also to FIG. 4, between the flange portion 45b of the screw shaft 45 and the partition wall 36 of the caliper body 26, an O-ring interposed between the sliding bearing 54 and the partition wall 36 and the connecting shaft portion 45a. The washer 55 sandwiched between the sliding bearing 54 and the partition wall 36 is interposed while fulfilling the function as a pressing member that prevents the 47 from being separated, and the sliding bearing 54 and the washer 55 are formed in a flat ring shape.

  A ring-shaped fitting recess 56 is formed on the surface of the flange portion 45b facing the partition wall 36 so that the inner periphery is defined by the outer periphery of the base portion of the connecting shaft portion 45a. Is fitted into the fitting recess 56. Thus, the inner periphery of the fitting recess 56 is continuous with the outer periphery of the base of the connecting shaft 45a via the saddle curved surface 57, and the inner diameter of the sliding bearing 54 avoids contact with the saddle curved surface 57. Thus, it is set larger than the base outer diameter of the connecting shaft 45a.

  In such a screw mechanism 24, when the power from the electric motor 22 is decelerated by the speed reducer 23 and the power that rotates in one direction is transmitted to the screw shaft 45, the rotation of the brake piston 38 and the nut 46 is prevented. In this state, the disc rotor 25 is clamped from both sides by the friction pads 27 and 28 due to the action and the reaction caused by the brake piston 38 sliding forward in the axial direction, whereby a braking force is obtained. Further, when the screw shaft 45 is rotated in the other direction, the brake piston 38 slides rearward in the axial direction to release the braking state.

  Referring to FIG. 4, the motor case 83 of the electric motor 22 is attached to the housing portion 26 a of the caliper body 26 so as to close the open end of the housing recess 35. In the gear case 60 constituted by the caliper body 26, a reduction chamber 59 partially formed by the accommodation recess 35 is formed, and the reduction gear 23 is accommodated in the reduction chamber 59.

  The reduction gear 23 is provided with a first planetary gear mechanism 61 and a second planetary gear mechanism 62 between a motor shaft 95 of the electric motor 22 and a connecting shaft portion 45 a of the screw shaft 45 in the screw mechanism 24. It is made up of.

  Referring also to FIG. 5, the first planetary gear mechanism 61 includes a first sun gear 63 provided on the motor shaft 95, a ring gear 64 fixed to the gear case 60, the ring gear 64 and the first gear. A first carrier 66 rotatably supporting a plurality of, for example, three first planetary gears 65 meshing with the sun gear 63, and the second planetary gear mechanism 62 is provided on the inner periphery of the first carrier 66. The second sun gear 67 meshed with the outer periphery, the ring gear 64 common to the first planetary gear mechanism 61, and a plurality of, for example, three second planetary gears 68 meshed with the ring gear 64 and the second sun gear 67. And a second carrier 69 that is rotatably supported.

  The ring gear 64 common to the first and second planetary gear mechanisms 61 and 62 is formed in a cylindrical shape having an outer diameter slightly smaller than the inner diameter of the receiving recess 35 and is inserted into the reduction chamber 59. An end portion of the ring gear 64 opposite to the electric motor 22 is an inner end wall of the accommodating recess 35 in the caliper body 26 in order to restrict the rotation of the ring gear 64 about the axis. A concave-convex engagement is made with the partition wall 36 that constitutes. For this uneven engagement, in this embodiment, engagement slits 71 opened to the partition wall 36 at a plurality of circumferential positions, for example, three locations on the end of the ring gear 64 opposite to the electric motor 22. Are provided, and a plurality of, for example, three engaging pins 72, which are provided in the partition wall 36 and extend in parallel with the axis of the ring gear 64, are inserted into the engaging slits 71, respectively. Thus, each of the engagement pins 72 is provided in the partition wall 36 by inserting one end portion into a bottomed pin support hole 73 provided in the partition wall 36 and protrudes from the partition wall 36. The other ends of the pins 72 are inserted into the engagement slits 71.

  Moreover, as clearly shown in FIG. 6, the engagement pin 72 has a width d of the engagement slit 71 along the circumferential direction of the ring gear 64 so that a gap 74 is formed between the ring gear 64 and the engagement pin 72. The outer diameter D is set to be slightly larger than the outer diameter D of the ring gear 64, so that the ring gear 64 is in a limited range until the ring gear 64 comes into contact with the inner peripheral surface of the housing recess 35. The displacement of the ring gear 64 is allowed.

  The first carrier 66 is formed in a flat ring shape. The outer circumference of the second sun gear 67 on the electric motor 22 side of the second sun gear 67 whose cross-sectional shape is the same over the entire length in the axial direction is the first carrier 66. Engaged with the inner periphery, the second sun gear 67 rotates together with the first carrier 66.

  In the first carrier 66, a plurality of, for example, three locations that are equidistant from each other in the circumferential direction on a virtual circle centered on the axis are provided with first support pins 75 that have axes parallel to the first carrier 66. One end is fixed by, for example, press-fitting, and the other end of each first support pin 75 is inserted into a first support hole 76 provided in the first planetary gear 65.

  In addition, the first planetary gear 65 is opposed to the lid member main portion 88a of the lid member 88 of the motor case 83 constituting a part of the gear case 60. An annular recess 91 that is recessed on the opposite side of the machine 23 is formed so as to face the other end of each of the first support pins 75.

  The second planetary gears 68 mesh with the outer periphery of the half of the second sun gear 67 on the side opposite to the electric motor 22 and are arranged in the circumferential direction of the second carrier 69 formed in a flat ring shape. A second support hole 78 provided at the center of the second planetary gears 68 is provided at the other end of the second support pins 77 with one end fixed by press-fitting or the like at a plurality of spaced intervals, for example, three locations. Are inserted respectively.

  The end of the connecting shaft portion 45a that is coaxially and integrally connected to the screw shaft 45 in the screw mechanism 24 is inserted into the speed reducing chamber 59, and the end of the connecting shaft portion 45a is The second carrier 69 is directly press-fitted into a press-fitting hole 79 provided in the central portion.

  By the way, when the electric motor 22 is detached from the caliper body 26 and the deceleration chamber 59 is opened, the accommodation recess 35 provided in the caliper body 26 so as to constitute a part of the deceleration chamber 59 is opened. In this state, the speed reducer 23 can be disassembled leaving the second carrier 69 in which the connecting shaft portion 45a integrally connected to the screw shaft 45 of the screw mechanism 24 is press-fitted in the housing recess 35, and is left behind. The second carrier 69 is provided with a plurality of engagement holes 80 that are formed in a non-circular cross-section so that the rotary operation tool can be engaged.

  The motor case 83 of the electric motor 22 has a motor chamber 84 formed therein and is attached to the housing portion 26a of the caliper body 26. A flange portion 86a projecting outward in the radial direction is integrated with an opening end portion. A metal yoke 86 having a bottomed cylindrical shape, a metal bearing holder 87 disposed at the open end of the yoke 86, and an outer peripheral portion of the flange 86a. A lid member 88 made of a resin, for example, a synthetic resin, is used to close the open end of the yoke 86.

  The bearing holder 87 is formed by bending a metal plate, and has a cylindrical bearing housing portion 87a and a disc portion 87b extending outward from the bearing housing portion 87a. A plurality of locations on the outer peripheral portion of 87b are caulked and joined to the inner peripheral portion of the open end of the yoke 86.

  Referring also to FIG. 7, the lid member 88 is formed in a disc shape so as to close the accommodating recess 35 provided in the caliper body 26, and a plurality of lid members 88 are spaced apart in the circumferential direction of the outer periphery thereof. A lid member main portion 88a formed with a recess 89 at a location and a coupler portion 88b projecting outward from the lid member main portion 88a for supplying power to the electric motor 22 are integrally formed of a synthetic resin. A deceleration chamber 59 is formed between the caliper body 26 and sandwiched between the caliper body 26 and the flange portion 86a, and the flange portion 86a and the flange portion 86a are fastened together by a plurality of bolts 90. The lid member 88 is fastened to the caliper body 26.

  Moreover, on the outer peripheral surface of the lid member main portion 88a, a cylindrical collar 94 through which the bolts 90 are inserted is disposed between a plurality of boss portions 88c, and the boss portions 88c. The recesses 89 are formed, and the inner ends of the boss portions 88c along the radial direction of the lid member main portion 88a communicate with the recesses 89 on both sides of the boss portions 88a. The lightening communication holes 104 are formed.

  Further, in this embodiment, the heat insulating space recess 106 is formed on either the surface on the electric motor 22 side of the lid member main portion 88a or the surface on the speed reducer 23 side. The motor case 83 includes a heat insulating space recess 106 of the lid member main portion 88a and a metal bearing holder 87 disposed at the opening end of the yoke 86 so as to cover the heat insulating space recess 106. A heat insulating space 105 interposed between the motor chamber 84 and the deceleration chamber 59 formed therein is formed.

  Further, a plurality of ribs 107 arranged in the recesses 89 are integrally provided on the outer periphery of the lid member main portion 88a.

  Thus, in a state where the motor case 83 is attached to the housing portion 26 a of the caliper body 26, the opening end of the accommodation recess 35 in the caliper body 26 is closed by the lid member 88 constituting a part of the motor case 83. As a result, the axial movement of the ring gear 64 in the speed reducer 23 is restricted by the partition wall 36 of the caliper body 26 and the lid member 88, and is engaged with the partition wall 36 of the caliper body 26 in an uneven manner. As a result, the circumferential movement of the ring gear 64 is restricted. Therefore, the ring gear 64 is substantially fixed to the gear case 60 by restricting the axial movement by the partition wall 36 and the cover member 88.

  A motor shaft 95 of the electric motor 22 is rotatably supported by the motor case 83, and one end portion of the motor shaft 95 is inserted into a bearing housing 86 b provided at the central portion of the closed end of the yoke 86 via a ball bearing 96. The other end portion of the motor shaft 95 passes through the bearing holder 87 and the lid member 88 to be freely rotatable and enters the deceleration chamber 59, and the other end portion of the motor shaft 95 is inserted into the deceleration chamber 59. A first sun gear 63 is engraved on the outer periphery, and a ball is provided between the bearing housing portion 87a of the bearing holder 87 and the motor shaft 95 to prevent grease from flowing into the motor chamber 84 from the speed reduction chamber 59. A bearing 97 is interposed.

  In the motor chamber 84, the motor shaft 95 is provided with an armature 99 having a commutator 98, and a plurality of magnets 100, 100... Are fixed to the inner periphery of the yoke 139 at a portion corresponding to the armature 99.

  Further, a brush holder 101 is fixedly supported on the inner surface side of the bearing holder 140, and a brush (not shown) slidably supported by the brush holder 101 is in sliding contact with the commutator 98.

  An annular seal member 92 having a larger diameter than the inner periphery of the housing recess 35 is interposed between the housing portion 26 a of the caliper body 26 and the lid member 88, and the flange portion 86 a of the yoke 86 and the lid member 88. An annular seal member 93 located inside the bolt 90 is disposed between the annular seal members 93.

  Next, the operation of this embodiment will be described. The caliper body 26 of the disc brake 21 has a cylinder hole 34 into which the brake piston 38 is slidably fitted, and an accommodation recess 35 coaxial with the cylinder hole 34. The second carrier 69 that is an output member of the speed reducer 23 that is partly housed in the housing recess 35 is provided so as to open to the opposite side with the partition wall 36 interposed therebetween. Further, the screw mechanism 24 having the screw shaft 45 that is coaxially connected and rotatably penetrates the partition wall 36 converts the rotation of the screw shaft 45 into the forward and backward operation of the brake piston 38 in the axial direction. An electric motor 22 that is provided between the pistons 38 and that inputs rotational power to the speed reducer 23 is attached to the caliper body 26, and the screw shaft 4 is inserted into the cylinder hole 34. Between the flange portion 45b and the partition wall 36 which are provided integrally with the partition wall 36, a flat bearing 54 formed in the shape of a flat ring is interposed, but is opposed to the partition wall 36 of the flange portion 45b. A fitting recess 56 is formed on the surface to be fitted, and the sliding bearing 54 is fitted into the fitting recess 56. Therefore, the sliding bearing 54 can be attached to the flange portion 45b to facilitate the assembly, and the distance between the flange portion 45b of the screw shaft 45 and the partition wall 36 of the caliper body 26 is set short. This can contribute to shortening the axial length of the electric brake device.

  The speed reducer 23 includes a second carrier 69 that is coaxial with the screw shaft 45, and an end portion of a connecting shaft portion 45 a that the screw shaft 45 is integrated and coaxial is press-fitted coaxially and directly into the second carrier 69. Therefore, the axial displacement of the screw shaft 45 with respect to the second carrier 69 can be prevented, and it is not necessary to form the outer periphery of the end portion of the screw shaft 45, that is, the outer periphery of the connecting shaft portion 45a. Can be reduced.

  By the way, the speed reducer 23 is a two-stage planetary gear type speed reducer in which first and second planetary gear mechanisms 61 and 62 are provided between the motor shaft 95 of the electric motor 22 and the screw shaft 45 of the screw mechanism 24. The first planetary gear mechanism 61 includes a first sun gear 63 provided on the motor shaft 95, a ring gear 64 fixed to the gear case 60, and the ring gear 64. And a first carrier 66 that rotatably supports a plurality of first planetary gears 65 meshing with the first sun gear 63, and the second planetary gear mechanism 62 meshes with the inner periphery of the first carrier 66 at the outer periphery. The second sun gear 67, the ring gear 64 common to the first planetary gear mechanism 61, and the plurality of second planetary gears 68 meshing with the ring gear 64 and the second sun gear 67 are rotatable. In which and a second carrier 69 which supports.

  According to such a reduction gear 23, since the ring gear 64 common to the first and second planetary gear mechanisms 61 and 62 is fixed to the gear case 60, the bearing member is interposed between the ring gear 64 and the gear case 60. There is no need, and accordingly, the number of parts can be reduced and the gear case 60 can be reduced in size. In addition, since the inner periphery of the first carrier 66 of the first planetary gear mechanism 61 is meshed with the outer periphery of the second sun gear 67 in the second planetary gear mechanism 62, the second sun gear 67 is press-fitted into the first carrier 66. It is not necessary to secure the press-fitting length required in some cases, and it is possible not only to avoid the increase in the axial direction of the reduction gear 23 that is a two-stage planetary gear type, but also to eliminate the press-fitting step. The assembling work is facilitated, and the rotation can be stabilized by the self-aligning action by the engagement of the second sun gear 67 and the first carrier 66. Further, the outer peripheral shape of the second sun gear 67 is the same in the meshing portion with the first carrier 66 and the meshing portion with the second planetary gears 68, so that the processing of the second sun gear 67 can be facilitated.

  By the way, the motor case 83 of the electric motor 22 attached to the caliper body 26 so as to close the accommodating recess 35 provided in the caliper body 26 of the disc brake 21, and the caliper body 26 constituting the gear case 60 together with the motor case 83 In the meantime, a speed reduction chamber 59 for accommodating the speed reducer 23 is formed, and the ring gear 64 is decelerated so as to be prevented from axial movement by the lid member 88 and the caliper body 26 constituting a part of the motor case 83. Since the end of the ring gear 64 opposite to the electric motor 22 is inserted into the chamber 59 and engaged with the caliper body 26 so as to restrict the rotation of the ring gear 64 around the axis, A ring gear 64 that is common to the second planetary gear mechanisms 61 and 62 is formed as a part of the gear case 60. It can be substantially fixed to the caliper body 26.

  Moreover, engagement slits 71 are provided at a plurality of circumferential positions on the end of the ring gear 64 opposite to the electric motor 22, and the engagement pins 72 inserted into the engagement slits 71 are caliper bodies. 26, the number of parts for substantially fixing the ring gear 64 to the caliper body 26 can be reduced, and the engagement slits 71 can be formed by simply inserting the ring gear 64 into the reduction chamber 59. Since the engagement pins 72 are inserted, the ring gear 64 can be easily assembled.

  Further, the width d of the engagement slits 71 along the circumferential direction of the ring gear 64 and the outer diameter D of the engagement pins 72 are within a range in which the ring gear 64 is limited within a plane orthogonal to the axis of the speed reducer 23. Since the displacement is set to be allowed, the ring gear 64 can move in a plane orthogonal to the axis by the gap 74 formed between the engagement slits 71 and the engagement pins 72. The axial deviation of the first and second planetary gear mechanisms 61 and 62 can be absorbed, and smooth rotational power transmission by the speed reducer 23 becomes possible.

  Further, an annular seal member 92 having a larger diameter than the inner periphery of the housing recess 35 is interposed between the lid member 88 constituting a part of the motor case 83 and the caliper body 26. This sealing member 92 can prevent water or the like from entering the deceleration chamber 59 and the motor case 83.

  Meanwhile, in the first planetary gear mechanism 61, one end portions of a plurality of first support pins 75 are fixed to the first carrier 66, and the first support holes 76 provided in the first planetary gears 68 are first. The other end portions of the support pins 75 are inserted, and the annular recess 91 facing the other end portion of each first support pin 75 is a wall surface facing the first planetary gears 68 of the gear case 60. In the embodiment, it is formed on the cover member 88 that is a part of the motor case 83 that constitutes the gear case 60 together with the caliper body 26, so that the first planet 66 is moved in the axial direction relative to the first planetary gears 68. The length of the first support pins 75 can be set long while preventing the other end of the first support pins 75 projecting from the gears 68 from contacting the inner surface of the gear case 60. 1 can be secured a first support pin 75 ... take allowance significantly to the first planetary gear 68 ... rotational stability of the to the planetary gears 68 ....

  The accommodation recess 35 provided in the caliper body 26 is closed when the electric motor 22 is attached to the caliper body 26 to form a part of the deceleration chamber 59, and is opened when the electric motor 22 is detached from the caliper body 26. However, the speed reducer 23 includes an output member 70 that can be engaged with the twelve-angle socket 80 and is fixed to the screw shaft 45, and when the accommodating recess 35 is opened, the output member 70 is placed in the accommodating recess 35. Since the electric motor 22 is removed and most of the speed reducer 23 is removed, the 12-side socket 80 is engaged with the output member 70 and rotated. The parking brake state can be released by operating, and the reduction shaft 23 is connected to the screw shaft 45 of the screw mechanism 24. It is possible to exert a manual operation force without a, it is possible to release the parking brake state by a relatively small manual operation amount.

  The accommodation recess 35 provided in the caliper body 26 is closed when the electric motor 22 is attached to the caliper body 26 to form a part of the deceleration chamber 59, and is opened when the electric motor 22 is detached from the caliper body 26. However, the speed reducer 23 has a second carrier 69 fixed to the screw shaft 45 so as to be provided with a plurality of engagement holes 80.. When opened, the second carrier 69 can be left in the housing recess 35 and disassembled so that the second carrier 69 is accommodated in the speed reduction chamber 59. Therefore, the second motor 69 is removed while the electric motor 22 is removed and most of the speed reducer 23 is removed. The parking brake state can be released by engaging the rotation tool with the rotation operation tool on the carrier 69, and the screw mechanism 24. It is possible to exert a manual operating force without the screw shaft 45 going through a reduction gear 23, it can be released with a relatively small manual operation amount parking brake state.

  A heat insulating space 105 is provided between the motor chamber 84 formed in the motor case 83 of the electric motor 22 and the speed reduction chamber 59 that houses the speed reducer 23 so that at least a part of the caliper body 26 is formed. Since it is arranged, heat transfer from the electric motor 22 to the speed reducer 23 can be suppressed, and even if the parts constituting the speed reducer 23 are made of synthetic resin, the thermal deformation and strength reduction can be suppressed. it can.

  Further, the heat insulation is provided on the cover member 88 that constitutes a part of the motor case 83 and is interposed between the motor chamber 84 and the speed reduction chamber 59 so as to be fastened to the caliper body 26 around the open end of the housing recess 35. Since the heat insulating space recess 106 for forming the space 105 is provided, it is possible to reduce the weight of the lid member 88 and the motor case 83 while forming the heat insulating space 105, and further reduce the cost by reducing the material. Can be planned.

  Further, the lid member 88 includes a lid member main portion 88a formed in a disc shape so as to close the accommodating recess 35 provided in the caliper body 26, and the lid member main portion 88a for supplying power to the electric motor 22. Are integrally formed with a coupler portion 88b protruding outward from the outer peripheral surface of the lid member main portion 88a, and a plurality of cylindrical collars 94 through which bolts 90 are inserted are embedded. Are formed between the boss portions 88c and the boss portions 88c, respectively. The inner end portions of the boss portions 88c along the radial direction of the lid member main portion 88a are Since the through-hole communicating holes 104 are formed so as to communicate with each other the concave portions 89 on both sides of the boss portions 88c of the boss portions 88c, the weight of the lid member 88 can be reduced and the cost can be reduced by reducing the material. Moreover, even when water from the outside enters the concave portion 89 that is located at the upper position when the vehicle is mounted, water can flow to the lower concave portion 89 side through the lightening communication hole 104, and water is accumulated in the concave portion 89. This can prevent the surrounding parts from being rusted and prevent the lid member 88 from being deteriorated in durability.

  In addition, since the plurality of ribs 107 arranged in the concave portions 89 are integrally provided on the outer periphery of the lid member main portion 88a, it is possible to prevent the strength of the lid member 88 from being lowered due to the formation of the concave portions 89. it can.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. Is possible.

DESCRIPTION OF SYMBOLS 21 ... Disc brake 22 ... Electric motor 23 ... Reduction gear 24 ... Screw mechanism 26 which is a motion conversion mechanism ... Caliper body 35 ... Containing recessed part 38 ... Brake piston 59 ... Deceleration chamber 83 ... motor case 86 ... yoke 86a ... flange portion 88 ... lid member 88a ... lid member main portion 88b ... coupler portion 88c ... boss portion 89 ... Recess 90 ... Bolt 94 ... Collar 104 ... Meat removal communication hole 105 ... Insulation space 106 ... Insulation space recess 107 ... Rib

Claims (3)

  A flange portion (86a) is provided at an open end of a bottomed cylindrical yoke (86) constituting a part of a motor case (83) included in the electric motor (22), and a caliper body ( 26) is provided with a housing recess (35) that opens to the electric motor (22) side, and a lid member main portion (88a) formed in a disk shape so as to be able to close the housing recess (35); A coupler part (88b) protruding outward from the lid member main part (88a) is integrally provided for supplying power to the electric motor (22), and is spaced apart in the circumferential direction of the outer periphery of the lid member main part (88a). A resin lid member (88) in which recesses (89) are formed at a plurality of opened positions forms a deceleration chamber (59) between the caliper body (26) and the caliper body (26) and the Flange ( 6a), the flange portion (86a) and the lid member (88) are fastened to the caliper body (26) by joint fastening with a plurality of bolts (90), and the rotational power is supplied to the brake piston (38). In the electric brake device for a vehicle, the motion conversion mechanism (24) for converting into the axial advance / retreat operation is coupled to the electric motor (22) via the speed reducer (23) accommodated in the speed reduction chamber (59). A plurality of boss portions (88c) in which a cylindrical collar (94) for inserting the bolt (90) is embedded in the outer peripheral surface of the lid member main portion (88a), and the boss portions (88c) The recesses (89) respectively disposed between the boss portions (88c) are formed at the inner end portions of the boss portions (88c) along the radial direction of the lid member main portion (88a). The recesses on both sides ( Vehicle electric braking apparatus characterized by lightening communicating hole which communicates the 9) mutually (104) is formed.   A motor chamber (84) formed in the motor case (83) on one of the surface on the electric motor (22) side and the surface on the speed reducer (23) side of the lid member main portion (88a); The vehicular electric brake device according to claim 1, further comprising a heat insulation space recess (106) that forms a heat insulation space (105) interposed between the deceleration chambers (59).   The electric brake for vehicles according to claim 1 or 2, wherein a plurality of ribs (107) arranged in the recess (89) are integrally provided on an outer periphery of the lid member main part (88a). apparatus.

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